JP7386191B2 - electric valve - Google Patents

Description

The present invention relates to an electric valve used in a refrigeration cycle system or the like.

BACKGROUND ART Conventionally, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control area and a large flow rate area (see, for example, Patent Document 1). The conventional motor-operated valve described in Patent Document 1 includes a main valve body and a sub-valve body, and allows refrigerant (fluid) to flow into the sub-valve chamber in the main valve body from the communication passage of the sub-valve body. The refrigerant is throttled in the port throttle section, which is the gap between the needle valve and the auxiliary valve port, to control the flow rate to a small level.

JP2020-106086A

However, in the conventional motor-operated valve as described in Patent Document 1, if the liquid phase of the refrigerant flowing into the communication passage mixes with the gas phase and the state of the refrigerant is unstable, the port throttle is closed without stabilizing the refrigerant. When the refrigerant flows into the port constriction section, there is a problem in that the sound of refrigerant passing through the port constriction section increases.

An object of the present invention is to fully close a main valve port with a main valve element, and control the flow rate of fluid in a small flow rate control range by using a gap between the auxiliary valve port provided on the main valve element and the auxiliary valve element. To provide a motorized valve capable of stabilizing the state of fluid in a sub-valve chamber, reducing fluid passage noise at a sub-valve port, and suppressing noise and vibration of the motor-operated valve. .

The motor-operated valve of the present invention includes a valve body that constitutes a main valve chamber and a main valve port, a main valve body that is provided in the main valve chamber and opens and closes the main valve port, and a sub-valve body that is formed in the main valve body. a sub-valve body provided movably in the axial direction in the valve chamber, the main valve body closes the main valve port, and the opening degree of the sub-valve port provided in the main valve body is controlled by the sub-valve body. The motor-operated valve has a small flow rate control region that throttles the flow rate of fluid in a gap between the needle valve and the auxiliary valve port by controlling the needle valve of the valve body, A communication passage that opens toward the chamber, and an annular space that continues annularly around the axis between the communication passage and the sub-valve chamber, and between the annular space and the sub-valve chamber. is provided with a muffling member that muffles noise by allowing fluid to pass therethrough, and in the small flow rate control region, fluid from the main valve chamber to the main valve port enters the annular space from the communication path and enters the annular space. After turning, it bends in the axial direction, passes through the noise damping member, enters the auxiliary valve chamber, and is narrowed from the auxiliary valve chamber by a gap between the needle valve and the auxiliary valve port.

According to the present invention, in the small flow rate control region, the fluid from the main valve chamber to the main valve port enters the annular space from the communication path, turns in the annular space, and then bends in the axial direction and passes through the sound deadening member. By entering the auxiliary valve chamber after passing through, the fluid swirling in the annular space is decelerated, and after being further bent in the axial direction, it passes through the muffling member and is muffled. Therefore, the state of the fluid is stabilized before it enters the auxiliary valve chamber, reducing the sound of fluid passing through the gap between the auxiliary valve port and the needle valve of the auxiliary valve body, and suppressing the noise and vibration of the electric valve. can do.

In this case, it is preferable that the annular space has a flow cross-sectional area larger than the total cross-sectional area of the communication passages.

Further, it is preferable that a throttle passage having a flow passage cross-sectional area smaller than that of the annular space is provided between the annular space and the sub-valve chamber.

Further, it is preferable that the sub-valve chamber is provided with an enlarged space whose volume is larger than that of the annular space.

Moreover, it is preferable that a bending path is provided between the annular space and the sub-valve chamber, the bending path bending outward in the radial direction and further bending in the axial direction.

Further, a holding member for holding the sound deadening member is provided in the main valve body, and a part of the bending path is formed by a gap between an inner circumferential surface of the main valve body and an outer circumferential surface of the holding member, It is preferable that the holding member is provided with a communication hole that communicates the bending path with the auxiliary valve chamber.

Further, a fixing member for holding the sound damping member is provided in the main valve body, the fixing member has a first fixing member provided on the annular space side, and the first fixing member includes the It is preferable that a first through hole communicating with the annular space is provided.

Furthermore, it is preferable that the first fixing member has a bottom portion that comes into contact with a bottom surface of the sound deadening member, and a wall portion that faces a side surface of the sound deadening member. Furthermore, the first through hole is provided in the bottom, the height of the wall is smaller than the height of the sound deadening member, and the sound deadening member is located beyond the tip of the wall. Preferably, the sides are exposed.

