Motor-operated valve

Abstract

An object of the present invention is to provide a motor-operated valve in which it is difficult to control a flow rate of a fluid even when foreign matter is accumulated on a muffling member.SOLUTION: The sub-valve chamber 13b of the motor-operated 1 including the main body 11, the main valve body 13, the sub-valve chamber 13b, and the sub-valve body 14 includes the first sub-valve chamber 13d continuous with the communication hole 13b1 opened in the main valve body 13 and the second sub-valve chamber 13c continuous with the sub-valve port 13b2 provided in the main valve body 13, and the silencing member 16 is provided between the first sub-valve chamber 13b1 and the second sub-valve chamber 13b2. The flow path from the communication hole 13d to the sub-valve port 13c is provided with a first flow path R1 that flows from the first sub-valve chamber 13b1 into the second sub-valve chamber 13b2 through the silencing member 16 and a second flow path R2 that flows from the first sub-valve chamber 13b1 into the second sub-valve chamber 13b2 without passing through the silencing member 16, and the flow path area of the second flow path R2 is larger than the flow path area of the first flow path. R1.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a motor-operated valve. [Background technology]

[0002] Conventionally, a two-stage motor-operated valve that controls the flow rate of a fluid between a small flow rate control region and a large flow rate control region is known (see, for example, Patent Document 1). This motor-operated valve includes a valve housing (valve body) having a main valve chamber, a main valve element that opens and closes the main valve port, and a sub-valve element provided in a sub-valve chamber within the main valve element. The main valve element is provided with a communication passage that opens into the main valve chamber and a sub-valve port that opens toward the main valve port. An annular space that is continuous with the communication passage is formed inside the main valve element, and a sound-absorbing member is provided at a position that separates the annular space from the sub-valve chamber. The sound-absorbing member is made of, for example, a mesh-like member, and by breaking down air bubbles contained in the fluid passing through, it disperses the energy generated when the bubbles burst, thereby reducing the sound of the fluid passing through. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2022-94879 Summary of the Invention [Problem to be solved by the invention]

[0004] As described above, the silencer member is installed at a position that separates the annular space from the sub-valve chamber, i.e., in the fluid flow path, and the fluid passing through the silencer member may contain foreign matter generated from the piping connected to the motor-operated valve, the compressor connected to the piping, etc. For this reason, as the fluid passes through the silencer member, foreign matter may accumulate on the silencer member, clogging the flow path and making it difficult to control the flow rate of the fluid.

[0005] An object of the present invention is to provide an electrically operated valve that is less likely to become difficult to control the flow rate of a fluid even when foreign matter accumulates on the sound-absorbing member. [Means for solving the problem]

[0006] In order to solve the above problems and achieve the object, the motor-operated valve of the present invention comprises a cylindrical valve body having a valve chamber, a valve element disposed in the valve chamber, a drive unit that moves the valve element back and forth along the axial direction of the valve body, a valve seat having a valve port between which the valve element moves close to and away from each other, a first coupling pipe and a second coupling pipe attached to the valve body and communicating with the valve port, a flow path through which a fluid can pass in the order of the first coupling pipe, the valve chamber, the valve port, and the second coupling pipe, and a large opening in the flow path between the valve port and the second coupling pipe that does not block the flow path. and a sound-absorbing member provided at a length equal to or greater than the width of the valve body, the flow path comprising: a first retention section provided between the first joint pipe and the valve port for retaining the fluid; a first gap flow path formed by a gap between an outer surface of the valve body and an inner surface of the valve port; a second retention section provided between the first gap flow path and the second joint pipe and having a flow path area larger than that of the first gap flow path; and a second gap flow path provided between the second retention section and the second joint pipe and formed by a gap between the sound-absorbing member and the inner surface of the flow path.

[0007] Furthermore, it is preferable that the valve seat is formed in a cylindrical shape extending in the axial direction, the valve port opens on a surface of the valve seat facing the valve chamber, the valve seat is provided with a first opening continuing from the valve port and extending toward the second coupling pipe, and a second opening continuing from the first opening and opening toward the second coupling pipe, the silencing member is disposed inside the second opening, the second retention portion is defined by the internal space of the first opening, and the second gap flow path is defined by a gap between the silencing member and the inner surface of the second opening.

[0008] It is also preferable that an annular groove extending circumferentially around the axis of the valve body is formed on the outer periphery of the valve seat, and the first retention portion is defined by the inside of the groove. [Effects of the Invention]

[0009] According to the present invention, it is possible to provide an electrically operated valve in which control of the flow rate of fluid is unlikely to become difficult even when foreign matter accumulates on the sound-deadening member. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is an assembled cross-sectional view of an electrically operated valve according to a first embodiment of the present invention. [Figure 2] FIG. [Figure 3] FIG. [Figure 4] 1 is an enlarged cross-sectional view of a motor-operated valve according to a first modified example; [Figure 5] 10A is an enlarged cross-sectional view of the motor-operated valve and a perspective view of the sound-deadening member in a second modified example, and FIG. 10B is an enlarged cross-sectional view of the motor-operated valve and a perspective view of the sound-deadening member in a third modified example. [Figure 6] 10A is an enlarged cross-sectional view of the motor-operated valve in the fourth modified example, and FIG. 10B is a perspective view of the main valve body in the fourth modified example. [Figure 7] FIG. 10 is an enlarged cross-sectional view of a motor-operated valve according to a fifth modified example. [Figure 8] 10A is a perspective view of a sound-absorbing member in a sixth modified example, and FIG. 10B is an enlarged cross-sectional view of a motor-operated valve and a perspective view of the sound-absorbing member in a seventh modified example. [Figure 9] 13A is an enlarged cross-sectional view of the motor-operated valve in the eighth modified example, and FIG. 13B is a perspective view of the main valve body in the eighth modified example. [Figure 10] 11A is an enlarged cross-sectional view of the motor-operated valve according to the second embodiment, and FIG. 11B is a cross-sectional view taken along line AA in FIG. DETAILED DESCRIPTION OF THE INVENTION

[0011] A first embodiment of the present invention will be described below with reference to Figures 1 to 3. The motor-operated valve 1 according to this embodiment is a two-stage motor-operated valve used in a refrigeration cycle system or the like to control the flow rate of a refrigerant (fluid). The motor-operated valve 1 includes a valve body 11, a guide member 12, a main valve element 13, a sub-valve element 14, and a drive unit 15.

