JP6968768B2 - Electric valve and refrigeration cycle system - Google Patents

Description

The present invention relates to an electric valve and a refrigeration cycle system used for 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 the flow rate in a small flow rate control range and a large flow rate control range. Such an electric valve has an application to be mounted on an indoor unit (for example, a dehumidifying valve), and it is necessary to reduce the noise of fluid (refrigerant) flowing when controlling a small flow rate. Therefore, an electric valve in consideration of quietness is disclosed in, for example, Japanese Patent Application Laid-Open No. 2017-211032 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2017-21134 (Patent Document 2).

Japanese Unexamined Patent Publication No. 2017-211032 Japanese Unexamined Patent Publication No. 2017-21134

In the conventional techniques of Patent Documents 1 and 2, the muffling member is arranged so as to intersect the flux of the flow of the refrigerant, and the structure is such that the refrigerant is transmitted through the muffling member. In a structure that allows the refrigerant to permeate as in this conventional technique, the sound deadening member may be clogged by foreign matter such as dust in the refrigerant, which makes it difficult to properly control the flow rate.

The present invention is an electric valve that controls the flow rate in the small flow rate control range and the large flow rate control range. The task is to reduce the passing sound and improve the quietness.

The electric valve according to claim 1 is a main valve body that changes the opening degree of the main valve port of the main valve chamber and a sub-valve body that changes the opening degree of the sub-valve port of the sub-valve chamber provided in the main valve body. And a drive unit that drives the sub-valve body to move forward and backward in the axial direction, and the sub-valve body changes the opening degree of the sub-valve port while the main valve body closes the main valve port. It is an electric valve that controls the flow rate of the fluid in two stages of a small flow rate control area and a large flow rate control area in which the main valve body changes the opening degree of the main valve port. Exposed to the fluid flowing through the sub-valve chamber and the sub-valve port in the flow control area, it constitutes a part of the side wall of the flow path of the fluid, and is provided so as not to block the flow path. It is characterized by having a foam member.

The electric valve according to claim 2 is the electric valve according to claim 1, and the defoaming member is arranged in the auxiliary valve chamber so as not to block the flow path on the wall surface that does not allow the fluid to permeate. It is characterized by being.

The electric valve according to claim 3 is the electric valve according to claim 2, wherein the defoaming member is provided in a part of the auxiliary valve body.

The electric valve according to claim 4 is the electric valve according to claim 2, wherein the defoaming member is provided on the auxiliary valve chamber side around the auxiliary valve port.

The electric valve according to claim 5 is the electric valve according to claim 1, wherein the defoaming member is provided on the side opposite to the auxiliary valve chamber around the auxiliary valve port. do.

The refrigeration cycle system according to claim 6 includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and the indoor heat exchanger. A refrigeration cycle system including a dehumidifying valve provided in a heat exchanger, wherein the electric valve according to any one of claims 1 to 5 is used as the dehumidifying valve.

According to the electric valves of claims 1 to 5, since the defoaming member constitutes a part of the side wall of the flow path of the fluid with respect to the fluid having a small flow rate in the small flow rate control range, this fluid is extinguished. It collides with the foam member and breaks up the bubbles. However, since the defoaming member is a part of the side wall of the flow path, the defoaming member does not block the flow path and does not obstruct the flow of fluid. Therefore, it is possible to secure the flow of the fluid in the small flow rate control range, reduce the passing noise due to the bursting of the bubbles of the fluid, and improve the quietness.

According to the refrigeration cycle system of claim 6, the same effect as that of claims 1 to 5 can be obtained.

It is a vertical sectional view of the electric valve of 1st Embodiment of this invention. It is an enlarged sectional view of the main part of the small flow rate control range state of the electric valve of 1st Embodiment. It is an enlarged sectional view of the main part of the large flow rate control range state of the electric valve of 1st Embodiment. It is an enlarged sectional view of the main part of the small flow rate control range state of the electric valve of the 2nd Embodiment of this invention. It is an enlarged sectional view of the main part of the small flow rate control range state of the electric valve of the 3rd Embodiment of this invention. It is an enlarged sectional view of the main part of the small flow rate control range state of the electric valve of the reference example of this invention. It is a graph which shows the relationship between the valve lift amount and the flow rate in the electric valve of embodiment of this invention. It is a figure which shows the refrigeration cycle system of an embodiment.

