JP2022094879A - Motor valve - Google Patents

Abstract

To provide a motor valve which stabilizes a state of a fluid in a sub valve chamber in a low flow rate control area state to reduce a fluid passing sound of a sub valve port and inhibit generation of noise and vibration.SOLUTION: A motor valve 10 includes: a valve housing forming a main valve chamber 1A and a main valve port 1B; a main valve body 3 which is provided in the main valve chamber 1A and opens or closes the main valve port 1B; and a sub valve body 4 which is provided so as to be movable in an axis L direction in a sub valve chamber 3B formed in the main valve body 3. The main valve body 3 is formed with: a communication passage 3E which is open to the main valve chamber 1A; and an annular space 3F which continues in an annular form around an axis L between the communication passage 3E and the sub valve chamber 3B. A sound deadening member 37 which allows the fluid to pass therethrough to suppress sounds is provided between the annular space 3F and the sub valve chamber 3B.SELECTED DRAWING: Figure 2

Description

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

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

Japanese Unexamined Patent Publication No. 2020-106086

However, in the conventional electric valve as described in Patent Document 1, when the liquid phase is mixed in the gas phase of the refrigerant flowing into the communication passage and the state of the refrigerant is unstable, the port throttle is performed without the refrigerant being stable. There is a problem that the sound of passing the refrigerant in the port throttle portion increases when the liquid flows into the portion.

An object of the present invention is to set the main valve port in a fully closed state in the main valve body, and control the flow rate of the fluid in a small flow rate control range by the gap between the sub-valve port provided in the main valve body and the sub-valve body. It is an object of the present invention to provide an electric valve capable of stabilizing the fluid state in the auxiliary valve chamber, reducing the fluid passing noise of the auxiliary valve port, and suppressing the generation of noise and vibration of the electric valve. ..

The electric valve of the present invention includes a valve body constituting the main valve chamber and the main valve port, a main valve body provided in the main valve chamber to open and close the main valve port, and a sub-valve formed in the main valve body. A sub-valve body provided so as to be movable in the axial direction in the valve chamber is provided, 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 adjusted. It is an electric valve having a small flow rate control range that throttles the flow rate of fluid in the gap between the needle valve and the auxiliary valve port by controlling with the needle valve of the valve body, and the main valve body has the main valve. A continuous passage that opens toward the chamber and an annular space that is annularly continuous around the axis between the continuous passage and the auxiliary valve chamber are formed, and between the annular space and the auxiliary valve chamber. Is provided with a muffling member that allows the fluid to pass through and muffles the sound. In the small flow control area, the fluid from the main valve chamber to the main valve port enters the annular space from the communication passage and enters the annular space. After turning, it bends in the axial direction, passes through the sound deadening 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 as described above, in the small flow rate control range, the fluid from the main valve chamber to the main valve port enters the annular space from the communication passage, swirls in the annular space, and then bends in the axial direction to form a muffling member. By entering the auxiliary valve chamber after passing through, the fluid swirling in the annular space is decelerated, further bent in the axial direction, and then passed through the muffling member to muffle the sound. Therefore, the state of the fluid is stabilized by the time it enters the auxiliary valve chamber, the noise of the fluid passing through the gap between the auxiliary valve port and the needle valve of the auxiliary valve body is reduced, and the noise and vibration of the motorized valve are suppressed. can do.

At this time, it is preferable that the annular space has a flow path cross section larger than the total flow path cross section of the communication passage.

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

Further, it is preferable that the auxiliary valve chamber is provided with an enlarged space having a larger volume than the annular space.

Further, it is preferable that a bending path that is bent outward in the radial direction and further bent in the axial direction is provided between the annular space and the auxiliary valve chamber.

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

Further, a fixing member for holding the sound deadening 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 has the said. It is preferable that the first through hole communicating with the annular space is provided.

Further, it is preferable that the first fixing member has a bottom portion that abuts on the bottom surface of the sound deadening member and a wall portion that faces the side surface of the sound deadening member. Further, the first through hole is provided in the bottom portion, the height dimension of the wall portion is formed to be smaller than the height dimension of the muffling member, and the muffling member beyond the tip end portion of the wall portion. It is preferable that the sides are exposed.