Furthermore, the fixing member has a second fixing member provided on the opposite side of the first fixing member with the sound deadening member interposed therebetween, and the first fixing member and the second fixing member allow the fixing member to It is preferable to hold the sound deadening member between them. Furthermore, it is preferable that the second fixing member is provided in contact with substantially the entire surface of one surface of the sound deadening member, and is provided with a second through hole that communicates with the sub-valve chamber. Further, a radial width dimension of the second fixing member is smaller than a radial width dimension of the sound deadening member, and the second fixing member is provided in partial contact with one surface of the sound deadening member. It may be.

Moreover, it is preferable that at least one of the first fixing member and the second fixing member is an elastic member.

According to the electric valve of the present invention, even if the fluid is a mixture of gas phase fluid and liquid phase fluid, the state of the fluid in the auxiliary valve chamber is stabilized, and the auxiliary valve port and the needle of the auxiliary valve body are stabilized. The state of the fluid before passing through the valve gap is stabilized. Therefore, it is possible to reduce the noise of fluid passing through the gap between the auxiliary valve port and the needle valve, and to suppress the generation of noise and vibration of the electric valve.

BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows the electric valve of 1st Embodiment of this invention. FIG. 3 is an enlarged sectional view showing a main part of the electric valve in a small flow rate control region state. FIG. 6 is a diagram showing the flow of fluid in a small flow rate control region state of the electric valve. FIG. 7 is an enlarged cross-sectional view showing a first modification of the electric valve. FIG. 7 is an enlarged sectional view showing a second modification of the electric valve. FIG. 7 is an enlarged sectional view showing a third modification of the electric valve. FIG. 7 is an enlarged sectional view showing a fourth modification of the electric valve. FIG. 2 is an enlarged cross-sectional view showing the main parts of an electric valve according to a second embodiment of the present invention. It is a sectional view showing modification 5 of the electric valve. FIG. 7 is an enlarged sectional view showing a sixth modification of the electric valve. It is an enlarged sectional view showing modification 7 of the electric valve. FIG. 7 is an enlarged cross-sectional view showing modification example 8 of the electric valve. FIG. 7 is an enlarged sectional view showing a modification 9 of the electric valve.

Embodiments of the electric valve of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal cross-sectional view showing a motor-operated valve according to a first embodiment of the present invention, FIG. 2 is an enlarged cross-sectional view showing the main parts of the motor-operated valve in a small flow control region state (secondary valve lower end position), and FIG. 3 is an enlarged cross-sectional view of the motor-operated valve. FIG. 3 is a diagram showing the flow of refrigerant (fluid) in a small flow rate control region state. Note that the concept of "up and down" in the following description corresponds to the up and down in FIG. 1, and this up and down direction is sometimes referred to as the axis L direction, and the direction orthogonal to the axis L is sometimes referred to as the radial direction. Further, in the second embodiment and subsequent embodiments to be described later, members and parts that are the same as or similar to those in the first embodiment are given the same reference numerals and explanations may be omitted or simplified.

The electric valve 10 of this embodiment includes a valve housing 1 which is a valve body, a guide member 2, a main valve body 3, a sub-valve body 4, and a drive section 5.

The valve housing 1 is made of, for example, brass or stainless steel and has a substantially cylindrical shape, and has a main valve chamber 1A inside thereof. A first joint pipe 11 connected to the main valve chamber 1A is connected to one side of the outer circumference of the valve housing 1, and a second joint pipe 12 is connected to a cylindrical portion extending downward from the lower end. Further, a main valve seat 13 is formed on the main valve chamber 1A side of the second joint pipe 12 of the valve housing 1, and the inside of this main valve seat 13 is a main valve port 1B. The main valve port 1B is a cylindrical hole centered on the axis L, and the second joint pipe 12 is communicated with the main valve chamber 1A via the main valve port 1B. In this embodiment, the main valve seat 1B is integrally formed with the valve housing 1, but a valve seat member having a main valve port is provided separately from the valve housing, and the valve seat member is attached to the valve housing. It may also be assembled into a form.