Next, an embodiment of the electric valve and the refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the small flow rate control range state of the electric valve of the first embodiment, FIG. 2 is an enlarged cross-sectional view of a main part of the small flow rate control range state of the electric valve of the first embodiment, and FIG. 3 is the first embodiment. It is an enlarged sectional view of the main part of the large flow rate control range state of the electric valve of the form. The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawings of FIGS. 1 to 3. The electric valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "secondary valve body", 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 1R inside thereof. A first joint pipe 11 conducting to the main valve chamber 1R 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 cylindrical main valve seat 13 is formed on the main valve chamber 1R side of the second joint pipe 12, and the inside of the main valve seat 13 is a main valve port 13a, and the second joint pipe 12 is the main valve seat 13. It is conducted to the main valve chamber 1R via the valve port 13a. The main valve port 13a is a cylindrical through hole centered on the axis L. The first joint pipe 11 and the second joint pipe 12 are fixed to the valve housing 1 by brazing or the like.

A guide member 2 is attached to the opening at the upper end of the valve housing 1. The guide member 2 includes a press-fitting portion 21 to be press-fitted into the inner peripheral surface of the valve housing 1, a substantially columnar guide portion 22 located inside the press-fitting portion 21, and a holder extending above the guide portion 22. It has a portion 23 and a ring-shaped flange portion 24 located on the outer periphery of the guide portion 22. The press-fitting portion 21, the guide portion 22, and the holder portion 23 are configured as an integral product made of resin. Further, the flange portion 24 is, for example, a metal plate such as brass or stainless steel, and the flange portion 24 is integrally provided together with the resin press-fitting portion 21 and the holder portion 22 by insert molding.

The guide member 2 is assembled to the valve housing 1 and fixed to the upper end of the valve housing 1 via the flange portion 24 by welding. Further, in the guide member 2, a cylindrical guide hole 22a coaxial with the axis L is formed in the guide portion 22, and a female screw portion 23a coaxial with the guide hole 22a and a screw hole thereof are formed in the center of the holder portion 23. Is formed. The main valve body 3 is arranged in the guide hole 22a of the holder portion 23.

The main valve body 3 has a main valve portion 31 that is seated and separated from the main valve seat 13, a holding portion 32 having a columnar needle guide hole 32a, and a sub valve seat 33. The lower part of the needle guide hole 32a is the auxiliary valve chamber 3R. A washer 43 attached to a valve shaft 41 and a guide boss portion 44, which will be described later, are inserted into the needle guide hole 32a of the holding portion 32, and a ring-shaped retainer 321 is provided at the upper end of the holding portion 32. It is fixed by fitting or welding. Further, the outer peripheral portion of the upper end of the holding portion 32 has a reduced diameter, and a main valve spring 3a is disposed between the outer peripheral portion of the upper end of the holding portion 32 and the upper end portion of the guide hole 22a. The main valve body 3 is urged in the direction (closed direction) of the main valve seat 13 by the valve spring 3a. The auxiliary valve seat 33 is located at the lower end of the needle guide hole 32a, and the auxiliary valve port 33a is formed in the center thereof. The auxiliary valve port 33a has a cylindrical shape centered on the axis L. Further, a conduction hole 32b that conducts the sub-valve chamber 3R and the main valve chamber 1R is formed at at least one position on the side surface of the holding portion 32, and the needle valve 4 as the sub-valve body is subordinate as described later. When the valve port 33a is opened, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a are electrically connected.

The needle valve 4 integrally forms a valve shaft 41 integrally formed with the rotor shaft 51 at the lower end of the rotor shaft 51, which will be described later, and is connected to the rotor shaft 51 side, and a needle portion 42 connected to the lower end of the valve shaft 41. And prepare. The needle portion 42 is composed of a straight portion 42a and a truncated cone portion 42b. The straight portion 42a has a diameter that matches the sub-valve port 33a and can be inserted into the sub-valve port 33a, and its side surface has the same diameter in the axis L direction. The truncated cone portion 42b has a truncated cone shape whose diameter gradually decreases toward the tip. Further, the needle valve 4 has an annular washer 43 arranged on the valve shaft 41 and a guide boss portion 44 fixed to the valve shaft 41. Although the guide boss portion 44 is fixed separately from the valve shaft 41, the guide boss portion 44 may be integrally formed with the valve shaft 41. The washer 43 and the guide boss portion 44 are slidably inserted into the needle guide hole 32a.