Further, 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 are used from both sides in the axial direction. It is preferable to sandwich and hold the sound deadening member. Further, 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 communicating with the auxiliary valve chamber. Further, the radial width dimension of the second fixing member is formed to be smaller than the radial width dimension of the sound deadening member, and the second fixing member is provided so as to be partially in contact with one surface of the sound deadening member. It may have been.

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

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

It is a vertical sectional view which shows the electric valve of 1st Embodiment of this invention. It is an enlarged sectional view which shows the main part of the small flow rate control range state of the electric valve. It is a figure which shows the flow of the fluid in the small flow rate control range state of the electric valve. It is an enlarged sectional view which shows the modification 1 of the electric valve. It is an enlarged sectional view which shows the modification 2 of the electric valve. It is an enlarged sectional view which shows the modification 3 of the electric valve. It is an enlarged sectional view which shows the modification 4 of the electric valve. It is an enlarged sectional view which shows the main part of the electric valve of the 2nd Embodiment of this invention. It is sectional drawing which shows the modification 5 of the electric valve. It is an enlarged sectional view which shows the modification 6 of the electric valve. It is an enlarged sectional view which shows the modification 7 of the electric valve. It is an enlarged sectional view which shows the modification 8 of the electric valve. It is an enlarged sectional view which shows the modification 9 of the electric valve.

An embodiment of the motorized valve of the present invention will be described with reference to the drawings. FIG. 1 is a vertical sectional view showing an electric valve according to the first embodiment of the present invention, FIG. 2 is an enlarged sectional view showing a main part of a small flow rate control range state (secondary valve lower end position) of the electric valve, and FIG. 3 is an electric valve. It is a figure which shows the flow of the refrigerant (fluid) in the small flow rate control range state of. The concept of "up and down" in the following description corresponds to the up and down in FIG. 1, and the up and down direction may be referred to as the axis L direction, and the direction orthogonal to the axis L may be referred to as the radial direction. In addition, in the second and subsequent embodiments described later, members and parts that are the same as or similar to those of the first embodiment are designated by a common reference numeral, and the description may be omitted or abbreviated.

The motorized valve 10 of the present embodiment includes a valve housing 1 which is a valve main body, a guide member 2, a main valve body 3, a sub valve body 4, and a drive unit 5.

The valve housing 1 is formed of, for example, brass, stainless steel, or the like in a substantially cylindrical shape, and has a main valve chamber 1A inside thereof. A first joint pipe 11 conducting to the main valve chamber 1A is connected to one side of the outer periphery 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 the main valve seat 13 is the 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 conducted to the main valve chamber 1A via the main valve port 1B. In the present embodiment, the main valve seat 1B is integrally formed with the valve housing 1, but the valve seat member having the main valve port is provided separately from the valve housing, and the valve seat member is provided in the valve housing. It may be assembled in the form of.

A guide member 2 is attached to the opening at the upper end of the valve housing 1. The guide member 2 includes a fitting portion 21 fitted in the inner peripheral surface of the valve housing 1, a substantially columnar guide portion 22 located inside the fitting portion 21 and centered on the axis L, and a guide. It has a holder portion 23 extended to the upper part of the portion 22, a stopper portion 24 provided above the holder portion 23, and a ring-shaped fixing bracket 25 made of a metal plate protruding from the outer periphery of the fitting portion 21. is doing. The fitting portion 21, the upper guide portion 22, the holder portion 23, and the stopper portion 24 are configured as an integral product made of resin, and the fixing bracket 25 is provided integrally with the fitting portion 21 made of resin by insert molding. ing. 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 by the fitting portion 21, and is fixed to the upper end portion of the valve housing 1 by welding via the fixing bracket 25. Further, in the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the fitting portion 21 and the guide portion 22, and the center of the holder portion 23 is coaxial with the guide hole 2A. An insertion hole 2B for guiding the rotor shaft 51 (described later) is formed, and the stopper portion 24 is coaxial with the guide hole 2A and the insertion hole 2B and is screwed with the male screw portion 51A (described later) of the rotor shaft 51. A matching female screw portion 2C is formed. Then, the main valve body 3 is arranged in the guide hole 2A, and the main valve body 3 is guided forward and backward in the axis L direction by the guide hole 2A.