A guide member 2 is attached to an opening at the upper end of the valve housing 1 . The guide member 2 includes a fitting part 21 fitted into the inner peripheral surface of the valve housing 1, a substantially cylindrical guide part 22 located inside the fitting part 21 and centered on the axis L, and a guide part 22. It has a holder part 23 extending above the part 22, a stopper part 24 provided above the holder part 23, and a ring-shaped fixing fitting 25 made of a metal plate that protrudes from the outer periphery of the fitting part 21. are doing. The fitting part 21, the upper guide part 22, the holder part 23, and the stopper part 24 are constructed as an integral part made of resin, and the fixing fitting 25 is provided integrally with the fitting part 21 made of resin by insert molding. ing. Note that the fitting portion 21 of the guide member 2 may be press-fitted into the valve housing 1.

The guide member 2 is assembled to the valve housing 1 through a fitting portion 21 and is fixed to the upper end of the valve housing 1 via a fixing fitting 25 by welding. Further, in the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the fitting part 21 and the guide part 22, and a cylindrical guide hole 2A coaxial with the guide hole 2A is formed in the center of the holder part 23. An insertion hole 2B for guiding the rotor shaft 51 (described later) forward and backward is formed in the center of the stopper part 24. A matching female threaded portion 2C is formed. A main valve body 3 is disposed within the guide hole 2A, and the main valve body 3 is guided forward and backward in the direction of the axis L by the guide hole 2A.

The main valve body 3 includes a main valve part 31 that seats and leaves the main valve seat 13, and a holding part 32 that is a side wall of the main valve body 3 and holds the sub valve body 4. has been done. A cylindrical opening 3A is formed inside the main valve part 31, and a cylindrical sub-valve chamber 3B is formed inside the holding part 32. A holding member 3C that holds the member 37 within the main valve body 3 is provided. A cylindrical sub-valve port 3D is formed between the main valve part 31 and the holding part 32 and opens from the sub-valve chamber 3B toward the opening 3A with the axis L as the center.

A communication passage 3E is formed on the side surface of the holding portion 32 of the main valve body 3 and opens toward the main valve chamber 1A in a direction intersecting the axis L. As shown in FIG. 3(A), a plurality of communication passages 3E (for example, eight) are formed radially at positions that are rotationally symmetrical about the axis L. Further, the main valve body 3 has a retainer 33 at the upper end of the holding part 32, and a main valve spring 34 between the retainer 33 and the upper end of the guide hole 2A of the guide member 2. The main valve body 3 is biased toward the main valve seat 13 (closed direction) by the valve spring 34 . Note that a muffling member 35 is disposed inside the opening 3A of the main valve portion 31. Note that the communication passages 3E are not limited to a configuration in which a plurality of communication passages 3E are formed radially at rotationally symmetrical positions, and the number of communication passages 3E may be one, or a plurality of communication passages 3E may be formed at irregular intervals.

The sub-valve body 4 is integrally provided at the lower end of the rotor shaft 51. This sub-valve body 4 is composed of a guide boss portion 41 and a needle valve 42. Further, the needle valve 42 of the sub-valve body 4 has its tip inserted into the sub-valve port 3D in the direction of the axis L, and a small flow rate of refrigerant flows through the gap between the needle valve 42 and the sub-valve port 3D. As a result, small flow rate control is performed. An annular washer 43 made of lubricating resin is disposed at the upper end of the guide boss 41, and the guide boss 41 is inserted into the holding member 3C. The outer circumferential surface of this guide boss portion 41 is guided by slidingly contacting the inner circumferential surface of the holding member 3C. Note that the sub-valve body 4 and the rotor shaft 51 may be formed separately and assembled together.

A case 14 is airtightly fixed to the upper end of the valve housing 1 by welding or the like, and a drive section 5 is configured inside and outside the case 14. The drive unit 5 includes a stepping motor 5A, a screw feeding mechanism 5B that advances and retreats the sub-valve body 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C that restricts the rotation of the stepping motor 5A.

The stepping motor 5A includes a rotor shaft 51, a magnet rotor 52 rotatably disposed inside the case 14, and a stator coil (not shown) disposed opposite to the magnet rotor 52 on the outer periphery of the case 14. In addition, it is composed of a yoke, exterior members, etc. The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male threaded portion 51A is formed on the outer periphery of the upper part of the rotor shaft 51. The male threaded portion 51A is screwed into the female threaded portion 2C of the guide member 2, so that the guide member 2 supports the rotor shaft 51 on the axis L. The female threaded portion 2C of the guide member 2 and the male threaded portion 51A of the rotor shaft 51 constitute a screw feeding mechanism 5B.