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 needle valve 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, a stator coil 53 arranged to face the magnet rotor 52 on the outer circumference of the case 14, and others shown in the figure. It is composed of a yoke and exterior members that do not. 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 rotor shaft 51 on the guide member 2 side. The male threaded portion 51a is screwed into the female threaded portion 23a of the guide member 2, whereby the guide member 2 supports the rotor shaft 51 on the axis L. The female screw portion 23a of the guide member 2 and the male screw portion 51a of the rotor shaft 51 constitute the screw feed mechanism 5B.

With the above configuration, the magnet rotor 52 and the rotor shaft 51 are rotated by driving the stepping motor 5A, and the rotor shaft 51 is rotated by the screw feed mechanism 5B between the male screw portion 51a of the rotor shaft 51 and the female screw portion 23a of the guide member 2. Move in the L direction of the axis. Then, the needle valve 4 moves back and forth in the axis L direction, and the needle valve 4 approaches or separates from the auxiliary valve port 33a. Thereby, the opening degree of the auxiliary valve port 33a is controlled. Further, the needle valve 4 (washer 43) engages with the main valve body 3 (retainer 321), and the main valve body 3 moves together with the needle valve 4 to sit and leave the main valve seat 13. As a result, the flow rate of the refrigerant flowing from the first joint pipe 11 to the second joint pipe 12 or from the second joint pipe 12 to the first joint pipe 11 is controlled. A protrusion 52a is formed on the magnet rotor 52, and the protrusion 52a operates the rotation stopper mechanism 5C as the magnet rotor 52 rotates, so that the lowermost position and the uppermost end of the rotor shaft 51 (and the magnet rotor 52) are formed. The position is regulated. 1 and 2 show a state in which the rotor shaft 51 (and the magnet rotor 52) is at the lowermost position.

FIG. 7 is a graph showing the relationship between the pulse amount (= valve opening degree) of the drive pulse in the stepping motor 5A and the flow rate, and the above electric valve 100 operates as follows. First, in the state of FIG. 2 (and FIG. 1), the main valve portion 31 of the main valve body 3 is seated on the main valve seat 13, and the main valve port 13a is closed. On the other hand, in the needle valve 4 at the first position closest to the sub-valve port 33a, the straight portion 42a is inserted into the sub-valve port 33a, but the needle valve 4 does not sit on the sub-valve seat 33. The refrigerant slightly flows through the gap between the outer peripheral surface of the straight portion 42a and the auxiliary valve port 33a. That is, as shown in FIG. 7, even if the drive pulse is at the reference point (zero point), a minute flow rate is generated.

Next, by driving the stepping motor 5A to rotate the magnet rotor 52 to raise the needle valve 4, the straight portion 42a of the needle valve 4 comes out of the auxiliary valve port 33a, and the conical base portion 42b of the needle valve 4 and the sub A flow path is formed by the gap with the valve port 33a. Here, since the diameter of the truncated cone portion 42b gradually decreases, the gap with the auxiliary valve port 33a becomes large, the flow path expands, and the flow rate gradually increases as shown in FIG. 7. At this time, since the main valve portion 31 of the main valve body 3 remains seated on the main valve seat 13, the increase in the flow rate is slight until the second position where the needle valve 4 engages with the main valve body 3. .. The control range in which the needle valve 4 is moved between the first position and the second position to change the opening degree is the small flow rate control range.

Next, when the needle valve 4 is raised to the second position and the washer 43 is engaged with the main valve body 3, the main valve body 3 is raised together with the needle valve 4. Then, when it is further raised, as shown in FIG. 3, the main valve body 3 is pulled up by the valve shaft 41 (and washer 43), and the main valve portion 31 is separated from the main valve seat 13 to open the valve. The control range for raising the main valve body 3 from the seated position (closed position) toward the valve open position (open position) in this way is the large flow rate control range.

A defoaming member 10 is attached to the valve shaft 41 of the needle valve 4 between the guide boss portion 44 and the needle portion 42. In the small flow rate control range state shown in FIG. 2, the refrigerant (fluid) flows into the auxiliary valve chamber 3R from the conduction hole 32b, passes through the gap between the needle portion 42 (straight portion 42a) and the auxiliary valve port 33a, and is the first. 2 Flows to the joint pipe 12. At this time, the refrigerant flowing into the auxiliary valve chamber 3R from the conduction hole 32b collides with the defoaming member 10 and flows to the auxiliary valve port 33a. That is, the defoaming member 10 constitutes a part of the side wall of the flow path with respect to the flow of the refrigerant. Further, since the defoaming member 10 does not block the flow path and the valve shaft 41 forming a "wall surface" that does not allow the refrigerant to permeate inside the cylindrical defoaming member 10, the refrigerant permeates the defoaming member 10. Even if there is a foreign substance in the refrigerant, the defoaming member 10 is prevented from being clogged, so that the flow in the small flow rate control range can be ensured. Then, when the refrigerant collides with the defoaming member 10, the bubbles in the refrigerant are subdivided, and vibration and noise due to the bursting of the bubbles can be reduced.