The main valve body 3 includes a main valve portion 31 that sits and leaves the main valve seat 13, and a holding portion 32 that is a side wall of the main valve body 3 and holds the auxiliary valve body 4. Has been done. A columnar opening 3A is formed inside the main valve portion 31, and a columnar sub-valve chamber 3B is formed inside the holding portion 32, and a muffling described later is performed inside the sub-valve chamber 3B. A holding member 3C for holding the member 37 in the main valve body 3 is provided. A columnar sub-valve port 3D that opens from the sub-valve chamber 3B to the opening 3A side with the axis L as the center is formed between the main valve portion 31 and the holding portion 32.

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

The auxiliary valve body 4 is integrally provided at the lower end portion of the rotor shaft 51. The auxiliary 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 in the axis L direction with respect to the sub-valve port 3D, 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 a lubricating resin is disposed at the upper end of the guide boss portion 41, and the guide boss portion 41 is inserted into the holding member 3C. Then, the outer peripheral surface of the guide boss portion 41 is in sliding contact with the inner peripheral surface of the holding member 3C to be guided. The auxiliary valve body 4 and the rotor shaft 51 may be formed separately and assembled.

A case 14 is airtightly fixed to the upper end of the valve housing 1 by welding or the like, and a drive unit 5 is configured inside and outside the case 14. The drive unit 5 includes a stepping motor 5A, a screw feed mechanism 5B for advancing and retreating the auxiliary valve body 4 by the rotation of the stepping motor 5A, and a stopper mechanism 5C for restricting the rotation of the stepping motor 5A.

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

A male screw-shaped guide groove 24A is formed on the outer peripheral surface of the stopper portion 24 of the guide member 2, and the guide groove 24A is provided with a slider 52. The slider 52 abuts on 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 abuts on the upper end or the lower end of the guide groove 24A to form a stopper mechanism 5C that regulates the rotation of the magnet rotor 52. The stopper mechanism 5C regulates the lowermost and uppermost 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 screw feed mechanism 5B between the male screw portion 51A and the female screw portion 2C causes the rotor shaft 51 to move in the axis L direction together with the magnet rotor 52. Move to. Then, the sub-valve body 4 moves back and forth in the axis L direction, 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 (at the upper end position of the sub-valve), and the main valve body 3 moves together with the sub-valve body 4 to move the main valve body 3 together. The main valve portion 31 of the above is separated from the main valve seat 13. As a result, the main valve port 1B is fully opened and a large flow rate range is established.

As shown in FIGS. 2 and 3, a sub-valve seat 36 centered on the axis L is formed around the sub-valve port 3D of the main valve body 3. The auxiliary valve seat 36 is formed in a cylindrical shape and is provided so as to rise upward from the opening 3A. On the outer peripheral side of the sub-valve seat 36, a groove-shaped annular space 3F recessed below the upper surface of the sub-valve seat 36 is formed. The annular space 3F is located inside and above the radial direction of the communication passage 3E, is continuous in an annular shape around the axis L, and is formed by opening upward. The annular space 3F has an annular flow path cross section illustrated in FIG. 3 (A). The annular space 3F has a flow path cross section larger than the total of the flow path cross sections of the eight continuous passages 3E. Further, as will be described later, in order to reliably decelerate the fluid in the annular space 3F, it is preferable that the height of the annular space 3F is larger than the radius of the communication passage 3E. A sound deadening member 37 is provided on the upper side of the annular space 3F, and the upper opening of the annular space 3F is covered with the sound deadening member 37. The sound deadening members 35 and 37 are made of a mesh-like or porous member, and the sound deadening member 37 is formed in an annular shape.

