JP7372885B2 - Electric valve and refrigeration cycle system - Google Patents

Description

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

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. Such a motor-operated valve is used for being mounted on an indoor unit (for example, as a dehumidification valve), and is disclosed in, for example, Japanese Patent Application Publication No. 2017-211034 (Patent Document 1).

The electric valve of Patent Document 1 includes a main valve body (valve body 32) and a sub-valve body (valve shaft 20), and the main valve body is This is to control the small flow rate of the refrigerant to pass through to the sub-valve port (valve port 36). Furthermore, when the main valve body is fully open, most of the fluid (refrigerant) flows to the main valve port (valve port 16), which is the gap between the main valve body and the main valve seat, but some of the fluid flows to the sub valve body. flows from the communication path (29w) to the sub-valve port of the main valve body (paragraph [0050] of Patent Document 1).

Further, as this type of electric valve, one shown in FIG. 7, for example, has been considered. This electric valve has a main valve body c that opens and closes a main valve port b in a main valve chamber aR of a valve body a, and a main valve body c that controls the opening degree of a sub-valve port d in a sub-valve chamber cR formed in the main valve body c. This is an electric valve equipped with a sub-valve element e to be controlled. The main valve body c fully closes the main valve port b, and the sub-valve body e controls the opening degree of the sub-valve port d to throttle the fluid, and the main valve body c controls the main valve port b. This is a two-stage motor-operated valve having a large flow rate region in which the valve is fully opened and fluid flowing in from the inlet port g of the first joint pipe f flows to the main valve port b.

JP 2017-211034 Publication

In the motor-operated valve of Patent Document 1, when the main valve body is fully open (large flow range), a portion of the fluid flows from the communication passage (29w) of the sub-valve body to the sub-valve port of the main valve body. Disturbances occur in the flow velocity and pressure, making the fluid flow unstable and potentially causing noise and vibration. In addition, in the motor-operated valve shown in FIG. 7, when the main valve body c is fully open (large flow range), fluid mainly passes between the main valve body c and the main valve port b from the main valve chamber aR. , a flow passes through the auxiliary valve chamber cR inside the main valve element c from the communication hole h provided in the main valve element c, and passes between the auxiliary valve element e and the auxiliary valve port d. Therefore, due to the flow that passes through the sub-valve port d and is throttled, the velocity and pressure behavior of the fluid flowing into the main valve port b become unstable, which may cause vibrations in the main valve body c and refrigerant passing noise. be.

The present invention fully closes the main valve port with the main valve element, and controls the flow rate of refrigerant in a small flow rate control range using the throttle section between the auxiliary valve port and the auxiliary valve element formed in the main valve element. In a two-stage electric valve that controls a large flow range where the main valve port is fully open with the main valve body and the fluid flows to the main valve port, when controlling the large flow range, the main valve body and the main valve port The objective is to stabilize the flow of fluid to and suppress the noise and vibration of the electric valve itself.

The motor-operated valve of the present invention includes a main valve body that is provided in a main valve chamber of a valve body and opens and closes a main valve port that opens into the main valve chamber, and a main valve body that is disposed in a sub-valve chamber that is formed in the main valve body. a sub-valve body that moves in the axial direction of a sub-valve port formed in the body to control the opening degree of the sub-valve port, the main valve body closes the main valve port, and the sub-valve body closes the main valve port; a small flow rate control region that throttles the fluid by controlling the opening degree of the sub-valve port; and an inlet that opens into the main valve chamber at a side of the main valve body when the main valve port is fully opened by the main valve body. A two-stage motor-operated valve having a large flow rate region that allows fluid flowing in from a port to flow into the main valve port, wherein the main valve body is provided with a communication hole that communicates from the main valve chamber to the auxiliary valve chamber. , the communication hole is provided at a position where at least one of the communication holes located on the inlet port side does not directly oppose the opening of the inlet port when the main valve body is fully opened; , a guide member for guiding the main valve body is provided, and a retainer provided separately from the main valve body is provided at an end of the main valve body opposite to the main valve port side in the axial direction. the retainer is provided so as to be engageable with the auxiliary valve body, and a space between the guide member and the retainer urges the main valve body toward the main valve port side through the retainer. It is characterized by being provided with a main valve spring .