FIG. 4 is an enlarged cross-sectional view of a main part of the small flow rate control range state of the electric valve of the second embodiment of the present invention, and in each of the following embodiments, the same elements as those of the first embodiment of FIGS. The same reference numerals as 1 and duplicated description will be omitted as appropriate. In this second embodiment, an annular defoaming member 20 is provided on the side of the auxiliary valve chamber 3R around the auxiliary valve port 33a. The defoaming member 20 has a passage 20a having a diameter larger than that of the auxiliary valve port 33a at the center. Therefore, the refrigerant flowing into the sub-valve chamber 3R from the conduction hole 32b in the small flow rate control range state passes through the passage 20a of the defoaming member 20 and through the gap between the needle portion 42 (straight portion 42a) and the sub-valve port 33a. , Flows to the second joint pipe 12. At this time, the refrigerant flowing into the auxiliary valve chamber 3R from the conduction hole 32b collides with the defoaming member 20 and flows from the passage 20a to the auxiliary valve port 33a. That is, the defoaming member 20 constitutes a part of the side wall of the flow path with respect to the flow of the refrigerant passing through the passage 20a. Further, since the defoaming member 20 does not block the flow path and there is a sub-valve seat 33 forming a "wall surface" on the sub-valve seat 33 side of the annular defoaming member 20 that does not allow the refrigerant to permeate, the refrigerant defoams. Even if there is a foreign substance in the refrigerant without penetrating the member 20, the defoaming member 20 is prevented from being clogged, so that the flow in the small flow rate control range can be ensured. Then, when the refrigerant collides with the defoaming member 20, the bubbles in the refrigerant are subdivided, and vibration and noise due to the bursting of the bubbles can be reduced.

FIG. 5 is an enlarged cross-sectional view of a main part of the small flow rate control range state of the electric valve according to the third embodiment of the present invention. In this third embodiment, an annular defoaming member 30 is provided around the auxiliary valve port 33a on the side opposite to the auxiliary valve chamber 3R. The defoaming member 30 has a passage 30a having a diameter larger than that of the auxiliary valve port 33a at the center. Therefore, in the small flow rate control range state, the refrigerant flowing out from the auxiliary valve chamber 3R through the gap between the needle portion 42 and the auxiliary valve port 33a, that is, the squeezed refrigerant is the second through the passage 30a of the defoaming member 30. It flows to the joint pipe 12. At this time, the squeezed refrigerant collides with the defoaming member 30 in the passage 30a and flows to the second joint pipe 12. That is, the defoaming member 30 constitutes a part of the side wall of the flow path with respect to the flow of the refrigerant. In this way, when the refrigerant collides with the defoaming member 30, the bubbles in the refrigerant are subdivided, and vibration and noise due to the bursting of the bubbles can be reduced. Further, since the passage 30 constitutes the flow path of the defoaming member 30, it is possible to secure the flow in the small flow rate control range.

FIG. 6 is an enlarged cross-sectional view of a main part of the electric valve of the reference example of the present invention in the small flow rate control range state. In this reference example, an annular defoaming member 40 is provided below the press-fitting portion 21 of the guide member 2. A part of the defoaming member 40 is provided so as to face the outlet of the first joint pipe 11. Then, in the small flow rate control range state, a part of the refrigerant flowing from the first joint pipe 11 into the conduction hole 32b collides with the defoaming member 40. That is, the defoaming member 40 forms a part of the side wall of the flow path with respect to the flow of the refrigerant, and the refrigerant does not permeate toward the outer peripheral surface of the holding portion 33 of the main valve body 3 forming the wall surface. In this way, when the refrigerant collides with the defoaming member 40, the bubbles in the refrigerant are subdivided, and vibration and noise due to the bursting of the bubbles can be reduced.