The holding member 3C is formed in a substantially cylindrical shape as a whole, and has a fitting portion 38A that projects radially outward at the upper end thereof and fits to the inner peripheral surface of the main valve body 3, and an inner peripheral surface of the main valve body 3. A cylindrical guide portion 38B extending along the axis L to guide the auxiliary valve body 4 in the axial direction L, a bottom portion 38C extending radially inward from the lower end portion of the guide portion 38B, and a cylinder extending downward from the radial inside of the bottom portion 38C. It is provided with a shaped extension 38D. The holding member 3C is fixed by fitting the fitting portion 38A to the inner peripheral surface of the main valve body 3, and the muffling member 37 is held 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 auxiliary valve seat 36, and this gap constitutes a throttle passage 3G having a flow path cross-sectional area smaller than that of the annular space 3F. ..

In the small flow rate control range state of the motorized valve 10 shown in FIGS. The opening degree of the valve port 3D is controlled, and the small flow rate is controlled. At this time, as shown in FIGS. 3A and 3B, the refrigerant flowing into the main valve chamber 1A from the first joint pipe 11 enters the annular space 3F from the communication passage 3E and swirls in the annular space 3F. After that, it bends upward in the L direction of the axis and then passes through the sound deadening member 37. Further, as shown in FIG. 3C, the refrigerant bends inward in the radial direction while passing through the muffling member 37, passes through the throttle passage 3G, enters the sub-valve chamber 3B, and enters the sub-valve chamber 3B from the sub-valve chamber 3B. It is throttled by the gap between the needle valve 42 and the auxiliary valve port 3D.

4 to 7 are enlarged cross-sectional views showing modified examples 1 to 4 of the motorized valve 10 of the present embodiment, respectively. The differences between these modifications 1 to 4 from the above-described embodiment are the form of the holding member 3C and the flow path of the refrigerant.

The holding member 3C of the modified example 1 shown in FIG. 4 is provided with the lower end of the extending portion 38D in contact with the upper surface of the auxiliary valve seat 36, and the annular space 3F is provided by a through hole provided in the middle of the extending portion 38D. A throttle passage 3G having a smaller flow path cross-sectional area (total) is configured. In the first modification, 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 auxiliary valve chamber 3B, as described above.

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

The holding member 3C of the modification 3 shown in FIG. 6 does not have the bottom portion 38C and the extending portion 38D, and holds the lower end of the guide portion 38B in contact with the sound deadening member 37. Further, the auxiliary valve chamber 3B is provided with an enlarged space 3H whose volume is larger than that of the annular space 3F. In the third modification, the refrigerant that has passed through the muffling member 37 enters the enlarged space 3H, bends inward in the radial direction in the expanded space 3H, and then flows to the auxiliary valve port 3D.

The holding member 3C of the modified example 4 shown in FIG. 7 is provided with the lower end of the extending portion 38D abutting on the upper surface of the auxiliary valve seat 36, and the guide portion 38B is provided with a through hole 38E as a second continuous passage. There is. In this modification 4, the refrigerant that has passed through the muffling member 37 bends 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 bending path 3J that is bent outward in the radial direction and further bent in the axis L direction is provided between the annular space 3F and the auxiliary valve chamber 3B. The cross-sectional area of the flow path of the bent path 3J is smaller than the cross-sectional area of the flow path of the annular space 3F.

According to the above embodiment, even if the refrigerant in the main valve chamber 1A is in a state where the liquid phase refrigerant is mixed with the gas phase refrigerant, this refrigerant is decelerated by passing through the annular space 3F. Further, it is stabilized by passing through the sound deadening member 37, further passing through the throttle passage 3G, the expansion space 3H, and the bending path 3J, and then entering the auxiliary valve chamber 3B. Therefore, the state of the refrigerant in the auxiliary valve chamber 3B is stabilized, the refrigerant passing noise when passing through the gap between the needle valve 42 and the auxiliary valve port 3D is reduced, and the noise and vibration of the electric valve 10 are generated. It can be suppressed.