[0012] In the following explanation, in the drawings, the axial direction of the valve body 11 will be referred to as the "axial L direction," the side of the axial L direction where the drive unit 15 is located will be referred to as the "one side L1," and the opposite side of the one side L1 will be referred to as the "other side L2." The direction perpendicular to the axial L direction will be referred to as the "radial direction X." In addition, in the radial direction X, the side where the axial L is located will be referred to as the inside, and the opposite side of the inside will be referred to as the outside. This is for the sake of convenience of explanation only, and does not necessarily coincide with the directions in the actual operating state of the motor-operated valve 1, and does not limit the directions in the actual operating state of the motor-operated valve 1.

[0013] The valve body 11 is formed in a generally cylindrical shape from, for example, brass, stainless steel, or the like, and has a main valve chamber 11A therein. A first coupling pipe 18, which is connected to the main valve chamber 11A, is connected to the side wall of the valve body 11. A cylindrical portion 111 extending to the other side L2 is formed in the bottom wall of the valve body 11, and a second coupling pipe 19, which is connected to the main valve chamber 11A, is connected to the cylindrical portion 111. A main valve seat 112 is formed on the main valve chamber 11A side of the second coupling pipe 19 of the valve body 11, and the inside of this main valve seat 112 is a main valve port 112a. The main valve port 112a is a cylindrical hole centered on the axis L, and the second coupling pipe 19 is connected to the main valve chamber 11A via the main valve port 112a. In this way, the valve body 11 forms the main valve chamber 11A and the main valve port 112a. In this embodiment, the main valve seat 112 is formed integrally with the valve body 11, but a valve seat member having the main valve port 112a may be provided separately from the valve body 11 and assembled to the valve body 11.

[0014] The guide member 12 is attached to an opening on one side L1 of the valve body 11. The guide member 12 has a cylindrical guide portion 121 that is coaxial with the valve body 11 and extends in the direction of the axis L, a fitting portion 122 that protrudes radially outward from the outer circumferential surface of the guide portion 121 in the radial direction X and is fitted into the inner circumferential surface of the valve body 11, a holder portion 123 that extends to the one side L1 of the guide portion 121, a stopper portion 124 that is provided on the one side L1 of the holder portion 123, and a ring-shaped fixing member 125 made of a metal plate that protrudes from the outer periphery of the fitting portion 122. The guide portion 121, the fitting portion 122, the holder portion 123, and the stopper portion 124 are configured as a single piece made of resin, and the fixing member 125 is formed integrally with the resin fitting portion 122 by insert molding.

[0015] The guide member 12 is assembled to the valve body 11 by fitting the fitting portion 122 into the inner circumferential surface of the valve body 11, and is fixed to the upper end of the valve body 11 by welding via a fixing bracket 125. When assembling the guide member 12 to the valve body 11, the fitting portion 122 may be press-fit into an opening on one side L1 of the valve body 11. In the guide member 12, a cylindrical guide hole 12a coaxial with the axis L is formed inside the guide portion 121 and the fitting portion 122, and an insertion hole 12b coaxial with the guide hole 12a and for guiding a rotor shaft 152a (described later) forward and backward is formed in the center of the holder portion 123, and a female thread portion 12c coaxial with the guide hole 12a and for guiding a male thread portion 152c of the rotor shaft 152a (described later) is formed in the center of the stopper portion 124. A spiral guide groove 124a is formed on the outer peripheral surface of the stopper portion 124, in which a slider 154a of a stopper mechanism 154 (described later) is installed. The main valve element 13 is disposed within the guide hole 12a, and is guided back and forth in the direction of the axis L by the guide hole 12a.

[0016] The main valve element 13 is formed in a cylindrical shape extending in the direction of the axis L. The main valve element 13 is configured to have a main valve portion 131 that opens and closes the main valve port 112a by being seated on and released from the main valve seat 112, and a holding portion 132 that is a side wall of the main valve element 13 and holds the sub-valve element 14. A cylindrical opening 13a (external opening) that is centered on the axis L and opens toward the other side L2 (toward the main valve port 112a) is formed inside the main valve portion 131. The opening 13a is formed with a larger diameter than the sub-valve port 13c, which will be described later. A second sound-absorbing member 17, which will be described later, is installed in the opening 13a.

[0017] A sub-valve chamber 13b is formed inside the holding portion 132, and a holding member 13A that holds a muffler member 16 (described later) is disposed in the sub-valve chamber 13b. The holding member 13A is provided coaxially with the holding portion 132 and is formed in a cylindrical shape with a bottom that opens to the other side L2. The outer peripheral surface of the holding member 13A extends in the direction of the axis L along the inner peripheral surface of the holding portion 132. An end of the other side L2 of a rotor shaft 152a (described later) is inserted in the direction of the axis L through a bottom wall (wall portion of the one side L1) of the holding member 13A, thereby connecting the holding member 13A and the rotor shaft 152a. In other words, the main valve element 13 and the rotor shaft 152a are connected via the holding member 13A. A sub-valve port 13c is formed between the main valve portion 131 and the holding portion 132. The sub-valve port 13c is a cylindrical space that opens from the sub-valve chamber 13b to the other side L2 (the opening 13a side) about the axis L.

[0018] A communication hole 13d is formed in a side surface of the holding portion 132 of the main valve element 13, opening in the radial direction X toward the main valve chamber 11A. A plurality of (e.g., eight) communication holes 13d are formed radially at rotationally symmetric positions about the axis L. As a result, the sub-valve chamber 13b communicates with the main valve chamber 11A via the communication holes 13d. The main valve element 13 also has a retainer 133 at an end of one side L1 of the holding portion 132, and a main valve spring 134 between the retainer 133 and the upper end of the guide hole 12a of the guide member 12. The main valve element 13 is biased toward the other side L2 (closing direction) by this main valve spring 134. Note that the above-mentioned communication hole 13d is not limited to being formed radially at rotationally symmetric positions, and the number of communication holes 13d may be one, or multiple communication holes 13d may be formed at unequal intervals.

