CN110107724B - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
- Publication number
- CN110107724B CN110107724B CN201910032327.XA CN201910032327A CN110107724B CN 110107724 B CN110107724 B CN 110107724B CN 201910032327 A CN201910032327 A CN 201910032327A CN 110107724 B CN110107724 B CN 110107724B
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- valve
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- main valve
- valve body
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 14
- 230000002093 peripheral effect Effects 0.000 claims abstract description 35
- 239000011347 resin Substances 0.000 claims description 8
- 229920005989 resin Polymers 0.000 claims description 8
- 238000005520 cutting process Methods 0.000 claims description 6
- 239000012530 fluid Substances 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 description 9
- 230000007257 malfunction Effects 0.000 description 4
- 210000000078 claw Anatomy 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- HCHKCACWOHOZIP-UHFFFAOYSA-N Zinc Chemical compound [Zn] HCHKCACWOHOZIP-UHFFFAOYSA-N 0.000 description 1
- 229910001297 Zn alloy Inorganic materials 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 229920006351 engineering plastic Polymers 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000005405 multipole Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 239000011701 zinc Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Lift Valve (AREA)
Abstract
The invention provides an electric valve and a refrigeration cycle system, which can properly control the flow rate in a small flow rate control area in the electric valve with two-stage flow rate control area. The motor-operated valve (10) is provided with a main valve element (2), an auxiliary valve element (3), and a drive unit (4), and has a flow rate control region in two stages, namely a small flow rate control region in which the auxiliary valve element (3) changes the opening of the auxiliary port (22), and a large flow rate control region in which the main valve element (2) opens and closes the main port (1 c). The sub-valve body (3) has a sub-valve portion (31) provided on the outer peripheral surface thereof and changing the opening degree of the sub-valve port (22), and a thrust washer (34) provided on the front end side of the sub-valve portion (31). A through flow path (35) is formed as a bypass flow path R' on at least one of the main valve element (2) and the sub valve element (3), and the through flow path (35) reaches the tip end of the sub valve element (3) while bypassing the contact surface between the engaged portion (23) and the thrust washer (34).
Description
Technical Field
The present invention relates to an electric valve and a refrigeration cycle system.
Background
As an electric valve provided in a refrigeration cycle of an air conditioner, an electric valve having two stages of a small flow control region in which a sub valve body is driven by an electric motor to move forward and backward in an axial direction to control a flow rate at a sub valve port of a main valve body and a large flow control region in which the main valve body opens and closes a main valve port of a valve chamber has been proposed (see, for example, patent document 1).
The electrically operated valve (electric flow rate control valve) described in patent document 1 includes: a main valve element (valve core) for opening and closing a main valve port (valve hole) of the valve chamber; a main valve spring (first spring) for urging the main valve element in a closing direction; an auxiliary valve element for opening and closing an auxiliary valve port (auxiliary valve hole) formed in the main valve element; an auxiliary valve spring (second spring) for urging the auxiliary valve body in a closing direction; and a drive unit having an electric motor (motor) for driving the sub-valve body. In this motor-driven valve, the main valve body biased by the main valve spring is seated to close the main valve port, and the sub valve body biased by the sub valve spring is seated to close the sub valve port, thereby achieving a fully closed state. Then, the sub valve body is pulled up by the driving portion to open the sub valve port, thereby performing small flow rate control. Further, the main valve is pulled up by engaging the locking portion (first stopper) of the pulled-up sub valve body with the main valve body, and the main valve port is opened, thereby performing the large flow rate control.
