CN110873225A

CN110873225A - Electric valve and refrigeration cycle system

Info

Publication number: CN110873225A
Application number: CN201910745593.7A
Authority: CN
Inventors: 中川大树; 北见雄希; 小池亮司
Original assignee: Saginomiya Seisakusho Inc
Current assignee: Saginomiya Seisakusho Inc
Priority date: 2018-08-31
Filing date: 2019-08-13
Publication date: 2020-03-10
Also published as: JP2020034141A; JP6968768B2

Abstract

The invention provides an electric valve, in the electric valve which performs flow control in a small flow control area by a needle valve (4), the flow of fluid is ensured for the small flow of fluid in the small flow control area, and the passing sound caused by the rupture of bubbles of the fluid is reduced to improve the silence. A needle valve (4) (sub-valve body) having a conical surface portion (42b) whose diameter gradually decreases toward the tip end is disposed on the axis L of the sub-valve port (33 a). The needle valve (4) is moved back and forth on the axis by a drive unit (5). A small flow control area is obtained by the needle valve (4) and the sub-valve port (33 a). In the small flow control region, a defoaming member (10) is provided so as to be exposed to the fluid flowing in the sub-valve chamber (3R) and the sub-valve port (33 a). The fluid flowing into the sub-valve chamber (3R) from the leading hole (32b) is made to strike against the defoaming member (10), thereby thinning bubbles in the fluid.

Description

Electric valve and refrigeration cycle system

Technical Field

The present invention relates to an electrically operated valve used in a refrigeration cycle or the like and a refrigeration cycle.

Background

Currently, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that performs flow rate control in a small flow rate control area and a large flow rate control area. Such an electric valve is used in an indoor unit (for example, a dehumidification valve), and it is necessary to reduce the sound of a fluid (refrigerant) flow when controlling a small flow rate. Therefore, for example, japanese patent laid-open nos. 2017 and 211032 (patent document 1) and 2017 and 211034 (patent document 2) disclose electrically operated valves in consideration of quietness.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2017-211032

Patent document 2: japanese patent laid-open publication No. 2017-211034

Disclosure of Invention

Problems to be solved by the invention

In the prior art of

patent documents

1 and 2, a muffler member is disposed so as to intersect with a flow stream (flux) of a refrigerant flow, and the muffler member is constructed so as to allow the refrigerant to pass therethrough. As shown in the related art, in the structure through which the refrigerant passes, the muffler member may be clogged by foreign matter such as dust in the refrigerant, and it is difficult to perform an appropriate flow rate control.

The subject of the invention is: in an electrically operated valve for controlling flow in a small flow rate control region and a large flow rate control region, the flow of a fluid is ensured for a small flow rate of the fluid in the small flow rate control region, and passing sound caused by the collapse of bubbles of the fluid is reduced to improve quietness.

Means for solving the problems

The motor-operated valve of claim 1 comprises a main valve body for changing the opening degree of a main valve port of a main valve chamber, a sub-valve body for changing the opening degree of a sub-valve port of a sub-valve chamber provided in the main valve body, and a driving portion for driving the sub-valve body to advance and retreat in the axial direction, controlling the flow rate of the fluid in two stages of a small flow rate control region and a large flow rate control region in a state where the main valve element closes the main valve port, the small flow rate control region is a region where the sub valve body changes the opening degree of the sub valve port, and the large flow rate control region is a region where the main valve body changes the opening degree of the main valve port, and the electric valve is characterized by comprising a defoaming member, the defoaming member is disposed so as to be exposed to the fluid flowing through the sub-valve chamber and the sub-valve port in the small flow rate control region, and forms a part of a side wall of a flow path for the fluid.

The electrically operated valve according to claim 2 is characterized in that the defoaming member is disposed in the sub valve chamber on a wall surface that does not allow the fluid to pass therethrough so as not to block the flow path.

The electrically operated valve according to claim 3 is characterized in that the defoaming member is provided in a part of the sub valve body.

The electrically operated valve according to claim 4 is characterized in that the defoaming member is provided on the side of the auxiliary valve chamber around the auxiliary valve port, in the electrically operated valve according to claim 2.

The electrically operated valve according to claim 5 is characterized in that the defoaming member is provided on the side opposite to the sub valve chamber around the sub valve port.

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 a dehumidification valve provided in the indoor heat exchanger, and is characterized in that the electric valve according to any one of claims 1 to 5 is used as the dehumidification valve.