[0019] The sub-valve element 14 is provided integrally with the lower end of the rotor shaft 152a and is provided inside the sub-valve chamber 13b so as to be movable in the direction of the axis L. The sub-valve element 14 is composed of a columnar guide boss portion 141 formed with a diameter larger than that of the rotor shaft 152a and a shaft-shaped needle valve 142 formed with a diameter smaller than that of the rotor shaft 152a. The tip of the needle valve 142 of the sub-valve element 14 is inserted into the sub-valve port 13c in the direction of the axis L, and small flow rate control is performed by allowing a small flow rate of refrigerant to flow through the gap between the needle valve 142 and the sub-valve port 13c. The guide boss portion 141 is inserted into the retaining member 13A and is guided in the direction of the axis L by the retaining member 13A. Furthermore, when the end face on one side L1 of the guide boss portion 141 moves to one side L1 in conjunction with the movement of the rotor shaft 152a, it can come into contact with the wall surface facing the other side L2 on the inner wall surface of the holding member 13A, thereby enabling the rotor shaft 152a (sub-valve element 14) and the main valve element 13 to move integrally to one side L1. Note that the sub-valve element 14 and the rotor shaft 152a may be formed separately and then assembled together.

[0020] The drive unit 15 includes a case 151 that is hermetically fixed to the end of one side L1 of the valve body 11 by welding or the like, a stepping motor 152, a screw feed mechanism 153 that moves the sub-valve body 14 forward and backward by rotation of the stepping motor 152, and a stopper mechanism 154 that regulates the rotation of the stepping motor 152.

[0021] The stepping motor 152 is composed of a rotor shaft 152a extending in the direction of axis L, a magnet rotor 152b rotatably disposed inside the case 151, a stator coil (not shown) disposed opposite the magnet rotor 152b on the outer periphery of the case 151, and other components such as a yoke and exterior members. The rotor shaft 152a is attached to the center of the magnet rotor 152b via a bushing, and a male thread portion 152c is formed on the outer periphery of the upper part of the rotor shaft 152a. The male thread portion 152c is threadedly engaged with a female thread portion 12c of the guide member 12, so that the guide member 12 supports the rotor shaft 152a on the axis L. The female thread portion 12c of the guide member 12 and the male thread portion 152c of the rotor shaft 152a form a screw feed mechanism 153. As described above, the other side L2 portion of the rotor shaft 152a is inserted in the axial direction L into the bottom wall (wall portion of one side L1) of the retaining member 13A, and the above-mentioned sub-valve body 14 is integrally formed at its end.

[0022] The stopper mechanism 154 includes a guide groove 124a formed on the outer peripheral surface of the stopper portion 124 of the guide member 12, and a slider 154a installed in the guide groove 124a. The slider 154a abuts against the magnet rotor 152b around the axis L, rotates along the guide groove 124a in conjunction with the rotation of the magnet rotor 152b, and moves back and forth in the direction of the axis L. The slider 154a restricts the rotation of the magnet rotor 152b by abutting against the upper or lower end of the guide groove 124a. The stopper mechanism 154 restricts the lowermost and uppermost positions of the rotor shaft 152a and the magnet rotor 152b.

[0023] With the above configuration, when the stepping motor 152 is driven, the magnet rotor 152b and rotor shaft 152a rotate, and the rotor shaft 152a moves together with the magnet rotor 152b in the direction of the axis L due to the screw feed mechanism 153 between the male thread portion 152c and the female thread portion 12c. Then, the sub-valve element 14 moves back and forth in the direction of the axis L, and the needle valve 142 of the sub-valve element 14 moves toward or away from the sub-valve port 13c. At this time, as shown in FIG. 1, if the main valve element 13 is seated on the main valve seat 112, a small flow rate of refrigerant flows through the gap between the needle valve 142 and the sub-valve port 13c, and the state becomes a small flow rate control range state (small flow rate control region) in which small flow rate control is performed as described above. That is, the small flow rate control range state refers to a state in which the main valve element 13 closes the main valve port 112a and the sub-valve element 14 controls the opening degree of the sub-valve port 13c provided in the main valve element 13, thereby forming a refrigerant flow path in the gap between the sub-valve element 14 and the sub-valve port 13c. When the sub-valve element 14 moves to one side L1, as described above, the end face on one side L1 of the guide boss portion 141 abuts against the wall surface facing the other side L2 on the inner wall surface of the holding member 13A (this position is particularly referred to as the sub-valve upper end position). When the sub-valve element 14 moves further to one side L1, the main valve element 13 moves together with the sub-valve element 14, and the main valve portion 131 of the main valve element 13 lifts off the main valve seat 112. This fully opens the main valve port 112a, entering a large flow rate control range state (large flow rate control range) in which large flow rate range control is performed. That is, the large flow rate control range state refers to a state in which the main valve element 13 opens the main valve port 112a.

[0024] Next, the structure of the main valve element 13 will be described in detail. As shown in FIG. 2, a cylindrical sub-valve seat 13e is formed around the sub-valve port 13c of the main valve element 13. The sub-valve seat 13e is formed rising toward the one side L1 from the center of the inner circumferential surface of the main valve portion 131 facing the one side L1. A groove 13f, which is annular in plan view and opens toward the one side L1, is formed around the entire circumference of the sub-valve seat 13e on the radially outer side X of the sub-valve seat 13e so as to surround the periphery of the sub-valve port 13c. This groove 13f communicates with the communication hole 13d, and its interior forms the first sub-valve chamber 13b1 of the sub-valve chamber 13b. Note that the groove 13f does not necessarily have to be a completely annular space; it may have any shape that allows the fluid that flows into the groove 13f from the main valve chamber 11A via the communication hole 13d to temporarily remain therein. On the other hand, the inside of the holding portion 132 is a cylindrical space that continues to the sub-valve port 13c and faces the first sub-valve chamber 13b1 in the axial direction L, and this space constitutes the second sub-valve chamber 13b2 of the sub-valve chamber 13b.

[0025] A sound-absorbing member 16 is installed between the sub-valve seat 13e and the holding member 13A, i.e., between the first sub-valve chamber 13b1 and the second sub-valve chamber 13b2. The sound-absorbing member 16 reduces refrigerant passing noise by breaking down bubbles contained in the refrigerant and dispersing the energy generated when the bubbles burst. The sound-absorbing member 16 is made of a mesh material, a porous material, a sintered body, or other material, and is formed into a C-shape by cutting out approximately one-quarter of a portion of an annular shape along the inner circumferential surface of the main valve body 13, as shown in FIG. 3 . In addition to the above-mentioned materials, the sound-absorbing member 16 may also be formed using a material with holes formed by punching a metal, resin, or fiber plate member. As shown in FIG. 2 , the minimum inner diameter of the sound-absorbing member 16 is larger than the maximum inner diameter of the sub-valve port 13c and smaller than the minimum inner diameter of the groove 13f that defines the first sub-valve chamber 13b1. The width of the silencing member 16 is set to be larger than the groove width of the groove 13f. The height of the silencing member 16 is set to be the same as the dimension in the axial direction L from the wall surface facing the one side L1 of the sub-valve seat 13e to the end face of the other side L2 of the holding member 13A. Therefore, a bottom wall surface 16a (bottom surface portion), which is the wall surface of the other side L2 of the silencing member 16 shown in FIG. 3, abuts against both the wall surface facing the one side L1 of the sub-valve seat 13e and the wall surface of the inner wall surface of the main valve body 13 facing the one side L1. An upper wall surface 16b (upper surface portion) of the one side L1 of the silencing member 16 shown in FIG. 3 abuts against the end face of the other side L2 of the holding member 13A.