Documents of the prior art
Patent document 1: japanese patent laid-open No. 2014-20457
Disclosure of Invention
Problems to be solved by the invention
However, the conventional motor-operated valve described in patent document 1 is configured such that: the sub-valve port is formed in a cylindrical shape elongated along the axis, a long rod-shaped sub-valve body is loosely inserted into the sub-valve port, and a gap between an inner peripheral surface of the sub-valve port and an outer peripheral surface of the sub-valve body serves as a flow path for the refrigerant during small flow rate control. Since the fluid passes through such a long and narrow flow path, in the conventional motor-operated valve, foreign matter flows into the flow path and gets stuck between the sub-valve port and the sub-valve body, and there is a possibility that malfunction of the sub-valve body occurs, which causes a problem in flow rate control at the time of small flow rate control.
The invention aims to provide an electrically operated valve, which can appropriately control the flow rate in a small flow rate control area in the electrically operated valve with two-stage flow rate control areas.
The motor-operated valve of the present invention comprises: a main valve element for opening and closing a main valve port of the valve chamber; an auxiliary valve element which can change the opening degree of an auxiliary valve port arranged on the main valve element; and a drive unit that drives the sub-valve body to advance and retract in an axial direction, wherein the electric valve has a two-stage flow control region in which the sub-valve body changes an opening degree of the sub-valve port, and a large flow control region in which the main valve body opens and closes the main valve port, and is characterized in that, in the small flow control region, the sub-valve body moves between a first position at which the sub-valve body is closest to the sub-valve port and a second position at which the sub-valve body moves in an opening direction for opening the sub-valve port by a driving force of the drive unit and engages with the main valve body, and in the large flow control region, the main valve body moves between a closed position at which the main valve body is seated on the main valve port and an open position, the open position is a position at which the main valve element moves integrally with the sub valve element that has moved to the second position by the driving force of the driving unit to open the main valve port, the main valve element is provided with the sub valve port and an engaged portion on the main valve port side of the sub valve port on an inner peripheral surface that is formed in a cylindrical shape as a whole, the sub valve element is formed in a columnar shape as a whole and is disposed inside the main valve element, and has a sub valve portion that is disposed on an outer peripheral surface of the sub valve element and changes the opening degree of the sub valve port, and a locking portion that is disposed on a tip side of the sub valve portion and is capable of locking the engaged portion, and at least one of the main valve element and the sub valve element is provided with a bypass flow path that reaches a tip end portion of the sub valve element while bypassing a contact surface between the engaged portion and the locking portion.
According to the present invention, the sub-valve body disposed inside the main valve body includes the sub-valve portion and the locking portion, and the bypass flow path that reaches the tip end portion of the sub-valve body while bypassing the contact surface between the locked portion and the locking portion is formed in at least one of the main valve body and the sub-valve body. Therefore, a malfunction of the sub-valve body is less likely to occur, and the flow rate in the small flow rate control region can be appropriately controlled. Further, since the bypass flow path is provided, the fluid does not pass through the gap between the locking portion of the sub-valve body and the inner peripheral surface of the main valve body, the gap can be set small, and the gap can function as a slide guide portion that guides the locking portion of the sub-valve body and the inner peripheral surface of the main valve body to slide with each other. Accordingly, the main valve body is guided by the inner peripheral surface of the main valve body when the main valve body moves forward and backward, and the main valve body is guided by the locking portion of the main valve body when the main valve body moves forward and backward.
In this case, the bypass route is preferably configured by at least one of: a through flow path that penetrates from a side surface between the sub valve portion and the engagement portion to a distal end portion of the sub valve body; a sub valve notch portion formed by cutting out an outer peripheral surface of the sub valve body including the engagement portion; and a main valve notch formed by cutting off an inner peripheral surface of the main valve body.
If the bypass flow path is formed by a through flow path, the sliding contact surface where the inner peripheral surface of the main valve element and the outer peripheral surface of the sub valve element are in sliding contact with each other can be continued over the entire circumference, and the sliding resistance becomes constant, whereby the forward and backward movement of the main valve element and the sub valve element can be further stabilized. Further, if the bypass flow path is formed by the sub-valve notch portion and the main-valve notch portion, the processing is simplified as compared with the case of forming the through flow path, and the manufacturing cost can be suppressed.