In this case, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located within a lower guide portion of a guide member that guides the main valve body. Electrically operated valves are preferred.

Furthermore, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located at a position away from the front of the opening of the inlet port. preferable.

Further, when the main valve body is fully opened, a center axis of at least one of the communication holes located on the inlet port side and a center axis of the inlet port are perpendicular to the axis L of the main valve port. It is preferable to use an electric valve that is characterized by intersecting when projected onto a flat plane.

The refrigeration cycle system of the present invention 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 dehumidification valve provided in an exchanger, characterized in that the electric valve is used as the dehumidification valve.

According to the electric valve and refrigeration cycle system of the present invention, when the main valve body is fully opened, the fluid flowing into the main valve chamber from the inlet port is not directly injected into the communication hole, so the fluid flows from the communication hole into the sub-valve chamber. Inflow of fluid into the valve chamber can be reduced. Therefore, the flow of fluid to the main valve body and the main valve port can be stabilized, and the generation of noise and vibration of the electric valve itself can be suppressed.

FIG. 2 is a longitudinal cross-sectional view of the electric valve according to the first embodiment of the present invention in a small flow rate control region state. FIG. 2 is a longitudinal cross-sectional view of the electric valve of the first embodiment in a large flow range state. An enlarged vertical cross-sectional view (A) of the main part of the electric valve according to the second embodiment of the present invention in a large flow range state and an enlarged cross-sectional view (B) of the main part projected on a plane perpendicular to the axis L of the main valve port. be. FIG. 7 is an enlarged longitudinal cross-sectional view of a main part of an electric valve according to a third embodiment of the present invention in a large flow range state. FIG. 7 is an enlarged cross-sectional view of the main part of the electric valve according to the fourth embodiment of the present invention, in which the communication hole and the inlet port in a large flow range state are projected onto a plane perpendicular to the axis L of the main valve port. 1 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention. FIG. 2 is a diagram illustrating an example of a two-stage electric valve and its problems.

Next, embodiments of the electric valve and refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal cross-sectional view of the motor-operated valve according to the first embodiment in a small flow control region state, and FIG. 2 is a longitudinal cross-sectional view of the motor-operated valve according to the first embodiment in a large flow control region state. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of FIGS. 1 and 2. This electric valve 100 includes a valve housing 1 , 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 1R inside thereof. A first joint pipe 11 that communicates with the main valve chamber 1R 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 1R 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 13a. The main valve port 13a is a cylindrical through hole centered on the axis L, and the second joint pipe 12 is communicated with the main valve chamber 1R via the main valve port 13a. The inner end of the first joint pipe 11 on the side of the main valve chamber 1R serves as an inlet port 11a.

A guide member 2 is attached to an opening at the upper end of the valve housing 1 . The guide member 2 includes a press-fitting part 21 that is press-fitted into the inner circumferential surface of the valve housing 1, a substantially cylindrical upper guide part 22 located above the press-fitting part 21, and an upper part of the upper guide part 22 extending therefrom. A ring-shaped flange part 24 provided on the outer periphery of the press-fitting part 21 , and a substantially cylindrical lower guide part 25 located below the press-fitting part 21 are provided. The press-fitting part 21, the upper guide part 22, the lower guide part 25, and the holder part 23 are constructed as an integral part made of resin. Further, the flange portion 24 is, for example, a metal plate made of brass, stainless steel, or the like, and is integrally provided with the resin press-fit portion 21 by insert molding.

The guide member 2 is assembled to the valve housing 1 by a press-fitting part 21, and is fixed to the upper end part of the valve housing 1 via a flange part 24 by welding. Further, in the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the press-fitting part 21, the upper guide part 22, and the lower guide part 25, and a guide hole 2A coaxial with the axis L is formed in the center of the holder part 23. A female screw portion 23a coaxial with the hole 2A and its screw hole are formed. A main valve body 3 is disposed within 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 holds the sub valve body 4. A cylindrical expansion hole 3A is formed inside the main valve part 31, and a cylindrical sub-valve chamber 3R is formed inside the holding part 32, and the inner peripheral surface of the sub-valve chamber 3R is This is a guide hole 3B. A cylindrical sub-valve port 3a is formed between the main valve part 31 and the holding part 32 and opens from the sub-valve chamber 3R to the expansion hole 3A side with the axis L as the center.