A male threaded guide groove 24A is formed on the outer peripheral surface of the stopper portion 24 of the guide member 2, and a slider 52 is provided in the guide groove 24A. The slider 52 contacts the magnet rotor 52, and rotates and moves up and down along the guide groove 24A as the magnet rotor 52 rotates. The slider 52 constitutes a stopper mechanism 5C that restricts the rotation of the magnet rotor 52 by coming into contact with the upper end or lower end of the guide groove 24A. This stopper mechanism 5C regulates the lowest and highest positions of the rotor shaft 51 and the magnet rotor 52.

With the above configuration, when the stepping motor 5A is driven, the magnet rotor 52 and the rotor shaft 51 rotate, and the rotor shaft 51 is moved along with the magnet rotor 52 in the direction of the axis L by the screw feeding mechanism 5B of the male threaded portion 51A and the female threaded portion 2C. Move to. Then, the sub-valve body 4 moves forward and backward in the direction of the axis L, and the needle valve 42 of the sub-valve body 4 approaches or separates from the sub-valve port 3D. Further, when the sub-valve body 4 rises, the washer 43 engages with the retainer 33 of the main valve body 3 (sub-valve upper end position), the main valve body 3 moves together with the sub-valve body 4, and the main valve body 3 The main valve portion 31 is removed from the main valve seat 13. As a result, the main valve port 1B becomes fully open and enters a large flow range state.

As shown in FIGS. 2 and 3, a auxiliary valve seat 36 centered on the axis L is formed around the auxiliary valve port 3D of the main valve body 3. This sub-valve seat 36 is formed in a cylindrical shape and is provided rising upward from the opening 3A. A groove-shaped annular space 3F is formed on the outer peripheral side of the sub-valve seat 36 and is recessed below the upper surface of the sub-valve seat 36. The annular space 3F is located radially inside and above the communication path 3E, continues annularly around the axis L, and is formed to open upward. The annular space 3F has an annular flow passage cross-sectional area illustrated in FIG. 3(A). The annular space 3F has a passage cross-sectional area larger than the sum of the passage cross-sectional areas of the eight communication passages 3E. Further, in order to reliably decelerate the fluid in the annular space 3F as described later, the height of the annular space 3F is preferably greater than the radius of the communication path 3E. A noise reduction member 37 is provided above the annular space 3F, and the upper opening of the annular space 3F is covered by the noise reduction member 37. The sound deadening members 35 and 37 are made of mesh-like or porous members, and the sound deadening member 37 is formed in an annular shape.

The holding member 3C has a generally cylindrical shape as a whole, and includes a fitting portion 38A that protrudes radially outward at its upper end and fits into the inner circumferential surface of the main valve body 3; A cylindrical guide part 38B that extends along the axis L and guides the sub-valve body 4 in the axis L direction, a bottom part 38C that extends radially inward from the lower end of the guide part 38B, and a cylindrical cylinder that extends downward from the radially inner side of the bottom part 38C. It is provided with a shaped extension part 38D. The holding member 3C is fixed by fitting the fitting portion 38A to the inner circumferential surface of the main valve body 3, and holds the muffling member 37 by the bottom portion 38C. Further, a narrow gap is formed between the lower end of the extension portion 38D and the upper surface of the sub-valve seat 36, and this gap forms a throttle passage 3G having a flow passage cross-sectional area smaller than that of the annular space 3F. .

In the small flow rate control region state of the electric valve 10 shown in FIGS. 2 and 3, the main valve port 1B is closed while the main valve body 3 is seated on the main valve seat 13, and the needle valve 42 of the sub valve body 4 is closed. The opening degree of the valve port 3D is controlled, and a small flow rate is controlled. At this time, the refrigerant that has flowed into the main valve chamber 1A from the first joint pipe 11 enters the annular space 3F from the communication path 3E and turns in the annular space 3F, as shown in FIGS. 3(A) and 3(B). After that, it is bent upward in the direction of the axis L, and then passes through the sound deadening member 37. Furthermore, as shown in FIG. 3(C), the refrigerant bends inward in the radial direction while passing through the noise reduction member 37, passes through the throttle passage 3G, enters the sub-valve chamber 3B, and exits the sub-valve chamber 3B. It is narrowed by the gap between the needle valve 42 and the sub-valve port 3D.

4 to 7 are enlarged cross-sectional views showing modifications 1 to 4 of the electric valve 10 of this embodiment, respectively. These Modifications 1 to 4 differ from the above-described embodiments in the form of the holding member 3C and the coolant flow path.