In this case, it is preferable that the driving portion includes a screw feed mechanism having a male screw portion integrally connected to the sub-valve and a female screw portion screwed and guided by the male screw portion, and the driving portion drives the sub-valve to advance and retreat in the axial direction by the male screw portion being guided and rotated by the female screw portion.
According to this configuration, the external thread portion integrally connected to the sub-valve body is guided by the internal thread portion to drive the sub-valve body to advance and retreat, so that the sub-valve body can be directly driven by the driving portion, and further, the fluctuation of the sub-valve body can be suppressed to improve the accuracy of flow rate control in the small flow rate control region.
Preferably, the locking portion, the sub-valve portion, and the male screw portion are formed so as to have successively smaller diameters.
According to this configuration, since the engagement portion having a diameter larger than the diameter of the sub-valve portion and the external thread portion and the sub-valve portion having a diameter larger than the diameter of the external thread portion is provided at the distal end portion of the sub-valve body, the sub-valve body can be assembled by inserting the main valve body, which is cylindrical as a whole, from one side of the external thread portion, and further, the manufacturing efficiency of the electric valve can be improved.
Preferably, the valve further includes a valve body constituting the valve chamber, a support member fixed to the valve body, and a main valve spring biasing the main valve element in a closing direction, the support member being made of a resin molded member and including: the internal thread portion; a spring seat portion that holds the main valve spring in a compressed state between the main valve element and the main valve seat; and a main valve guide portion for guiding the main valve core to advance and retreat along the axial direction.
According to this configuration, the support member fixed to the valve main body has the female screw portion, the spring seat portion, and the main valve guide portion guides the main valve body to advance and retreat in the axial direction, whereby the vibration of the main valve body can be suppressed, and the main valve body can be reliably seated on the main valve port, thereby preventing the valve leakage. Therefore, the influence on the flow rate at the time of small flow rate control for opening the sub-port is reduced, and the flow rate in the small flow rate control region can be appropriately controlled. Further, since the support member is formed of a resin molded member, abrasion of the support member and the main valve body can be suppressed, and durability of the motor-operated valve can be improved.
The refrigeration cycle system of the present invention includes a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that the expansion valve is an electrically operated valve as described in any one of the above.
According to such a refrigeration cycle, as well as the effect of the above-described motor-operated valve, by preventing the engagement of foreign matter in the sub-valve port, it is difficult for a malfunction of the sub-valve body to occur, and therefore, in a refrigeration cycle using a motor-operated valve as an expansion valve, the flow rate at the time of small flow rate control can be appropriately controlled.
The effects of the invention are as follows.
According to the electric valve and the refrigeration cycle system of the present invention, in the electric valve having the two-stage flow rate control region, the flow rate in the small flow rate control region can be appropriately controlled.
Drawings
Fig. 1 is a vertical cross-sectional view showing a fully closed state of an electrically operated valve according to an embodiment of the present invention.
Fig. 2 is a longitudinal sectional view showing a fully opened state of the motor-operated valve.
Fig. 3 (a) and (B) are vertical sectional views showing a part of the motor-operated valve in an enlarged manner.
Fig. 4 is a graph showing a relationship between the valve opening degree and the flow rate of the electrically operated valve.
Fig. 5 is a schematic configuration diagram showing a refrigeration cycle system of the present invention.
Fig. 6 (a) and (B) are a vertical sectional view and a bottom view showing a part of an electrically operated valve in an enlarged manner according to a modification of the present invention.
Fig. 7 (a) and (B) are a vertical sectional view and a bottom view showing a part of an electrically operated valve in another modification of the present invention in an enlarged manner.