Further, a communication passage 3b communicating from the main valve chamber 1R to the sub-valve chamber 3R in a direction intersecting the axis L is formed on the side surface of the holding portion 32 of the main valve body 3. In this embodiment, a plurality of communicating passages 3b (for example, four) are formed radially at positions that are rotationally symmetrical about the axis L. The four communicating passages 3b are formed in positions that do not directly face the inlet port 11a, which is the opening of the first joint pipe 11, in the direction of the axis L. Note that although four communicating paths 3b are illustrated here, any number of communicating paths 3b may be used as long as they are not directly opposed to the inlet port 11a.

The main valve body 3 has a retainer 34 at the upper end of the holding part 32, and a main valve spring 35 between the retainer 34 and the upper end of the guide hole 2A of the guide member 2. 35 urges the main valve body 3 in the direction of the main valve seat 13 (closed direction). The sub-valve body 4 is formed integrally with the rotor shaft 51 at the lower end of the rotor shaft 51, and the sub-valve body 4 includes 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 3a 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 3a. 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 slidably inserted into the sub-valve guide hole 3B.

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 a case 14, a stator coil 53 disposed opposite to the magnet rotor 52 on the outer periphery of the case 14, and other components shown in the figure. It is made up 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 rotor shaft 51 on the guide member 2 side. The male threaded portion 51a is screwed into the female threaded portion 24a of the guide member 2, so that the guide member 2 supports the rotor shaft 51 on the axis L. The female threaded portion 24a of the guide member 2 and the male threaded portion 51a of the rotor shaft 51 constitute a screw feeding mechanism 5B. A cylindrical portion 14a that holds the rotation stopper mechanism 5C is provided on the inner ceiling of the case 14, and a guide member 54 that guides the upper end of the rotor shaft 51 is disposed within the cylindrical portion 14a.

With the above configuration, when the stepping motor 5A is driven, the magnet rotor 52 and the rotor shaft 51 rotate, and the screw feeding mechanism 5B of the male threaded portion 51a of the rotor shaft 51 and the female threaded portion 24a of the guide member 2 causes the magnet rotor 52 to rotate. At the same time, the rotor shaft 51 moves in the direction of the axis L. Then, the sub-valve body 4 moves forward and backward in the direction of the axis L, and the needle valve 42 approaches or separates from the sub-valve port 3a. Further, when the needle valve 42 rises, the washer 43 engages with the retainer 34 of the main valve body 3, and the main valve body 3 moves together with the sub valve body 4 and leaves the main valve seat 13. Note that the magnet rotor 52 is formed with a protrusion 52a, and as the magnet rotor 52 rotates, the protrusion 52a operates the rotation stopper mechanism 5C, and the lowermost position of the rotor shaft 51 (and the magnet rotor 52) and The top position is restricted.

In the small flow rate control region state of FIG. 1, the main valve port 13a is closed with the main valve body 3 seated on the main valve seat 13, and the opening degree of the sub valve port 3a is controlled by the needle valve 42 of the sub valve body 4. controlled, and small flow control is performed. At this time, the communication passage 3b is located below the lower end of the lower guide portion 25 of the guide member 2, and the refrigerant in the main valve chamber 1R flows into the sub valve chamber 3R through the communication passage 3b.