FIG. 8 is an enlarged cross-sectional view showing a main part of the motorized valve according to the second embodiment of the present invention. In this second embodiment, the difference from the above-mentioned first embodiment is the form of the holding member 3C and the position of the muffling member 37. As shown in FIG. 8, the holding member 3C includes a fitting portion 38A, a guide portion 38B, a bottom portion 38C, and a cylindrical extending portion 38D extending downward from the intermediate portion of the bottom portion 38C. The lower end of the extension portion 38D is provided in contact with the upper surface of the auxiliary valve seat 36, and the through hole 38E provided in the middle of the extension portion 38D makes the flow path cross-sectional area (total) of the annular space 3F larger than that of the annular space 3F. A small aperture passage is constructed. The sound deadening 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 auxiliary valve seat 36.

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

9 to 11 are enlarged cross-sectional views showing modified examples 5 to 7 in the motorized valve 10 of the present embodiment, respectively. The differences between the modified examples 5 to 7 and the second embodiment are that the holding member 3C is provided and the drawing member 39 for squeezing the refrigerant from the annular space 3F is provided. The diaphragm member 39 is a plate-shaped member provided so as to cover the upper opening of the annular space 3F, and through holes 39A penetrating vertically are formed at a plurality of locations in the circumferential direction. That is, the through hole 39A constitutes a throttle passage having a smaller (total) cross-sectional area of the flow path than the annular space 3F. These through holes 39A may be provided in the same number as the communication passage 3E at the same position in the circumferential direction, or may be provided at a position deviated from the communication passage 3E in the circumferential direction. The sound deadening member 37 is held between the holding member 3C and the upper surface of the throttle member 39. That is, the diaphragm member 39 also functions as a first fixing member provided on the annular space 3F side of the sound deadening member 37, and the first through hole is formed by the through hole 39A.

The holding member 3C of the modified example 5 shown in FIG. 9 has a bottom portion 38C, and the bottom portion 38C is in contact with the upper surface of the drawing member 39. In this modification 5, the refrigerant from the annular space 3F is squeezed by the through hole 39A and then enters the sound deadening member 37, bends inward in the sound deadening member 37, passes through, and then enters the auxiliary valve chamber 3B. come in. The holding member 3C of the 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 drawing member 39. In this modification 6, the refrigerant from the annular space 3F enters the muffling member 37 after being squeezed by the through hole 39A, passes upward through the muffling member 37, and then enters the auxiliary valve chamber 3B. In the modified example 7 shown in FIG. 11, the height dimension (volume) of the sound deadening member 37 is larger than that in the case of FIG. 9, and the refrigerant is decelerated inside the sound deadening member 37.

12 and 13 are enlarged cross-sectional views showing modifications 8 and 9 of the motorized valve 10 of the present embodiment, respectively. In these modified examples 8 and 9, the point that the fixing member 60 for holding the sound deadening member 37 is provided is different from the above-described embodiment, the washer 43 described above is omitted, and the holding member 3C is the main valve body 3 by the retainer 33. It is fixed in the holding portion 32 of. The fixing member 60 includes a first fixing member 61 provided on the annular space 3F side inside the main valve body 3 and a second fixing member 62 provided on the opposite side of the first fixing member 61 with the sound deadening member 37 interposed therebetween. ,have. In the fixing member 60, the muffling member 37 is sandwiched between the first fixing member 61 and the second fixing member 62 from both sides in the L direction of the axis, and the second fixing member 62 has the axis line 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 faces the bottom portion 61A that abuts on the bottom surface of the sound deadening member 37 and covers the upper opening of the annular space 3F and the radial inner side surface of the sound deadening member 37. It has a wall portion 61B that comes into contact with the wall portion 61B, and is formed in a substantially L-shaped cross section. The bottom portion 61A of the first fixing member 61 is provided with first through holes 61C communicating with the annular space 3F at a plurality of locations along the circumferential direction. These first through holes 61C function as throttle passages for squeezing the refrigerant from the annular space 3F, and may be provided in the same number as the communication passages 3E at the same position in the circumferential direction, or may be provided at the same position in the circumferential direction. It may be provided at a position deviated from 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 the modified examples 8 and 9, the second fixing member 62 is an elastic member and is pressed by the holding member 3C. It is elastically deformed in the L direction of the axis and crushed while being pressed against the sound deadening member 37.