In the figure:
10-an electric valve, 1 d-a main valve port, 2-a main valve core, 3-a sub valve core, 4-a driving portion, 13-a support member, 13 a-a main valve guide portion, 13 b-an internal thread portion, 13 c-a spring seat portion, 22-a sub valve port, 23-an engaged portion, 26-a main valve spring, 31-a sub valve portion, 34-a thrust washer (an engaged portion), 35-a through flow path, 36-a sub valve notch portion, 37-a main valve notch portion, 42-a screw feed mechanism, 50 b-an external thread portion, 91-a first indoor side heat exchanger, 92-a second indoor side heat exchanger, 93-a compressor, 95-an outdoor side heat exchanger, and R' -a bypass flow path.
Detailed Description
An electrically operated valve according to an embodiment of the present invention will be described with reference to fig. 1 to 4. As shown in fig. 1 and 2, the motor-operated valve 10 of the present embodiment includes a valve housing 1, a main valve element 2, a sub valve element 3, and a drive unit 4. Note that the concept of "top and bottom" in the following description corresponds to the top and bottom in the drawings of fig. 1 and 2.
The valve housing 1 has a cylindrical valve body 1A, and the valve body 1A is made of brass (made of an alloy of copper and zinc), and a cylindrical valve chamber 1A is formed inside thereof. A primary joint pipe 11 that communicates with the valve chamber 1A from the side surface side to allow the refrigerant to flow in is attached to the valve main body 1A, and a secondary joint pipe 12 that communicates with the valve chamber 1A from the bottom surface side to allow the refrigerant to flow out is attached to the valve main body 1A. Further, in the valve main body 1A, a main valve seat 1b is formed at a position where the valve chamber 1A and the secondary joint pipe 12 communicate with each other, and a main valve port 1c having a circular cross-sectional shape is formed at a position closer to the secondary joint pipe 12 side than the main valve seat 1 b. A support member 13 and a housing 15 are fixed to an upper opening of the valve main body 1 a.
The support member 13 is a resin molded member formed in a substantially cylindrical shape as a whole, and is fixed to the valve housing 1 via a metal fixing member 14 welded to the upper opening of the valve main body 1 a. The support member 13 has: a cylindrical main valve guide portion 13a extending downward from the fixing member 14; a female screw portion 13b extending upward from the fixing member 14 and having a female screw formed therein; and a spring seat portion 13c provided at the inner upper end of the tubular shape. The resin material constituting the support member 13 may be a material having appropriate hardness and heat resistance, and various engineering plastics may be used. The housing 15 is fixed to the upper opening of the valve main body 1a by welding or the like, and an airtight space is formed by the valve main body 1a and the housing 15.
The main valve element 2 is a stainless steel member formed in a substantially cylindrical shape as a whole, and is supported so as to be movable in the vertical direction along the axis L inside the main valve guide portion 13a of the support member 13. Main valve element 2 has: a main valve portion 21 that seats on and unseats from the main valve seat 1 b; an annular sub-valve port 22 projecting from the cylindrical inner peripheral surface; an engaged portion 23 formed in a stepped shape on an inner peripheral surface on the main valve port 1c side (lower side) of the sub valve port 22; and a spring seat 24 provided at the upper end portion. The auxiliary valve chamber 2A is defined by an internal space of the main valve element 2 above the auxiliary valve port 22 and an internal space of the support member 13. A through hole 25 is formed in a side surface of the main valve element 2, and the valve chamber 1A and the sub-valve chamber 2A communicate with each other through the through hole 25. A main valve spring 26 is disposed in a compressed state between the support member 13 and the spring seat portions 13c and 24 of the main valve 2, and the main valve spring 26 biases the main valve 2 in the direction of the main valve seat 1b (closing direction).