In the large flow range state of FIG. 2, the refrigerant mainly passes between the main valve portion 31 of the main valve body 3 and the main valve port 13a from the main valve chamber 1R, but when the main valve body 3 is fully open, The communication path 3b is blocked by the lower guide portion 25 from the inlet port 11a. As a result, the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, so it is possible to reduce the flow of fluid from the communication hole 3b into the sub-valve chamber 3R. . Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

FIG. 3 is a diagram of the motor-operated valve according to the second embodiment of the present invention in a large flow range state, where FIG. 3(A) is an enlarged vertical cross-sectional view of the main part, and FIG. FIG. 2 is an enlarged cross-sectional view of the main part of the communication hole and the inlet port projected onto a plane perpendicular to the axis L of the main valve port. The difference from the first embodiment is that the length of the lower guide 25 of the guide member 2' on the side opposite to the inlet port 11a is shorter, whereas the lower guide 25 on the side of the inlet port 11a has a predetermined width. The main valve body 3 is longer in length and, although not shown, is provided with a rotation stopper to prevent the main valve body 3 from rotating even if it moves in the vertical direction. For example, the rotation stopper is formed by forming an axially elongated convex key part on the inner periphery of the guide member 2', which engages with a longitudinal groove formed on the outer periphery of the main valve element 3. It may also be used to prevent rotation. When initially assembling the valve, as shown in FIGS. 3(A) and 3(B), in a large flow range state, the communication hole 3b on the inlet port 11a side is blocked by the lower guide part on the inlet port 11a side. The position of the rotation stopper of the main valve body 3 may be set in advance. Accordingly, in the second embodiment as well, the communication hole 3b on the inlet port 11a side is blocked by the lower guide 25 in the large flow range state, as in the first embodiment. Therefore, since the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, the flow of fluid from the communication hole 3b into the sub-valve chamber 3R can be reduced. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

In addition, in FIG. 3, the axis of the communication hole 3b on the inlet port 11a side is set in the same direction (parallel) as the axis of the inlet port 11a, as shown in FIG. 3(B), but the axis is not limited to this. If the communication hole 3b on the side is within a predetermined width of the lower guide 25 on the inlet port 11a side, it will be blocked, so the axis of the communication hole 3b on the inlet port 11a side is set as a direction forming a predetermined angle with the axis of the inlet port. (not shown).

FIG. 4 is an enlarged sectional view of the main part of the third embodiment of the present invention in a large flow range state, and the difference from the first embodiment is that there is no guide part below the press-fit part 21'' of the guide member 2'' , as shown in FIG. 4, in the large flow range state, the communication passage 3b is located at a position where it does not directly oppose the inlet port 11a, which is the opening of the first joint pipe 11, in the direction of the axis L, that is, above the inlet port 11a in the direction of the axis L. It is a point that moves to a far away position. As a result, in the third embodiment as well, in the large flow range state, the refrigerant mainly passes between the main valve portion 31 of the main valve body 3 and the main valve port 13a from the main valve chamber 1R; When the body 3 is fully open, the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, so the flow of fluid from the communication hole 3b into the sub-valve chamber 3R is reduced. can do. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric motor 100 can be suppressed.

Although the axis of the communication hole 3b and the axis of the inlet port 11a are set in the same direction in FIG. 4, they may be set in different directions.

FIG. 5 is an enlarged cross-sectional view of main parts of the fourth embodiment of the present invention, in which the communication passage 3b and the inlet port 11a in a large flow area state are projected onto a plane perpendicular to the axis L, and shows differences from the third embodiment. The point is that the communication hole 3b on the inlet port 11a side is located within the range of the inner diameter of the opening of the inlet port 11a in the direction of the axis L, and the direction of the axis of the communication hole 3b is in the same direction (parallel) as the direction of the axis of the inlet port 11a. ), they intersect as shown in FIG. 5, and furthermore, although not shown, a rotation stopper is provided to prevent the main valve body 3 from rotating even if it moves in the vertical direction. The rotation stopper is the same as in the second embodiment, and even if the main valve body 3 moves in the L-axis direction, the angle formed by the axis of the communication hole 3b and the axis of the inlet port 11a does not change. As a result, even if the communication hole 3b is located within the inner diameter range of the opening of the inlet port 11a in the direction of the axis L, as shown in FIG. Since the fluid is not directly injected into the auxiliary valve chamber 3R, the inflow of fluid from the communication hole 3b into the sub-valve chamber 3R can be reduced. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

In the fourth embodiment, the angle α between the central axis of the communication hole 3b on the side of the inlet port 11a in FIG. 5 and the central axis of the inlet port 11a is preferably 45° or more and 90° or less.