[0026] Because the sound deadening member 16 is formed in a C-shape, the fluid flow path from the communication hole 13d inside the main valve element 13 to the sub-valve port 13c includes a first flow path R1 that passes from the first sub-valve chamber 13b1 to the second sub-valve chamber 13b2 through the sound deadening member 16 as shown by the dotted arrow in Fig. 2, and a second flow path R2 that passes from the first sub-valve chamber 13b1 to the second sub-valve chamber 13b2 without passing through the sound deadening member 16 as shown by the solid arrow in Fig. 2. The second flow path R2 is configured by an opening that is formed between the inner wall of the main valve element 13 that runs from the first sub-valve chamber 13b1 to the second sub-valve chamber 13b2 and the end 16c of the sound deadening member 16.

[0027] Here, the maximum flow path area (flow path area) of the first flow path R1 is the total area of ​​the gaps in the sound deadening member 16 at the portion where the opening of the groove 13f and the bottom wall surface 16a on the other side L2 of the sound deadening member 16 overlap in the axial direction L when the groove 13f is viewed in plan from the one side L1. In contrast, the minimum flow path area (flow path area) of the second flow path R2 is the smaller of the opening area of ​​the groove 13f at the portion where the opening does not overlap in the axial direction L with the bottom wall surface 16a on the other side L2 of the sound deadening member 16 at the groove 13f when viewed in plan from the one side L1, or the opening area (the product of the length from one end 16c to the other end 16c on the inner diameter of the sound deadening member 16 and the height of the sound deadening member 16) when the cutout portion (between one end 16c and the other end 16c) of the sound deadening member 16 is viewed from the front in the radial direction X. In this embodiment, the minimum flow path area of ​​the second flow path R2 is set to be larger than the maximum flow path area of ​​the first flow path R1. In addition, the minimum flow path area of ​​the second flow path R2 is set to be larger than the maximum opening area of ​​the sub-valve port 13c. The maximum opening area of ​​the sub-valve port 13c refers to the opening area when the sub-valve port 13c is viewed from the direction of the axis L.

[0028] A second silencing member 17 is installed in the opening 13a of the main valve portion 131. Similar to the silencing member 16, the second silencing member 17 also reduces refrigerant passing noise. The second silencing member 17 is formed in a cylindrical shape using a mesh material, a porous material, a sintered body, or other material, and is supported within the opening 13a by a retaining ring 171 fixed to the other side L2, with its outer circumferential surface abutting the inner circumferential surface of the opening 13a. Note that, like the silencing member 16, the second silencing member 17 may be formed using a material with holes formed by punching a metal, resin, or fiber plate member, for example. With this configuration, as described above, the opening 13a is formed with a larger diameter than the sub-valve port 13c, and therefore the other side L2 of the sub-valve port 13c is entirely covered by the second silencing member 17.

[0029] As described above, according to this embodiment, even if foreign matter accumulates on the muffler 16, the refrigerant flowing through the passage from the communication hole 13d to the sub-valve port 13c can move between the communication hole 13d and the sub-valve port 13c through the second passage R2, making it difficult to control the flow rate. Furthermore, by making the minimum flow area of ​​the second passage R2, which does not pass through the muffler 16, larger than the maximum flow area of ​​the first passage R1, which passes through the muffler 16, it is easy to ensure a flow path, and changes in the maximum flow rate in the small flow rate control range when foreign matter accumulates on the muffler 16 can be reduced. Therefore, it is possible to provide an electrically operated valve 1 in which it is difficult to control the flow rate of the refrigerant even when foreign matter accumulates on the muffler 16. Furthermore, if foreign matter is contained in the refrigerant, the foreign matter can be captured by the muffler 16 as the refrigerant passes through the first passage R1, thereby preventing the foreign matter from becoming trapped in the sub-valve port 13c.

[0030] In this case, a second flow path R2 that does not pass through the silencer 16 can be formed by an opening formed between the main valve element 13, which extends from the first sub-valve chamber 13b1 to the second sub-valve chamber 13b2, and the end 16c of the silencer 16. In this case, part of the second flow path R2 is formed by the end 16c of the silencer 16, so that if the refrigerant passing through the second flow path R2 contains bubbles, the bubbles will be broken down by the end 16c of the silencer 16. Therefore, the refrigerant passing sound can be reduced while ensuring the flow rate of the flow path from the communication hole 13d to the sub-valve port 13c.

[0031] Furthermore, by making the minimum flow path area of ​​the second flow path R2 larger than the maximum opening area of ​​the sub-valve port 13c, the maximum flow rate of the refrigerant in the small flow rate control range depends on the size of the sub-valve port 13c, so it is possible to reduce the change in the maximum flow rate of the refrigerant in the small flow rate control range between when foreign matter has accumulated in the sound-absorbing member 16 and when it has not, and to reduce the effect on the flow rate of the refrigerant caused by foreign matter clogging the sound-absorbing member 16.

[0032] Furthermore, because the first sub-valve chamber 13b1 is configured with the annular groove 13f that surrounds the periphery of the sub-valve port 13c, the refrigerant that flows into the first sub-valve chamber 13b1 through the communication hole 13d can swirl and accumulate in the circumferential direction along the wall of the first sub-valve chamber 13b1. This increases the contact opportunity between the refrigerant and the sound deadening member 16 provided between the first sub-valve chamber 13b1 and the second sub-valve chamber 13b2, thereby breaking down bubbles contained in the refrigerant and dispersing the energy generated when the bubbles burst, thereby reducing refrigerant passing noise. Increasing the contact opportunity between the refrigerant and the sound deadening member 16 also makes it easier for foreign matter to be absorbed by the sound deadening member 16, making it more difficult for foreign matter to be mixed into the refrigerant flowing through the first flow path R1 and the second flow path R2.