The holding member 3C of Modification 1 shown in FIG. The throttle passage 3G has a smaller (total) cross-sectional area than the flow path 3G. In this modification 1, as described above, the refrigerant that has passed through the muffling member 37 passes through the throttle passage 3G, which is a through hole, and then enters the sub valve chamber 3B.

In the holding member 3C of Modification 2 shown in FIG. 5, the lower end of the extending portion 38D is provided in contact with the upper surface of the sub-valve seat 36, and the through hole provided in the bottom portion 38C allows the flow path to be closer to the annular space 3F. The throttle passage 3G has a small (total) cross-sectional area. In this modification example 2, the refrigerant that has passed through the silencing member 37 flows upward, passes through the throttle passage 3G which is a through hole in the direction of the axis L, enters the sub-valve chamber 3B, and enters the sub-valve chamber 3B in the radial direction. After bending toward the side, it flows to the sub-valve port 3D.

A holding member 3C of modification example 3 shown in FIG. 6 does not include a bottom portion 38C and an extension portion 38D, and holds the lower end of the guide portion 38B in contact with the sound deadening member 37. Further, the sub-valve chamber 3B is provided with an enlarged space 3H whose volume is larger than that of the annular space 3F. In this third modification, the refrigerant that has passed through the muffling member 37 enters the enlarged space 3H, bends radially inward within the enlarged space 3H, and then flows to the sub-valve port 3D.

In the holding member 3C of modification example 4 shown in FIG. 7, the lower end of the extension portion 38D is provided in contact with the upper surface of the sub-valve seat 36, and the guide portion 38B is provided with a through hole 38E as a second communication path. There is. In this modification 4, the refrigerant that has passed through the muffling member 37 is bent radially outward, flows upward through the gap between the inner peripheral surface of the main valve body 3 and the guide portion 38B, and passes through the through hole 38E in the radial direction. Then enter the auxiliary valve chamber 3B. That is, a bent path 3J is provided between the annular space 3F and the sub-valve chamber 3B, which is bent radially outward and further bent in the axis L direction. Note that the passage cross-sectional area of the bent passage 3J is smaller than the passage cross-sectional area of the annular space 3F.

According to the embodiment described above, even if the refrigerant in the main valve chamber 1A is a mixture of gas-phase refrigerant and liquid-phase refrigerant, this refrigerant is decelerated by passing through the annular space 3F, Furthermore, it is stabilized by passing through the silencing member 37, further passing through the throttle passage 3G, the enlarged space 3H, and the bending passage 3J before entering the sub-valve chamber 3B. Therefore, the state of the refrigerant in the auxiliary valve chamber 3B is stabilized, and the sound of the refrigerant passing through the gap between the needle valve 42 and the auxiliary valve port 3D is reduced, and the generation of noise and vibration of the electric valve 10 is reduced. Can be suppressed.

FIG. 8 is an enlarged sectional view showing main parts of an electric valve according to a second embodiment of the present invention. This second embodiment differs from the first embodiment described above in the form of the holding member 3C and the position of the sound deadening member 37. As shown in FIG. 8, the holding member 3C includes a fitting part 38A, a guide part 38B, a bottom part 38C, and a cylindrical extension part 38D extending downward from the middle part of the bottom part 38C. The lower end of the extension part 38D is provided in contact with the upper surface of the sub-valve seat 36, and the through hole 38E provided in the middle of the extension part 38D makes the (total) cross-sectional area of the flow path larger than that of the annular space 3F. A small throttle passage is configured. The muffling member 37 is provided radially inside the extending portion 38D and is held between the bottom portion 38C of the holding member 3C and the upper surface of the sub valve seat 36.

In such an electric valve, as shown in FIG. 8, the refrigerant that has flowed into the main valve chamber 1A enters the annular space 3F from the communication passage 3E, turns in the annular space 3F, and then bends upward in the direction of the axis L. Then, it bends inward in the radial direction, passes through the through hole 38E, and then passes through the muffling member 37. The refrigerant that has passed through the silencing member 37 enters the sub-valve chamber 3B, and is throttled from the sub-valve chamber 3B through the gap between the needle valve 42 and the sub-valve port 3D.