The defoaming members 10, 20, 30, and 40 in each of the above embodiments and reference examples are members capable of subdividing the bubbles in the refrigerant when the refrigerant collides with each other, and are, for example, a sintered filter, a demister filter, and foaming. Members such as foamed members containing metal, metal mesh, or punching metal with a large number of small holes can be used. Further, as a method for fixing these defoaming members 10, 20, 30, 40, various means such as press-fit fixing, caulking fixing, and pinching by other parts can be applied.

Next, the refrigeration cycle system of the present invention will be described with reference to FIG. This refrigeration cycle system is used, for example, in an air conditioner such as a home air conditioner. The electric valve 100 of each of the above embodiments is a "dehumidification control valve" between the first indoor heat exchanger 91 (acting as a dehumidifying cooler) and the second indoor heat exchanger 92 (operating as a dehumidifying heater). It is provided in. The electric valve 100, the first indoor heat exchanger 91, the second indoor heat exchanger 92, the electronic expansion valve 93, the outdoor heat exchanger 94, the compressor 95 and the four-way valve 96 constitute a heat pump type refrigeration cycle. doing. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the electric valve 100 are installed indoors, and the electronic expansion valve 93, the outdoor heat exchanger 94, the compressor 95, and the four-way valve 96 are installed outdoors. It constitutes a heating and cooling system.

The electric valve 100 of the embodiment as a dehumidifying valve is fully opened in a state of a large flow control range as shown in FIG. 3 during cooling or heating other than dehumidification, and the first indoor heat exchanger 91 and the first chamber heat exchanger 91 and the first. 2 The indoor heat exchanger 92 is regarded as one indoor heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 alternately function as an "evaporator" and a "condenser".

The embodiments of the present invention have been described in detail with reference to the drawings, and other embodiments have also been described in detail. However, the specific configuration is not limited to these embodiments, and the present invention is not limited to these embodiments. It is included in the present invention even if there is a design change or the like within a range that does not deviate from the gist.

1 Valve housing 1R Main valve chamber 11 1st joint pipe 12 2nd joint pipe 13 Main valve seat 13a Main valve port L Axis line 2 Guide member 21 Press-fitting part 22 Guide part 22a Guide hole 23 Holder part 23a Female thread part 24 Flange part 3 Main Valve body 3a Main valve spring 31 Main valve part 32 Holding part 33 Sub valve seat 33a Sub valve port 4 Needle valve (secondary valve body)
41 Valve shaft 42 Needle part 42a Straight part 42b Conical base part 43 Washer 44 Guide boss part 5 Drive part 5A Stepping motor 51 Rotor shaft 51a Male thread part 52 Magnet rotor 52a Protrusion part 53 Stator coil 5B Screw feed mechanism 5C Stopper mechanism 10 Foam member 20 Defoaming member 30 Defoaming member 40 Defoaming member 91 First indoor heat exchanger 92 Second indoor heat exchanger 93 Electronic expansion valve 94 Outdoor heat exchanger 95 Compressor 96 Four-way valve 100 Electric valve

Claims (6)

The axis line is the main valve body that changes the opening degree of the main valve port of the main valve chamber, the sub-valve body that changes the opening degree of the sub-valve port of the sub-valve chamber provided in the main valve body, and the sub-valve body. A small flow rate control range in which the sub-valve body changes the opening degree of the sub-valve port in a state where the main valve body is closed and the sub-valve port is provided with a drive unit that drives forward and backward in the direction, and the above-mentioned It is an electric valve that controls the flow rate of fluid in a large flow rate control range in which the main valve body changes the opening degree of the main valve port and a two-stage flow rate control range.
In the small flow rate control area, it is exposed to the fluid flowing through the sub-valve chamber and the sub-valve port, forms a part of the side wall of the flow path of the fluid, and is provided so as not to block the flow path. An electric valve characterized by being equipped with a defoaming member. The electric valve according to claim 1, wherein the defoaming member is arranged in the sub-valve chamber so as not to block the flow path on the wall surface that does not allow the fluid to permeate. The electric valve according to claim 2, wherein the defoaming member is provided in a part of the auxiliary valve body. The electric valve according to claim 2, wherein the defoaming member is provided on the side of the auxiliary valve chamber around the auxiliary valve port. The electric valve according to claim 1, wherein the defoaming member is provided around the sub-valve port on the side opposite to the sub-valve chamber. A compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidifying valve provided in the indoor heat exchanger. A refrigeration cycle system comprising the above, wherein the electric valve according to any one of claims 1 to 5 is used as the dehumidifying valve.

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