The effects of the invention are as follows.

According to the motor-operated valve of claims 1 to 5, the defoaming member forms a part of the side wall of the flow path of the fluid with respect to a small flow rate of the fluid in the small flow rate control region, and the fluid hits the defoaming member, whereby bubbles are refined. 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 the fluid. Therefore, the flow of the fluid in the small flow rate control region can be ensured, and the noise can be improved by reducing the passing sound caused by the collapse of the bubbles of the fluid.

According to the refrigeration cycle system of scheme 6, the same effects as those of schemes 1 to 5 are obtained.

Drawings

Fig. 1 is a longitudinal sectional view of an electric valve according to a first embodiment of the present invention.

Fig. 2 is a main-part enlarged cross-sectional view of the motor-operated valve of the first embodiment in a small flow rate control region state.

Fig. 3 is an enlarged cross-sectional view of a main portion of the electric valve of the first embodiment in a large flow rate control region state.

Fig. 4 is an enlarged cross-sectional view of a main portion of a small flow rate control region of an electrically operated valve according to a second embodiment of the present invention.

Fig. 5 is an enlarged cross-sectional view of a main portion of a small flow rate control region of an electrically operated valve according to a third embodiment of the present invention.

Fig. 6 is an enlarged cross-sectional view of a main portion of a small flow rate control region of an electrically operated valve according to a reference example of the present invention.

Fig. 7 is a diagram showing a relationship between a valve lift amount and a flow rate of an electrically operated valve according to an embodiment of the present invention.

Fig. 8 is a diagram showing a refrigeration cycle system of the embodiment.

In the figure:

1-a valve housing, 1R-a main valve chamber, 11-a first joint pipe, 12-a second joint pipe, 13-a main valve seat, 13 a-a main valve port, L-an axis, 2-a guide member, 21-a press-in portion, 22-a guide portion, 22 a-a guide hole, 23-a holder portion, 23 a-an internal thread portion, 24-a flange portion, 3-a main valve spool, 3 a-a main valve spring, 31-a main valve portion, 32-a holding portion, 33-a sub valve seat, 33 a-a sub valve port, 4-a needle valve (sub valve spool), 41-a valve shaft, 42-a needle portion, 42 a-a straight portion, 42B-a cone portion, 43-a washer, 44-a guide boss portion, 5-a drive portion, 5A-a stepping motor, 51-a rotor shaft, 51 a-external thread portion, 52-a magnetic rotor, 52a boss portion, 53-a stator coil, 5B-a thread feed mechanism, 5C-a stopper mechanism, 10-a defoaming member, 20-a defoaming member, 30-defoaming component, 40-defoaming component, 91-first indoor heat exchanger, 92-second indoor heat exchanger, 93-electronic expansion valve, 94-outdoor heat exchanger, 95-compressor, 96-four-way valve and 100-electric valve.

Detailed Description

Next, embodiments of the motor-operated valve and the refrigeration cycle system according to the present invention will be described with reference to the drawings. Fig. 1 is a longitudinal sectional view of a small flow rate control range state of an electric valve of a first embodiment, fig. 2 is a main part enlarged sectional view of the small flow rate control range state of the electric valve of the first embodiment, and fig. 3 is a main part enlarged sectional view of the large flow rate control range state of the electric valve of the first embodiment. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of fig. 1 to 3. The motor-operated valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "sub valve body", and a drive unit 5.

The valve housing 1 is formed into a substantially cylindrical shape, for example, from brass, stainless steel, or the like, 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 that extends downward from the lower end. A cylindrical main valve seat 13 is formed on the main valve chamber 1R side of the second joint pipe 12, the inner side of the main valve seat 13 becomes a main valve port 13a, and the second joint pipe 12 is communicated with the main valve chamber 1R through the main valve port 13 a. 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 an opening portion at the upper end of the valve housing 1. The guide member 2 includes a press-fitting portion 21 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, a bracket portion 23 extended to the upper portion of the guide portion 22, and an annular 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 formed as an integral member made of resin. The flange portion 24 is a metal plate such as brass or stainless steel, for example, and the flange portion 24 is integrated with the resin press-fitting portion 21 and the bracket portion 22 by insert molding.

The guide member 2 is assembled to the valve housing 1, and is fixed to the upper end portion of the valve housing 1 by welding via the flange portion 24. 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. The main valve element 3 is disposed in the guide hole 22a of the holder portion 23.