The radial width dimension of the second fixing member 62 of the modification 8 shown in FIG. 12 is formed to be smaller than the radial width dimension of the sound deadening member 37, and is in contact with the upper surface on the outer peripheral side of the sound deadening member 37. The upper surface of the sound deadening member 37 on the inner peripheral side 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, and rises in the sound deadening member 37 to the second. It enters the sub-valve chamber 3B from the inner peripheral side of the fixing member 62, and bends inward in the radial direction in the sub-valve chamber 3B. The second fixing member 62 of the modified example 9 shown in FIG. 13 is provided in contact with substantially the entire upper surface of the sound deadening member 37, and is provided with a second through hole 62A communicating with the auxiliary valve chamber 3B. Further, the height dimension of the wall portion 61 of the first fixing member 61 is formed to be smaller than the height dimension of the muffling member 37, and the side surface of the muffling member 37 above the tip end portion (upper end portion) of the muffling member 61 is formed. It is exposed, and a gap is provided between the upper end portion of the wall portion 61 and the radial inner end portion of the second fixing member 62. In this modification 9, the refrigerant from the annular space 3F is squeezed by the first through hole 61C and then enters the muffling member 37, passes upward through the muffling member 37, and then is squeezed again by the second through hole 62A. Enter the auxiliary valve chamber 3B from. Further, a part of the refrigerant that has passed through the muffling member 37 may enter the auxiliary valve chamber 3B through the gap between the upper end portion of the wall portion 61 of the first fixing member 61 and the radial inner end portion of the second fixing member 62. be.

According to the above modification 8 and 9, the sound deadening member 37 is sandwiched and held by the first fixing member 61 and the second fixing member 62 of the fixing member 60, thereby enhancing the holding property of the sound deadening member 37. be able to. Further, the wall portion 61B of the first fixing member 61 comes into contact with the radial inner side surface of the sound deadening member 37, so that the radial holding property of the sound deadening member 37 can be improved. In particular, as in the modified example 9, the flow path that passes upward through the sound deadening member 37 and enters the auxiliary valve chamber 3B through the second through hole 62A and the wall portion 61 pass radially (that is, the wall). Quietness can be improved by dispersing the refrigerant in the flow path entering the auxiliary valve 3B (via the gap between the upper end portion of the portion 61 and the second fixing member 62). Further, the first through hole 61C functions as a throttle passage having a smaller cross-sectional area (total) of the flow path than the annular space 3F, thereby stabilizing the state of the refrigerant in the auxiliary valve chamber 3B. Further, since at least one of the first fixing member 61 and the second fixing member 62 is composed of an elastic member, the sound deadening member 37 can be pressed and held in the axis L direction, and the holding property of the sound deadening member 37 can be improved. It can be further enhanced.

Also in the above embodiment, the refrigerant is decelerated by passing through the annular space 3F, is further squeezed by the through holes 38E and 39A and the first through hole 61C, passes through the muffling member 37, and then enters the auxiliary valve chamber 3B. It is stabilized by entering. Further, as in the modified example 9, the refrigerant that has passed through the sound deadening member 37 includes the second through hole 62A of the second fixing member 62, the upper end portion of the wall portion 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 in the gap of. Therefore, the state of the refrigerant in the auxiliary valve chamber 3B is stabilized, the refrigerant passing noise when passing through the gap between the needle valve 42 and the auxiliary valve port 3D is reduced, and the noise and vibration of the electric valve 10 are generated. It can be suppressed.

The present invention is not limited to the above embodiment, but includes other configurations and the like that can achieve the object of the present invention, and the present invention also includes modifications and the like as shown below. Further, the electric valve of the present invention may be used in an air conditioner such as a household air conditioner or a commercial air conditioner, and can be applied not only to an air conditioner but also to various refrigerators and the like.