[0033] Furthermore, the first sub-valve chest 13b1 is formed as an annular groove, and the second sub-valve chest 13b2 is formed as a cylindrical space facing the sub-valve port 13c and the first sub-valve chest 13b1 in the direction of the axis L, so that refrigerant can flow between the first sub-valve chest 13b1 formed as an annular groove and the second sub-valve chest 13b2 formed as a cylindrical space via the first flow path R1 and the second flow path R2. At this time, if the refrigerant contains air bubbles, the size of the air bubbles decreases as they remain in the annular first sub-valve chest 13b1 and move to the cylindrical second sub-valve chest 13b2, so that the passing noise of the refrigerant flowing from the second sub-valve chest 13b2 to the sub-valve port 13c can be further suppressed.

[0034] Furthermore, according to the shape of the sound deadening member 16 of this embodiment, when the sound deadening member 16 is produced, it is only necessary to form a mesh or porous material into a circular ring shape and then cut out a portion of the ring into a C-shape, which simplifies the structure of the sound deadening member 16 and reduces the production cost of the sound deadening member 16.

[0035] Next, a first modified example of the motor-operated valve 1 will be described. FIG. 4 is an enlarged cross-sectional view of the motor-operated valve 1 in the first modified example. In the first modified example, the shape and inner diameter of the sound deadening member 16 differ from those of the first embodiment. Specifically, the sound deadening member 16 is formed in an annular shape along the inner circumferential surface of the main valve body 13. The minimum inner diameter (inner diameter) of the sound deadening member 16 is set larger than the maximum inner diameter (inner diameter) of the groove 13f that forms the first sub-valve chamber 13b1. In other words, the minimum inner diameter of the sound deadening member 16 is set larger than the maximum inner diameter (inner diameter) of the first sub-valve chamber 13b1.

[0036] With this configuration, a gap is created between the inner wall of the silencer member 16 and the inner wall of the first sub-valve chamber 13b1, and this gap can be used as part of the second flow path R2. Therefore, special processing is not required on the silencer member 16 side or the valve body 11 side to form the second flow path R2, which reduces the manufacturing costs of the silencer member 16 and the valve body 11. Furthermore, with this configuration, the silencer member 16 is formed in an annular shape, so that its outer peripheral edge can abut over its entire circumference against the wall surface facing one side L1 on the inner wall surface of the holding portion 132 of the main valve body 13, and therefore the posture of the silencer member 16 can be maintained more stably.

[0037] Next, a second modified example of the motor-operated valve 1 will be described. FIG. 5(A) is a cross-sectional view of the motor-operated valve 1 in the second modified example and a perspective view of the silencer member 16. In the second modified example, the dimensions of the silencer member 16 are different from those in the first modified example. The minimum inner diameter of the silencer member 16 is larger than the maximum inner diameter of the sub-valve port 13c and smaller than the minimum inner diameter of the groove 13f that defines the first sub-valve chamber 13b1. The width of the silencer member 16 is also larger than the groove width of the groove 13f. As a result, the bottom wall surface 16a on the other side L2 of the silencer member 16 abuts, over its entire periphery, against the wall surface facing the one side L1 of the inner wall surface of the holding portion 132 of the main valve body 13 and the wall surface facing the one side L1 of the sub-valve seat 13e, and the bottom wall surface 16a on the other side L2 of the silencer member 16 covers the opening of the groove 13f. 5(A), four inner circumferential recesses 16d (recesses) recessed outward in the radial direction X are formed at equal intervals in the circumferential direction on the inner circumferential surface (inner circumferential portion) of the sound deadening member 16. In the portions where the inner circumferential recesses 16d are formed, the distance between the inner circumferential surfaces of the sound deadening member 16 that face each other in the radial direction X is greater than the maximum inner diameter dimension of the grooves 13f.

[0038] With this configuration, a gap is formed between the inner surface of the inner circumferential recess 16d and the inner surface of the first sub-valve chamber 13b1, and this gap can be made part of the second flow path R2. That is, the inner circumferential recess 16d can be made part of the second flow path R2. Furthermore, with the above-described dimensions of the sound deadening member 16, the bottom wall surface 16a on the other side L2 of the sound deadening member 16 can abut over the entire circumference (excluding the inner circumferential recess 16d) against the wall surface facing the one side L1 of the sub-valve seat 13e and the wall surface facing the one side L1 of the inner wall surface of the holding portion 132 of the main valve body 13. That is, since the bottom wall surface 16a abuts against the wall surfaces on the inner and outer circumferential sides of the groove 13f, these wall surfaces support the sound deadening member 16, and the posture of the sound deadening member 16 can be more stably maintained.

[0039] Next, a third modified example of the motor-operated valve 1 will be described. FIG. 5(B) is a cross-sectional view of the motor-operated valve 1 and a perspective view of the sound deadening member 16 in the third modified example. In the third modified example, the shape of the sound deadening member 16 is different from that in the second modified example. Specifically, four protrusions 16e protruding toward the other side L2 are formed at equal intervals in the circumferential direction on the bottom wall surface 16a (bottom surface portion) of the other side L2 of the sound deadening member 16. The protrusions 16e are formed extending from the outer edge of the sound deadening member 16 in the radial direction X to the inner edge in the radial direction X. The portions between the protrusions 16e form bottom surface recesses 16f (recesses) recessed from the protruding ends of the protrusions 16e toward the one side L1. That is, four bottom surface recesses 16f are formed at equal intervals in the circumferential direction on the bottom wall surface 16a of the other side L2 of the sound deadening member 16.

[0040] When the silencer 16 is installed in the motor-operated valve 1, the protruding end of the protrusion 16e comes into contact with a wall surface facing the one side L1 of the sub-valve seat 13e and a wall surface facing the one side L1 of the inner wall surface of the holding portion 132 of the main valve body 13. That is, the protrusion 16e comes into contact with wall surfaces on the inner and outer circumferential sides of the groove 13f. In this state, a gap is generated in the bottom surface recess 16f in the direction of the axis L by the height of the protrusion 16e, and the refrigerant can pass through this gap in the radial direction X, and this gap forms part of the second flow path R2.

[0041] With this configuration, the bottom surface recess 16f can form part of the second flow path R2. Furthermore, the protruding end of the protrusion 16e abuts against the wall surface facing the one side L1 of the sub-valve seat 13e and the wall surface facing the one side L1 of the inner wall surface of the holding portion 132 of the main valve body 13, so that these wall surfaces support the sound deadening member 16, and the posture of the sound deadening member 16 can be maintained more stably.