The main valve body 3 includes a main valve portion 31 that seats on and unseats from the main valve seat 13, a holding portion 32 having a cylindrical needle guide hole 32a, and a sub valve seat 33. A portion below the needle guide hole 32a serves as the sub-valve chamber 3R. A washer 43 and a guide boss 44 attached to a valve shaft 41 described below are inserted into the needle guide hole 32a of the holding portion 32, and an annular retainer 321 is fitted and fixed to an upper end of the holding portion 32 or fixed thereto by welding or the like. The outer peripheral portion of the upper end of the holding portion 32 is reduced in diameter, 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, and the main valve spring 3a biases the main valve element 3 in the direction of the main valve seat 13 (closing direction). The sub valve seat 33 is located at the lower end portion of the needle guide hole 32a, and has a sub valve port 33a formed at the center thereof. The sub-valve port 33a has a cylindrical shape centered on the axis L. At least one of the side surfaces of the holding portion 32 is formed with a communication hole 32b for communicating the sub-valve chamber 3R with the main valve chamber 1R, and as will be described later, when the needle valve 4 serving as a sub-valve body opens the sub-valve port 33a, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a communicate with each other.

The needle valve 4 integrally includes: a valve shaft 41 formed integrally with the rotor shaft 51 at a lower end portion of the rotor shaft 51 described below and connected to the rotor shaft 51 side; and a needle 42 connected to a lower end of the valve shaft 41. The needle portion 42 is composed of a linear portion 42a and a tapered table portion 42 b. The linear portion 42a is formed to have a diameter matching the sub-port 33a and to be inserted into the sub-port 33a, and the side surfaces thereof have the same diameter in the direction of the axis L. The truncated cone portion 42b has a truncated cone shape whose diameter gradually decreases toward the front end. The needle valve 4 includes an annular washer 43 disposed on the valve shaft 41, and a guide boss 44 fixed to the valve shaft 41. The guide boss 44 is fixed separately from the valve shaft 41, but the guide boss 44 may be formed integrally with the valve shaft 41. The washer 43 and the guide boss 44 are slidably inserted into the needle guide hole 32 a.

A housing 14 is hermetically fixed to the upper end of the valve housing 1 by welding or the like, and a driving portion 5 is formed inside and outside the housing 14. The drive unit 5 includes a stepping motor 5A, a thread feed mechanism 5B that advances and retracts the needle valve 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C that restricts rotation of the stepping motor 5A.

The stepping motor 5A includes a rotor shaft 51, a magnetic rotor 52 rotatably disposed inside the housing 14, a stator coil 53 disposed on the outer periphery of the housing 14 so as to face the magnetic rotor 52, and other yoke parts and exterior members, which are not shown. The rotor shaft 51 is attached to the center of the magnetic rotor 52 via a bushing, 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 screw portion 51a is screwed into the female screw 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 a screw feeding mechanism 5B.

With the above configuration, the magnetic rotor 52 and the rotor shaft 51 are rotated by the driving of the stepping motor 5A, and the rotor shaft 51 is moved in the direction of the axis L by the screw feeding mechanism 5B constituted by the male screw portion 51a of the rotor shaft 51 and the female screw portion 23a of the guide member 2. Then, the needle valve 4 moves forward and backward in the direction of the axis L, and the needle valve 4 approaches or separates from the sub-valve port 33 a. Thereby controlling the opening degree of the sub-port 33 a. Then, the needle 4 (washer 43) engages with the main valve body 3 (holder 321), and the main valve body 3 moves together with the needle 4 to seat on and unseat from the main valve seat 13. Thereby controlling 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. The magnetic rotor 52 is provided with a projection 52a, and the projection 52a operates the rotation restricting mechanism 5C to restrict the lowermost end position and the uppermost end position of the rotor shaft 51 (and the magnetic rotor 52) in accordance with the rotation of the magnetic rotor 52. Fig. 1 and 2 show a state in which the rotor shaft 51 (and the magnetic rotor 52) is located at the lowermost position.