9 to 11 are enlarged cross-sectional views showing modifications 5 to 7 of the electric valve 10 of this embodiment, respectively. These modifications 5 to 7 differ from the second embodiment in the form of the holding member 3C and the provision of a throttle member 39 that throttles the refrigerant from the annular space 3F. The diaphragm member 39 is a plate-shaped member provided so as to cover the upper opening of the annular space 3F, and has through holes 39A vertically penetrating formed therein at multiple locations in the circumferential direction. That is, the through-hole 39A forms a throttle passage whose (total) cross-sectional area of the flow passage is smaller than that of the annular space 3F. These through holes 39A may be provided in the same number and at the same position in the circumferential direction as the communication path 3E, or may be provided in a position shifted from the communication path 3E in the circumferential direction. The muffling member 37 is held between the holding member 3C and the upper surface of the aperture member 39. That is, the aperture member 39 also functions as a first fixing member provided on the annular space 3F side of the sound deadening member 37, and the through hole 39A constitutes a first through hole.

A holding member 3C of modification 5 shown in FIG. 9 has a bottom portion 38C, and the bottom portion 38C is in contact with the upper surface of the aperture member 39. In this modification 5, the refrigerant from the annular space 3F is throttled by the through hole 39A, enters the muffling member 37, bends inward in the radial direction within the muffling member 37, and then enters the auxiliary valve chamber 3B. enter. A holding member 3C according to modification 6 shown in FIG. 10 does not have a bottom portion 38C, and the lower end of the guide portion 38B is in contact with the upper surface of the diaphragm member 39. In this modification 6, the refrigerant from the annular space 3F is throttled by the through hole 39A and then enters the silencing member 37, passes upward through the silencing member 37, and then enters the auxiliary valve chamber 3B. In Modification 7 shown in FIG. 11, the height dimension (volume) of the muffling member 37 is increased compared to the case of FIG. 9, so that the refrigerant is decelerated inside the muffling member 37.

12 and 13 are enlarged cross-sectional views showing modifications 8 and 9 of the electric valve 10 of this embodiment, respectively. These modified examples 8 and 9 differ from the above-mentioned embodiments in that they are provided with a fixing member 60 that holds the sound deadening member 37, and the above-mentioned washer 43 is omitted, and the retainer 33 allows the holding member 3C to be attached to the main valve body 3. It is fixed in the holding part 32 of. The fixing member 60 includes, inside the main valve body 3, a first fixing member 61 provided on the annular space 3F side, and a second fixing member 62 provided on the opposite side of the first fixing member 61 with the silencing member 37 in between. ,have. In the fixing member 60, the first fixing member 61 and the second fixing member 62 sandwich the muffling member 37 from both sides in the direction of the axis L, and the second fixing member 62 is fixed to the axis by the holding member 3C press-fitted into the main valve body 3. The sound deadening member 37 is held by being pressed downward in the L direction.

The first fixing member 61 is formed in an annular shape in a plan view, and has a bottom portion 61A that abuts the bottom surface of the sound deadening member 37 and covers the upper opening of the annular space 3F, and faces a radially inner side surface of the sound deadening member 37. It is formed into a substantially L-shaped cross section and has a wall portion 61B that abuts against the wall portion 61B. In the bottom portion 61A of the first fixing member 61, first through holes 61C communicating with the annular space 3F are provided at a plurality of locations along the circumferential direction. These first through holes 61C function as throttle passages that throttle the refrigerant from the annular space 3F, and may be provided in the same number and at the same position in the circumferential direction as the communication passages 3E, or may be provided in the same number and at the same position in the circumferential direction as the communication passages 3E. It may be provided at a position shifted in the circumferential direction. Further, at least one of the first fixing member 61 and the second fixing member 62 is an elastic member, and in Modifications 8 and 9, the second fixing member 62 is an elastic member and is pressed by the holding member 3C. It is pressed against the sound deadening member 37 while being elastically deformed and crushed in the direction of the axis L.