[0042] Next, a fourth modified example of the motor-operated valve 1 will be described. FIG. 6(A) is a cross-sectional view of the motor-operated valve 1 in the fourth modified example, and FIG. 6(B) is a perspective view of the main valve body 13 in the fourth modified example. In the fourth modified example, the shape of the sub-valve seat 13e is different from that of the above-described embodiment and modified examples. As shown in FIG. 6(B), the sub-valve seat 13e is formed in a substantially cylindrical shape, rising from the center of the wall surface facing one side L1 of the inner wall surface of the main valve portion 131 toward one side L1. Four sub-valve seat-side recesses 13g (recesses) recessed inward in the radial direction X are formed at equal intervals in the circumferential direction on the outer peripheral surface of the sub-valve seat 13e (the inner peripheral surface of the first sub-valve chamber 13b1). In the portion where the sub-valve seat-side recesses 13g are formed, the maximum diameter of the sub-valve seat 13e is set to be smaller than the minimum inner diameter of the sound-absorbing member 16. On the other hand, the maximum diameter dimension in the radial direction X of the sub-valve seat 13e in the portion where the sub-valve seat side recess 13g is not formed is set to be larger than the minimum inner diameter dimension of the sound deadening member 16.

[0043] With this configuration, a gap is created between the inner surface of the sub-valve seat side recess 13g and the inner circumferential surface of the sound deadening member 16, and this gap can be used as part of the second flow path R2. Therefore, to form the second flow path R2, there is no need to perform special processing, such as providing a recess on the sound deadening member 16 side, and the manufacturing cost of the sound deadening member 16 can be reduced.

[0044] The arrangement and number of the inner circumferential recess 16d, bottom recess 16f, and sub-valve seat side recess 13g described in the second to fourth modified examples may be different from each other. That is, the inner circumferential recess 16d, bottom recess 16f, and sub-valve seat side recess 13g do not have to be equally spaced circumferentially, and the number of recesses may be four or less or four or more. Furthermore, in each modified example, the motor-operated valve 1 has been described as having only the inner circumferential recess 16d, bottom recess 16f, and sub-valve seat side recess 13g, but this is merely an example, and the motor-operated valve 1 may be configured by combining any or all of the inner circumferential recess 16d, bottom recess 16f, and sub-valve seat side recess 13g.

[0045] Next, a fifth modified example of the motor-operated valve 1 will be described. FIG. 7 is a cross-sectional view of the motor-operated valve 1 in the fifth modified example. In the fifth modified example, the dimensions of the silencer member 16 and the structure of the retaining member 13A differ from those of the above-described embodiment and modified examples. The minimum inner diameter of the silencer member 16 is larger than the maximum inner diameter of the sub-valve port 13c and smaller than the minimum inner diameter of the groove 13f that defines the first sub-valve chamber 13b1. The maximum outer diameter of the silencer member 16 is smaller than the maximum outer diameter of the groove 13f that defines the first sub-valve chamber 13b1. As shown in FIG. 7, a communication portion 13A1 that communicates with the inside and outside of the retaining member 13A is formed in the end of the other side L2 of the retaining member 13A provided in the main valve body 13 and extends radially X. The communication portion 13A1 may be a through-hole, a slit, or the like. 7, the second flow path R2 is formed by the space between the inner wall surface of the holding portion 132 and the outer peripheral surface of the sound deadening member 16, the communicating portion 13A1, and the inside of the holding member 13A. In other words, the communicating portion 13A1 constitutes a part of the second flow path R2.

[0046] With this configuration, the second flow path R2 can be formed so as to pass through the inside and outside of the holding member 13A, which widens the range of options for where to form the second flow path R2. Furthermore, by providing the communication portion 13A1 in the configuration of the second flow path R2, the refrigerant that has flowed into the sub-valve chamber 13b from the communication hole 13d can be temporarily directed toward the holding member 13A, which makes it possible to change the flow direction and flow speed of the refrigerant.

[0047] Next, a sixth modified example of the motor-operated valve 1 will be described. FIG. 8(A) is a perspective view of the sound deadening member 16 in the sixth modified example. In the sixth modified example, the shape of the sound deadening member 16 differs from that of the fifth embodiment. The outer peripheral surface (outer peripheral portion) of the sound deadening member 16 is formed with outer peripheral recesses 16g (recesses) that are recessed inward in the radial direction X. Four outer peripheral recesses 16g are formed at equal intervals in the circumferential direction. Note that the arrangement and number of the outer peripheral recesses 16g are not limited to those of this modified example, as with the inner peripheral recesses 16d and bottom surface recesses 16f described above.

[0048] According to this configuration, a gap is formed between the inner wall surface of the retaining portion 132 and the inner surface of the outer peripheral recess 16g of the sound deadening member 16. This gap can serve as the second flow path R2, thereby achieving the same functions and effects as those of the fifth modified example. Unlike the fifth modified example, this modified example may have the maximum outer diameter of the sound deadening member 16 larger than the maximum outer diameter of the groove 13f. Even in this case, by setting the maximum outer diameter of the sound deadening member 16 smaller than the maximum outer diameter of the groove 13f in the portion where the outer peripheral recess 16g is formed, a gap can be formed between the inner surface of the retaining portion 132 and the inner surface of the outer peripheral recess 16g, thereby achieving the same functions and effects as those of the fifth embodiment. In this case, the outer radial direction X portion of the bottom wall surface 16a of the other side L2 of the sound deadening member 16, excluding the portion where the outer peripheral recess 16g is formed, can be brought into contact with the wall surface of the inner wall surface of the retaining portion 132 of the main valve body 13 that faces the one side L1. This is more preferable because the posture of the sound deadening member 16 can be more stably maintained.

[0049] Next, a seventh modified example of the motor-operated valve 1 will be described. FIG. 8(B) is a cross-sectional view of the motor-operated valve 1 and a perspective view of the silencer member 16 in the seventh modified example. In the seventh modified example, the structure of the retaining member 13A and the shape of the silencer member 16 differ from those in the fifth modified example. In this modified example, the communication portion 13A1 of the retaining member 13A is omitted. Furthermore, four convex portions 16h protruding toward the one side L1 are formed at equal intervals in the circumferential direction on the upper wall surface 16b, which is the wall surface of the one side L1 of the silencer member 16. The circumferential portions between the convex portions 16h form upper surface recesses 16i that are recessed from the protruding ends of the convex portions 16h toward the other side L2. When the silencer member 16 is installed in the motor-operated valve 1, the protruding ends of the convex portions 16h abut against the end surface of the other side L2 of the retaining member 13A. In this state, a gap is generated in the upper surface recess 16i in the direction of the axis L, and the refrigerant can pass through the gap in the radial direction X. This gap becomes part of the second flow path R2. In other words, the upper surface recess 16i constitutes part of the second flow path R2.