Fig. 7 is a diagram showing a relationship between the pulse amount (valve opening degree) and the flow rate of the drive pulse in the stepping motor 5A, 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 3 is seated on the main valve seat 13, and is in a valve-closed state in which the main valve port 13a is closed. On the other hand, although the linear portion 42a of the needle valve 4 located at the first position closest to the sub-valve port 33a is inserted into the sub-valve port 33a, the needle valve 4 is not seated on the sub-valve seat 33, and the refrigerant slightly flows through a gap between the outer peripheral surface of the linear portion 42a and the sub-valve port 33 a. 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, the magnetic rotor 52 is rotated by the driving of the stepping motor 5A to raise the needle valve 4, whereby the linear portion 42a of the needle valve 4 is disengaged from the sub-valve port 33a, and a flow path is formed by a gap between the conical table portion 42b of the needle valve 4 and the sub-valve port 33 a. Here, the diameter of the conical surface portion 42b gradually decreases, the gap with the sub valve port 33a increases, 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 flow rate increases slightly until the needle valve 4 engages with the second position of the main valve body 3. In this way, the control region in which the opening degree is changed by moving the needle valve 4 between the first position and the second position is the small flow rate control region.

Next, when the needle 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 4. When the valve further ascends, as shown in fig. 3, the main valve body 3 is lifted by the valve shaft 41 (and the washer 43), and the main valve portion 31 is separated from the main valve seat 13 and opened. Thus, the control region for raising the main valve element 3 from the seating position (closed position) to the valve opening position (open position) is a large flow rate control region.

The defoaming member 10 is attached to the valve shaft 41 of the needle valve 4 between the guide boss 44 and the needle 42. In the small flow rate control region state shown in fig. 2, the refrigerant (fluid) flows into the sub valve chamber 3R from the through hole 32b, passes through a gap between the needle portion 42 (straight portion 42a) and the sub valve port 33a, and then flows into the second joint pipe 12. At this time, the refrigerant flowing into the sub valve chamber 3R from the communication hole 32b hits the defoaming member 10 and flows into the sub valve port 33 a. That is, the defoaming member 10 forms 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 constituting a "wall surface" through which the refrigerant does not pass is provided inside the cylindrical defoaming member 10, the refrigerant does not pass through the defoaming member 10, and even when foreign matter is present in the refrigerant, clogging of the defoaming member 10 is suppressed, and the flow in the small flow rate control region can be ensured. Further, since the refrigerant hits the defoaming member 10, bubbles in the refrigerant are refined, and vibration and noise caused by the collapse of the bubbles can be reduced.

Fig. 4 is an enlarged cross-sectional view of a main portion of a small flow rate control region state of an electrically operated valve according to a second embodiment of the present invention, and in each of the following embodiments, the same elements as those in the first embodiment of fig. 1 to 3 are denoted by the same reference numerals as in fig. 1, and overlapping description thereof will be omitted as appropriate. In the second embodiment, an annular defoaming member 20 is provided on the side of the sub valve chamber 3R around the sub valve port 33 a. The defoaming member 20 has a passage 20a in the center, which is larger in diameter than the sub-valve port 33 a. Therefore, in the small flow rate control region state, the refrigerant flowing from the through hole 32b into the sub valve chamber 3R passes through the passage 20a of the defoaming member 20, passes through the gap between the needle portion 42 (the straight portion 42a) and the sub valve port 33a, and then flows into the second joint pipe 12. At this time, the refrigerant flowing into the sub valve chamber 3R from the communicating hole 32b hits the defoaming member 20 and flows from the passage 20a to the sub valve port 33 a. That is, the defoaming member 20 forms a part of the side wall of the flow path with respect to the flow of the refrigerant passing through the passage 20 a. Further, since the defoaming member 20 does not close the flow path, and the annular defoaming member 20 has the sub-valve seat 33 constituting the "wall surface" through which the refrigerant does not pass on the side of the sub-valve seat 33, the refrigerant does not pass through the defoaming member 20, and even when foreign matter is present in the refrigerant, clogging of the defoaming member 20 is suppressed, and the flow in the small flow rate control region can be ensured. Further, since the refrigerant hits the defoaming member 20, bubbles in the refrigerant are refined, and vibration and noise caused by the collapse of the bubbles can be reduced.