The radial width of the second fixing member 62 of Modification 8 shown in FIG. 12 is smaller than the radial width of the sound deadening member 37, and is in contact with the upper surface of the sound deadening member 37 on the outer peripheral side. The upper surface of the inner peripheral side of the sound deadening member 37 is not covered, and the refrigerant from the annular space 3F enters the sound deadening member 37 after being squeezed by the first through hole 61C, rises inside the sound deadening member 37, and flows into the second through hole 61C. It enters the sub-valve chamber 3B from the inner peripheral side of the fixed member 62 and is bent radially inward within the sub-valve chamber 3B. The second fixing member 62 of Modified Example 9 shown in FIG. 13 is provided so as to come into contact with substantially the entire upper surface of the muffling member 37, and is provided with a second through hole 62A that communicates with the sub-valve chamber 3B. The height of the wall 61 of the first fixing member 61 is smaller than the height of the sound deadening member 37, and the side surface of the sound deadening member 37 above the tip (upper end) of the wall 61 is smaller than the height of the sound deadening member 37. A gap is provided between the upper end of the wall portion 61 and the radially inner end of the second fixing member 62 . In this modified example 9, the refrigerant from the annular space 3F is throttled through the first through hole 61C, enters the sound deadening member 37, passes through the sound deadening member 37 upward, and is throttled again through the second through hole 62A. It enters the auxiliary valve chamber 3B. In addition, some of the refrigerant that has passed through the silencing member 37 may enter the sub-valve chamber 3B through the gap between the upper end of the wall 61 of the first fixing member 61 and the radially inner end of the second fixing member 62. be.

According to the above-mentioned modifications 8 and 9, the sound deadening member 37 is held between the first fixing member 61 and the second fixing member 62 of the fixing member 60, thereby increasing the retainability of the sound deadening member 37. be able to. Further, since the wall portion 61B of the first fixing member 61 comes into contact with the radially inner side surface of the sound deadening member 37, the radial retainability of the sound deadening member 37 can also be improved. In particular, as in Modification 9, the flow path passes upward through the muffling member 37 and enters the auxiliary valve chamber 3B via the second through hole 62A, and the flow path passes through the wall portion 61 in the radial direction (i.e., the wall portion Silence can be improved by dispersing the refrigerant by branching the flow path into the flow path that enters the sub valve 3B (via the gap between the upper end of the portion 61 and the second fixing member 62). Furthermore, the state of the refrigerant in the sub-valve chamber 3B is stabilized because the first through-hole 61C functions as a throttle passage whose (total) cross-sectional area of the flow path is smaller than that of the annular space 3F. Furthermore, since at least one of the first fixing member 61 and the second fixing member 62 is made of an elastic member, the sound deadening member 37 can be pressed and held in the direction of the axis L, and the retainability of the sound deadening member 37 can be improved. It can be further improved.

In this embodiment as well, the refrigerant is decelerated by passing through the annular space 3F, is further throttled by the through holes 38E, 39A and the first through hole 61C, and then passes through the silencing member 37, and then enters the auxiliary valve chamber 3B. It is stabilized by entering. Furthermore, as in Modified Example 9, the refrigerant that has passed through the muffling member 37 is transmitted through the second through hole 62A of the second fixing member 62, the upper end of the wall 61 of the first fixing member 61, and the second fixing member 62. It is stabilized by entering the auxiliary valve chamber 3B after being squeezed through the gap between the valves. Therefore, the state of the refrigerant in the auxiliary valve chamber 3B is stabilized, and the sound of the refrigerant passing through the gap between the needle valve 42 and the auxiliary valve port 3D is reduced, and the generation of noise and vibration of the electric valve 10 is reduced. Can be suppressed.

Note that the present invention is not limited to the embodiments described above, and includes other configurations that can achieve the object of the present invention, and the present invention also includes the following modifications. Further, the electric valve of the present invention may be used in air conditioners such as home air conditioners and commercial air conditioners, and is applicable not only to air conditioners but also to various types of refrigerators.

In the electric valve 10 of the embodiment, the sub-valve seat 36 and the sub-valve port 3D are integrally formed on the main valve body 3, but the present invention is not limited to this, and the valve seat member having the sub-valve port may be separate from the main valve body. The valve seat member may be provided in the main valve body, and the valve seat member may be assembled to the main valve body.

Further, in the electric valve 10 of the embodiment, a holding member 3C is provided inside the main valve body 3, and the holding member 3C guides the sub-valve body 4, and the holding member 3C holds the muffling member 37. However, the present invention is not limited to this, and the guide portion 38B that guides the sub-valve body 4 from the holding member 3C may be eliminated, and the sub-valve body may be guided by the inner peripheral surface of the main valve body. Furthermore, the holding member that holds the sound deadening member 37 may be formed of a washer-like member.

Further, although the drive unit 5 of the electric valve 10 of the embodiment described above includes a stepping motor 5A, a screw feeding mechanism 5B, and a stopper mechanism 5C, the configuration of each of these parts is not limited to that of the embodiment described above. , any type of mechanism may be employed.