[0050] According to this configuration, there is no need to form the communication portion 13A1 in the holding member 13A, which simplifies the structure of the holding member 13A and reduces the manufacturing cost of the holding member 13A. In the present embodiment, the communication portion 13A1 is omitted and the second flow path R2 is formed by providing the upper surface recess 16i in the sound deadening member 16. However, the same effects and advantages as those of this modified example can be achieved by, for example, providing a recess (not shown) recessed toward one side L1 in the wall surface on the other side L2 of the holding member 13A (the end surface that abuts the protrusion 16h in this modified example). That is, the recess (a recess corresponding to the upper surface recess 16i in this modified example) can be provided in at least one of the holding member 13A that holds the sound deadening member 16 provided in the main valve body 13 and the sound deadening member 16.

[0051] Next, an eighth modified example of the motor-operated valve 1 will be described. FIG. 9(A) is a cross-sectional view of the motor-operated valve 1 in the eighth modified example, and FIG. 9(B) is a perspective view of the main valve body 13 in the eighth modified example. In the eighth modified example, the structure of the main valve body 13 differs from the above-described embodiment and modified examples. As shown in FIG. 9(B), in the main valve body 13, an inner wall-side recess 13h recessed outward in the radial direction X is formed on the inner wall of the retaining portion 132 that constitutes the outer peripheral surface of the first sub-valve chamber 13b1. Note that in FIG. 9(B), the inner wall-side recess 13h is formed extending from an edge of one side L1 of each communication hole 13d to one side L1. However, the inner wall-side recess 13h and each communication hole 13d do not necessarily have to be aligned coaxially, and the inner wall-side recess 13h and each communication hole 13d may be positioned at different positions in the circumferential direction. In the portion where the inner wall recess 13h is formed, the maximum outer diameter of the groove 13f is set to be larger than the maximum outer diameter of the sound deadening member 16.

[0052] With this configuration, a gap is created between the inner surface of the inner-wall-side recess 13h and the outer peripheral surface of the sound deadening member 16, and this gap can be used as part of the second flow path R2. Because there is no need to form a recess or the like in the sound deadening member 16, the structure of the sound deadening member 16 can be simplified, and the manufacturing cost of the sound deadening member 16 can be reduced.

[0053] In the fifth to eighth modified examples, the configurations have been described in which the communicating portion 13A1 of the retaining portion 132, the outer peripheral recess 16g of the sound-absorbing member 16, the upper surface recess 16i of the sound-absorbing member 16, and the inner wall side recess 13h of the main valve body 13 are provided singly, but this is merely one example, and the electric valve 1 may be configured by combining any or all of the communicating portion 13A1, the outer peripheral recess 16g, the upper surface recess 16i, and the inner wall side recess 13h, or these configurations may be combined with the other modified examples described above.

[0054] For example, the fourth and eighth modifications may be combined to form a main valve element 13 having a sub-valve seat-side recess 13g and an inner wall-side recess 13h. In this case, for example, by adjusting the minimum inner diameter or maximum outer diameter of the silencing member 16 so that the silencing member 16 can be reliably supported by the wall surface facing the one side L1 of the sub-valve seat 13e and the wall surface facing the one side L1 of the inner wall surface of the holding portion 132 of the main valve element 13, the posture of the silencing member 16 can be stably maintained while favorably achieving both the sub-valve seat-side recess 13g and the inner wall-side recess 13h. This is more preferable because it also increases the flow path area of ​​the second flow path R2. In this way, the sub-valve seat-side recess 13g or the inner wall-side recess 13h (a recess provided on at least one of the inner circumferential surface and the outer circumferential surface of the first sub-valve chamber 13b1) can be part of the second flow path R2.

[0055] Similarly, it is also possible to combine the inner peripheral recess 16d, bottom surface recess 16f, and sub-valve seat side recess 13g of the above-described sound deadening member 16 with any of the fifth to eighth modified examples. In this way, the sound deadening member 16 can be provided with at least one of the inner peripheral recess 16d, bottom surface recess 16f, outer peripheral recess 16g, and top surface recess 16i.

[0056] Next, a motor-operated valve 1 according to a second embodiment of the present invention will be described. Fig. 10(A) is an enlarged cross-sectional view of the motor-operated valve 1 according to the second embodiment. Fig. 10(B) is a cross-sectional view taken along the line AA in Fig. 10. As shown in Fig. 10(A), the opening 13a of the main valve portion 131 includes a first opening 13a1 that is continuous with the opening edge of the other side L2 of the sub-valve port 13c, and a second opening 13a2 that is continuous with the first opening 13a1 and has a larger inner diameter than the first opening 13a1. A second silencing member 17 is disposed in the second opening 13a2.

[0057] In the second embodiment, the shape of the second silencing member 17 differs from the above-described embodiments and modifications. The second silencing member 17 is formed in a substantially cylindrical shape. A second recess 17a (recess) is formed in a part of the outer peripheral surface of the second silencing member 17. The second recess 17a is recessed inward in the radial direction X and opens outward in the radial direction X and in the direction of the axis L. The refrigerant flowing from the sub-valve port 13c to the other side L2 first enters the first opening 13a1 and then splits into two paths: one that passes through the second silencing member 17 to the main valve chamber 11A and reaches the main valve port 112a, and the other that passes through the second recess 17a to the main valve chamber 11A and reaches the main valve port 112a.

[0058] By providing the second silencer member 17 having the first opening 13a1, the second opening 13a2, and the second recess 17a in this manner, the flow path from the sub-valve port 13c to the main valve port 112a includes a third flow path R3 that flows from the first opening 13a1 (opening 13a (external opening)) through the second silencer member 17 into the main valve chamber 11A, and a fourth flow path R4 that flows from the first opening 13a1 through between the inner surface of the second recess 17a and the inner circumferential surface of the second opening 13a2 (opening 13a) into the main valve chamber 11A without passing through the second silencer member 17. That is, the first opening 13a1, the second opening 13a2, and the second recess 17a form part of the fourth flow path R4.