In the motorized valve 10 of the above 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 is different from the main valve body. It may be provided on the body and the valve seat member may be assembled to the main valve body.

Further, in the motorized valve 10 of the above embodiment, a holding member 3C is provided inside the main valve body 3, the holding member 3C guides the auxiliary 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 for guiding the auxiliary valve body 4 from the holding member 3C may be abolished so that the auxiliary valve body is guided by the inner peripheral surface of the main valve body. Further, the holding member for holding the sound deadening member 37 may be composed of a washer-shaped member.

Further, the drive unit 5 of the motorized valve 10 of the embodiment includes a stepping motor 5A, a screw feed mechanism 5B, and a stopper mechanism 5C, but the configuration of each portion is not limited to that of the embodiment. , Any form of mechanism can be adopted.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the design changes, etc. within the range not deviating from the gist of the present invention, etc. 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 Continuous passage 3F Circular space 3G Squeezing passage 3H Expansion space 3J Bending path 4 Sub valve body 37 Silent member 38E Penetration Hole (squeezing passage, second passage)
39 Aperture member (first fixing member)
39A through hole (throttle passage, first through hole)
42 Needle valve 60 Fixing member 61 First fixing member 61A Bottom 61B Wall 61C First through hole (throttle passage)
62 Second fixing member 62A Second through hole (throttle passage)

Claims (13)

It moves in the axial direction in the valve body constituting the main valve chamber and the main valve port, the main valve body provided in the main valve chamber to open and close the main valve port, and the auxiliary valve chamber formed in the main valve body. It is provided with a freely provided auxiliary valve body, the main valve port is closed by the main valve body, and the opening degree of the auxiliary valve port provided in the main valve body is controlled by the needle valve of the auxiliary valve body. By doing so, it is an electric valve having a small flow rate control range that throttles the flow rate of the 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 is annularly continuous around the axis between the communication passage and the sub-valve chamber.
A muffling member is provided between the annular space and the auxiliary valve chamber to allow a fluid to pass through and muffle the sound.
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 passage, swirls in the annular space, then bends in the axial direction and passes through the muffling member. An electric valve characterized in that it enters the sub-valve chamber and is throttled from the sub-valve chamber by a gap between the needle valve and the sub-valve port. The motorized valve according to claim 1, wherein the annular space has a flow path cross-sectional area larger than the total flow path cross-section of the communication passages. The electric valve according to claim 1 or 2, wherein a throttle passage having a cross-sectional area smaller than that of 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 expanded space having a volume larger than that of the annular space. The invention according to any one of claims 1 to 4, wherein a bending path that is bent outward in the radial direction and further bent in the axial direction is provided between the annular space and the auxiliary valve chamber. Electric valve. A holding member for holding the muffling member is provided in the main valve body.
A part of the bending path is formed by the gap between the inner peripheral surface of the main valve body and the outer peripheral surface of the holding member.
The electric valve according to claim 5, wherein the holding member is provided with a second communication passage that connects the bending path and the auxiliary valve chamber. A fixing member for holding the muffling member is provided in the main valve body.
The claim is characterized in that 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 electric valve according to claim 7, wherein the first fixing member has a bottom portion abutting on a bottom surface of the muffling member and a wall portion facing the side surface of the muffling member. The first through hole is provided in the bottom portion, the height dimension of the wall portion is formed to be smaller than the height dimension of the muffling member, and the side surface of the muffling member ahead of the tip portion of the wall portion is formed. The electric valve according to claim 8, wherein the electric valve is exposed. 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 sound deadening member is provided from both sides in the axial direction by the first fixing member and the second fixing member. The electric valve according to any one of claims 7 to 9, wherein the motorized valve is sandwiched and held. The electric motor according to claim 11, wherein 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 communicating with the auxiliary valve chamber. valve. The radial width dimension of the second fixing member is formed to be smaller than the radial width dimension of the sound deadening member, and the second fixing member is provided so as to partially abut on one surface of the sound deadening member. The electric valve according to claim 11, wherein the valve is provided. 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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