Fig. 5 is an enlarged cross-sectional view of a main portion of a small flow rate control region of an electrically operated valve according to a third embodiment of the present invention. In the third embodiment, an annular defoaming member 30 is provided around the sub valve port 33a and on the opposite side of the sub valve chamber 3R. The defoaming member 30 has a passage 30a in the center, which is larger in diameter than the sub-valve port 33 a. Therefore, in the small flow rate control region state, the refrigerant flowing out of the sub valve chamber 3R through the gap between the needle portion 42 and the sub valve port 33a, that is, the throttled refrigerant flows through the passage 30a of the defoaming member 30 to the second joint pipe 12. At this time, the throttled refrigerant hits the defoaming member 30 in the passage 30a and flows into 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. As a result, the refrigerant hits the defoaming member 30, bubbles in the refrigerant are reduced in size, and vibration and noise caused by the collapse of the bubbles can be reduced. Further, since the passage 30a of the defoaming member 30 constitutes a flow path, a flow in a small flow rate control region can be ensured.

Fig. 6 is an enlarged cross-sectional view of a main portion of a small flow rate control region of an electrically operated valve according to a reference example of the present invention. 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 disposed to face the outlet of the first joint pipe 11. In the small flow rate control area state, a part of the refrigerant flowing from the first joint pipe 11 into the guide through hole 32b hits 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, so that the refrigerant does not permeate toward the outer peripheral surface of the holding portion 33 of the main valve element 3 forming the wall surface. As a result, the refrigerant hits the defoaming member 40, bubbles in the refrigerant are reduced in size, and vibration and noise caused by the collapse of the bubbles can be reduced.

The

defoaming members

10, 20, 30, and 40 in the above embodiments and reference examples are members capable of attenuating bubbles in the refrigerant by hitting the refrigerant, and for example, a sintered filter, a defogging filter, a foaming member made of a foamed metal, a metal mesh, or a punched metal having a plurality of small holes formed therein may be used. As a method for fixing the

defoaming members

10, 20, 30, and 40, various methods such as press-fitting, caulking, and clamping with other members can be applied.

Next, a refrigeration cycle system of the present invention will be described with reference to fig. 8. This refrigeration cycle system is used for an air conditioner such as a household air conditioner. The motor-operated valve 100 of each of the above embodiments is provided as a "dehumidification control valve" between the first indoor heat exchanger 91 (which operates as a cooler during dehumidification) and the second indoor heat exchanger 92 (which operates as a heater during dehumidification). The motor-operated 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 refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated 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, thereby configuring a cooling/heating apparatus.

In the motor-operated valve 100 as the embodiment of the dehumidification valve, at the time of cooling or heating other than the time of dehumidification, as shown in fig. 3, the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are in the fully open state in the state of the large flow rate control region, and become one indoor heat exchanger. The integrated indoor and outdoor heat exchangers 94 alternatively function as "evaporators" or "condensers".

While the embodiments of the present invention have been described in detail with reference to the drawings and other embodiments have been described in detail, the specific configurations are not limited to the embodiments described above, and the present invention includes design changes and the like within a range not departing from the gist of the present invention.

Claims

1. An electrically operated valve comprising a main valve body for changing the opening degree of a main valve port of a main valve chamber, a sub valve body for changing the opening degree of a sub valve port of a sub valve chamber provided in the main valve body, and a driving section for driving the sub valve body to advance and retreat in the axial direction, wherein the flow rate of a fluid is controlled in two-stage flow rate control regions of a small flow rate control region and a large flow rate control region in a state where the main valve body closes the main valve port, the small flow rate control region is a region where the sub valve body changes the opening degree of the sub valve port, and the large flow rate control region is a region where the main valve body changes the opening degree of the main valve port,

the above-mentioned electric valve is characterized in that,

the valve device is provided with a defoaming member that is exposed to the fluid flowing in the sub-valve chamber and the sub-valve port in the small flow rate control region and that forms a part of a side wall of a flow path for the fluid.

2. Electrically operated valve according to claim 1,

the defoaming member is disposed in the sub valve chamber on a wall surface through which the fluid does not pass so as not to block the flow path.

3. Electrically operated valve according to claim 2,

the defoaming member is provided in a part of the sub-valve body.

4. Electrically operated valve according to claim 2,

the defoaming member is provided on the side of the auxiliary valve chamber around the auxiliary valve port.

5. Electrically operated valve according to claim 1,

the defoaming member is provided on the opposite side of the auxiliary valve port from the auxiliary valve chamber.

6. A refrigeration cycle system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve arranged between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidification valve arranged on the indoor heat exchanger,

use of an electrically operated valve as claimed in any one of claims 1 to 5 as said dehumidification valve.