FIG. 6 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention, and the refrigeration cycle system according to the embodiment will be explained based on the diagram. Refrigeration cycle systems are used, for example, in air conditioners such as household air conditioners. The motor-operated valve 100 of the embodiment is provided between the first indoor heat exchanger 91 (operates as a cooler during dehumidification) and the second indoor heat exchanger 92 (operates as a heater during dehumidification) of the air conditioner. The compressor 95, four-way valve 96, outdoor heat exchanger 94, and electronic expansion valve 93 constitute a heat pump refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the electric valve 100 are installed indoors, and the compressor 95, four-way valve 96, outdoor heat exchanger 94, and electronic expansion valve 93 are installed outdoors. They have heating and cooling equipment.

In the electric valve 100 of the embodiment as a dehumidification valve, the main valve body is fully opened during cooling or heating other than during dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are connected to one indoor heat exchanger. It is considered a heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 function alternatively as an "evaporator" and a "condenser." That is, the electric valve 93 as an electronic expansion valve is provided between the evaporator and the condenser.

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. For example, in the above embodiment, the electric valve 100 used in an air conditioner such as a domestic air conditioner is illustrated, but the electric valve of the present invention is not limited to a household air conditioner, but may be used in a commercial air conditioner. It is applicable not only to air conditioners but also to various types of refrigerators.

The embodiments of the present invention have been described above in detail with reference to the drawings, and other embodiments have also been described in detail, but the specific configuration is not limited to these embodiments. Even if there are changes in the design within the scope of the invention, they are included in the present invention.

1 Valve housing 1R Main valve chamber 11 First joint pipe 11a Inlet port 12 Second joint pipe 13 Main valve seat 13a Main valve port L Axis 2, 2', 2'' Guide member 2A Guide hole 22 Upper guide part 25 Lower guide part 23 Holder part 23a Female thread part 3 Main valve body 31 Main valve part 32 Holding part 3a Sub-valve port 3b Communication hole 3A Sub-valve chamber 4 Sub-valve body 41 Guide boss part 42 Needle valve 5 Drive part 5A Stepping motor 5B Screw feed mechanism 5C Stopper mechanism 51 Rotor shaft 51a Male thread 52 Magnet rotor 53 Stator coil 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 (5)

A main valve body that is provided in a main valve chamber of a valve body and opens and closes a main valve port that opens into the main valve chamber, and a sub-valve that is formed in the main valve body in a sub-valve chamber that is formed in the main valve body. a sub-valve element that moves in the axial direction of the port to control the opening degree of the sub-valve port, the main valve element closing the main valve port and the sub-valve element controlling the opening degree of the sub-valve port. a small flow rate control region that throttles the fluid by controlling the main valve body, and a small flow rate control region that controls the fluid flow by fully opening the main valve port with the main valve body, and controlling the fluid flowing in from the inlet port that opens into the main valve chamber at the side of the main valve body. In a two-stage electric valve that has a large flow area flowing to the main valve port,
The main valve body is provided with a communication hole that communicates from the main valve chamber to the auxiliary valve chamber,
The communication hole is provided at a position where at least one of the communication holes located on the inlet port side does not directly oppose the opening of the inlet port when the main valve body is fully opened;
The valve body is provided with a guide member that guides the main valve body,
A retainer provided separately from the main valve body is coupled to an end of the main valve body opposite to the main valve port side in the axial direction,
The retainer is provided so as to be engageable with the sub-valve body,
The motor-operated valve is characterized in that a main valve spring is provided between the guide member and the retainer to urge the main valve body toward the main valve port via the retainer. Claim 1, wherein when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located within a lower guide portion of a guide member that guides the main valve body. Electric valve described in. According to claim 1, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located away from in front of the opening of the inlet port. electric valve. When the main valve body is fully opened, a central axis of at least one of the communication holes located on the inlet port side and a central axis of the inlet port are in a plane perpendicular to the axis L of the main valve port. The motor-operated valve according to claim 1, wherein the motor-operated valve intersects when projected on. 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 dehumidification valve provided in the indoor heat exchanger. A refrigeration cycle system comprising: the electric valve according to any one of claims 1 to 4 being used as the dehumidification valve.

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