Although the embodiments of the present invention have been described above in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the design may be changed without departing from the gist of the present invention. Even if there is, it is included in the present invention.

1 Valve housing (valve body)
1A Main valve chamber 1B Main valve port 2 Guide member 3 Main valve body 3B Sub-valve chamber 3C Holding member 3D Sub-valve port 3E Communication passage 3F Annular space 3G Throttle passage 3H Expansion space 3J Bend passage 4 Sub-valve body 37 Silence member 38E Penetration Hole (throttle passage, second communication passage)
39 Aperture member (first fixed member)
39A Through hole (throttle passage, first through hole)
42 Needle valve 60 Fixing member 61 First fixing member 61A Bottom part 61B Wall part 61C First through hole (throttling passage)
62 Second fixing member 62A Second through hole (throttle passage)

Claims (13)

A valve body that constitutes a main valve chamber and a main valve port, a main valve body that is provided in the main valve chamber and opens and closes the main valve port, and a auxiliary valve chamber that is formed in the main valve body and moves in the axial direction. a freely provided sub-valve body, the main valve body closes the main valve port, and the opening degree of the sub-valve port provided on the main valve body is controlled by a needle valve of the sub-valve body. By doing so, the motor-operated valve has a small flow rate control region that throttles the flow rate of fluid in the gap between the needle valve and the auxiliary valve port,
The main valve body is formed with a communication passage that opens toward the main valve chamber, and an annular space that continues in an annular shape around an axis between the communication passage and the auxiliary valve chamber,
A noise-reducing member is provided between the annular space and the sub-valve chamber to allow fluid to pass therethrough and muffle the noise.
In the small flow rate control region, the fluid flowing from the main valve chamber to the main valve port enters the annular space from the communication passage, turns in the annular space, bends in the axial direction, and passes through the sound deadening member. The motor-operated valve is characterized in that the motor-operated valve enters the auxiliary valve chamber from the auxiliary valve chamber, and is throttled from the auxiliary valve chamber by a gap between the needle valve and the auxiliary valve port. The motor-operated valve according to claim 1, wherein the annular space has a flow cross-sectional area larger than a total cross-sectional area of the communication passages. 3. The motor-operated valve according to claim 1, wherein a throttle passageway having a smaller cross-sectional area than the annular space is provided between the annular space and the auxiliary valve chamber. The electric valve according to any one of claims 1 to 3, wherein the auxiliary valve chamber is provided with an enlarged space whose volume is larger than that of the annular space. According to any one of claims 1 to 4, a bending path is provided between the annular space and the auxiliary valve chamber, the bending path bending outward in the radial direction and further bending in the axial direction. electric valve. A holding member that holds the sound deadening member is provided within the main valve body,
A part of the bending path is constituted by a gap between an inner circumferential surface of the main valve body and an outer circumferential surface of the holding member,
The motor-operated valve according to claim 5, wherein the holding member is provided with a second communication passage that communicates the bending passage with the auxiliary valve chamber. A fixing member that holds the sound deadening member is provided within the main valve body,
The fixing member has a first fixing member provided on the annular space side, and the first fixing member is provided with a first through hole communicating with the annular space. The electric valve according to any one of 1 to 5. The motor-operated valve according to claim 7, wherein the first fixing member has a bottom portion that comes into contact with a bottom surface of the sound deadening member, and a wall portion that faces a side surface of the sound deadening member. The first through hole is provided in the bottom, the height of the wall is smaller than the height of the sound deadening member, and the side surface of the sound deadening member beyond the tip of the wall is The electric valve according to claim 8, wherein the electric valve is exposed. The fixing member includes a second fixing member provided on the opposite side of the first fixing member with the sound-deadening member interposed therebetween, and the first fixing member and the second fixing member make it possible to secure the sound-deadening member from both sides in the axial direction. The electric valve according to any one of claims 7 to 9, wherein the electric valve is held by sandwiching the valve. 11. The second fixing member is provided in contact with substantially the entire surface of one surface of the sound deadening member, and is provided with a second through hole that communicates with the sub-valve chamber. Electric valve. A radial width dimension of the second fixing member is smaller than a radial width dimension of the sound deadening member, and the second fixing member is provided in partial contact with one surface of the sound deadening member. 12. The motor-operated valve according to claim 11. The electric valve according to any one of claims 10 to 12, wherein at least one of the first fixing member and the second fixing member is an elastic member.

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