[0059] As shown in FIG. 10(B), when the main valve element 13 is cut in the radial direction X at the first opening 13a1 and viewed in cross section from the axial direction L, the minimum flow path area of ​​the fourth flow path R4 is the area surrounded by the inner circumferential surface of the second recess 17a and the inner circumferential surface of the first opening 13a1. In the present embodiment, the minimum flow path area of ​​the fourth flow path R4 is set to be larger than the maximum opening area of ​​the sub-valve port 13c. In the second embodiment, the fourth flow path R4 is formed by forming the second recess 17a in the second silencer member 17. However, for example, the fourth flow path R4 may be formed by forming a recess corresponding to the second recess 17a in the inner circumferential surface of the opening 13a. That is, a portion of the fourth flow path R4 can be formed by a recess provided in at least one of the inner circumferential surface of the opening 13a of the main valve element 13 and the outer circumferential surface of the second silencer member 17.

[0060] With this configuration, the refrigerant passing through the sub-valve port 13c and heading toward the main valve port 112a passes through either the third flow path R3 or the fourth flow path R4, and even if foreign matter accumulates on the second silencer 17, the refrigerant can pass through the fourth flow path R4, making it difficult to control the flow rate. In addition, by making the minimum flow area of ​​the fourth flow path R4 larger than the maximum opening area of ​​the sub-valve port 13c, a flow path is secured, and it is possible to reduce changes in the maximum flow rate in the small flow rate control range when foreign matter accumulates on the second silencer 17. Therefore, it is possible to provide an electrically operated valve 1 in which it is difficult to control the flow rate of the refrigerant even if foreign matter accumulates on the second silencer 17.

[0061] In this case, a recess provided on at least one of the inner circumferential surface of the opening 13a of the main valve body 13 and the outer circumferential surface of the second silencing member 17 can form part of the fourth flow path R4.

[0062] Although the embodiments of the motor-operated valve 1 have been described above in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the present invention also includes design changes and the like within the scope of the present invention. For example, in the first embodiment, the second flow path R2 is configured by an opening formed between the inner wall of the main valve body 13 extending from the first sub-valve chamber 13b1 to the second sub-valve chamber 13b2 and the end portion 16c of the silencer member 16, but the configuration of the second flow path R2 is not limited to this. For example, the second flow path R2 may be provided in any of the flow paths extending from the communication hole 13d to the sub-valve port 13c, such as the configurations exemplified in the above-mentioned Modifications 1 and 2, or other configurations.

[0063] Furthermore, the minimum flow path area of ​​the second flow path R2 may be smaller than the maximum opening area of ​​the sub-valve port 13c. If the minimum flow area of ​​the second flow path R2 is larger than at least the maximum flow area of ​​the first flow path R1, the flow path is easily secured, and the change in the maximum flow rate in the small flow rate control range when foreign matter accumulates in the sound deadening member 16 can be reduced.

[0064] Furthermore, the first sub-valve chamber 13b1 does not have to be formed in a circular ring shape in a plan view. The first sub-valve chamber 13b1 may have any shape as long as it has a wall portion or the like against which the fluid flowing in from the communicating hole 13d can collide, so that the fluid flowing in from the main valve chamber 11A through the communicating hole 13d can temporarily remain. Similarly, the second sub-valve chamber 13b2 does not have to be formed as a cylindrical space.

[0065] Furthermore, the shape of the sound absorbing member 16 is not limited to the C-shape described above, and may be any shape that has an opening that allows the second flow path R2 to be formed. Furthermore, in each of the modified examples, the sound absorbing member 16 is formed in an annular shape that follows the inner circumferential surface of the main valve body 13, but the shape of the sound absorbing member 16 is not limited to this, and may be various shapes, such as a square tube or a rounded square tube, that may or may not match the inner shape of the main valve body 13. In each of the modified examples, the sound absorbing member 16 may also have a shape with a portion cut out, as in the first embodiment.

[0066] Furthermore, in the second embodiment, the second silencing member 17 is formed in a substantially cylindrical shape, but various shapes, such as a cube or a rectangular parallelepiped, may be used to match or not match the shape of the inner surface of the opening 13a. Furthermore, instead of forming the second recess 17a in the second silencing member 17, a part of the columnar second silencing member 17 may be cut in the direction of the axis L to form a fourth flow path R4 between the outer surface of the second silencing member 17 and the inner surface of the opening 13a. [Explanation of symbols]

[0067] L axis R1 First flow path R2 Second flow path 1. Motor-operated valve 11A Main valve chamber 11 Valve body 112a Main valve port 13 Main valve body 13b Sub-valve chamber 13b1 First sub-valve chamber 13b2 Second sub-valve chamber 13c Sub-valve port 13d communication hole 14 Sub-valve body 16 Sound deadening material

Claims

1. an actuator for moving the valve element back and forth along the axial direction of the valve element; a valve seat having a valve port where the valve element moves close to and away from the valve element; first and second coupling pipes attached to the valve element and communicating with the valve port; a flow path through which a fluid can pass through the first coupling pipe, the valve chamber, the valve port, and the second coupling pipe in that order; and a sound-absorbing member provided in a portion of the flow path between the valve port and the second coupling pipe and sized so as not to block the flow path, In the middle of the flow path, a first retention portion provided between the first joint pipe and the valve port to retain the fluid; a first gap flow path formed by a gap between an outer surface of the valve body and an inner surface of the valve port; a second retention section provided between the first gap flow passage and the second joint pipe and having a flow passage area larger than that of the first gap flow passage; a second gap flow path provided between the second retention portion and the second coupling pipe and configured as a gap between the silencing member and the inner surface of the flow path.

2. The valve seat portion is formed in a cylindrical shape extending in the axial direction, the valve port opens to a surface of the valve seat facing the valve chamber, the valve seat portion is provided with a first opening portion that is continuous with the valve port and extends toward the second joint pipe, and a second opening portion that is continuous with the first opening portion and opens toward the second joint pipe, the sound deadening member is disposed inside the second opening, the second retention portion is formed by an internal space of the first opening, 2. The motor-operated valve according to claim 1, wherein the second gap flow path is formed by a gap between the silencing member and the inner surface of the second opening.

3. an annular groove extending in a circumferential direction around the axis of the valve body is formed on the outer periphery of the valve seat; 3. The motor-operated valve according to claim 2, wherein the first retention portion is formed by the inside of the groove.

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