The sub-valve body 3 is a stainless steel member formed in a substantially cylindrical shape as a whole, is disposed inside the main valve body 2, is integrally connected to a lower end portion of a rotor shaft (valve shaft) 50 of a drive unit 4 described later, and is driven by the drive unit 4 to advance and retract and rotate. The sub-valve body 3 includes: an auxiliary valve portion 31 provided on the outer peripheral surface thereof and changing the opening degree of the auxiliary valve port 22; a small diameter portion 32 formed to have a small diameter and provided on the front end side (lower side) of the sub valve portion 31; and a flange portion 33 provided at the tip of the small diameter portion 32 and formed to have a larger diameter than the sub valve portion 31. A thrust washer 34 composed of a high-slip surface washer made of metal, a high-slip resin washer made of fluororesin, or the like, or a high-slip resin-coated washer is provided on the upper side of the flange portion 33, and this thrust washer 34 serves as a locking portion capable of locking the locked portion 23 of the main valve element 2. The thrust washer 34 can be brought into contact with the upper surface of the flange portion 33 and the engaged portion 23, and the frictional force between the contact surfaces is extremely small. A through flow passage 35 that penetrates the sub-valve body 3 is provided between a side surface of the small diameter portion 32 and a lower surface of the flange portion 33, the side surface of the small diameter portion 32 is between the sub-valve portion 31 and the flange portion 33, and the lower surface of the flange portion 33 is a tip end portion of the sub-valve body 3.
The drive unit 4 includes: a stepping motor 41 as an electric motor; a screw feed mechanism 42 for advancing and retracting the sub-valve body 3 by rotation of the stepping motor 41; and a stopper mechanism 43 for restricting the rotation of the stepping motor 41.
The stepping motor 41 includes: a magnetic rotor 44 magnetized in a multi-pole manner at its outer periphery; a stator coil 45 disposed on the outer periphery of the housing 15; and a rotor shaft 50 fixed to the magnetic rotor 44 and extending in the direction of the axis L. The stepping motor 41 applies a pulse signal to the stator coil 45 to rotate the magnetic rotor 44 in accordance with the number of pulses.
The rotor shaft 50 is a long rod-shaped member fixed to the magnetic rotor 44 via a fixing member 50a, and is formed integrally with the sub-valve body 3 by machining such as cutting or roll forming a metal material such as stainless steel. A male screw portion 50b is integrally formed at an intermediate portion of the rotor shaft 50, and the male screw portion 50b is screwed to the female screw portion 13b of the support member 13, thereby constituting the screw feeding mechanism 42. The upper end portion of the rotor shaft 50 is inserted into the guide 46 of the stopper mechanism 43 and guided in the direction of the axis L. In the rotor shaft 50 and the sub-valve body 3 which are integrally formed, the diameters of the flange portion 33, the thrust washer 34, the sub-valve portion 31, and the male screw portion 50b are sequentially made smaller, that is, the outer diameter of the thrust washer 34 is the largest, the outer diameter of the sub-flange portion 33 is the next largest, the outer diameter of the sub-valve portion 31 is again made smaller, and the outer diameter of the male screw portion 50b is the smallest.
When the magnetic rotor 44 and the rotor shaft 50 of the driving unit 4 rotate, the male screw portion 50b is guided by the female screw portion 13b, and the magnetic rotor 44 and the rotor shaft 50 move in the direction of the axis L according to the pitch. Here, the magnetic rotor 44 and the rotor shaft 50 descend in accordance with the normal rotation thereof, and the sub-valve body 3 also descends in accordance with the descent. On the other hand, the magnetic rotor 44 and the rotor shaft 50 rise along with the reverse rotation thereof, and the sub-valve body 3 also rises along with the rise.
The stopper mechanism 43 includes: a cylindrical bar-shaped guide 46 hanging down from the top of the housing 15; a guide screw portion 47 fixed to the outer periphery of the guide 46; and a movable slider 48 guided by the guide screw portion 47 to be capable of moving up and down while rotating. The movable slider 48 is provided with a claw portion 48a protruding radially outward, the magnetic rotor 44 is provided with an extended portion 44a extending upward and abutting against the claw portion 48a, and when the magnetic rotor 44 rotates, the extended portion 44a presses the claw portion 48a, and the movable slider 48 moves up and down while rotating along the guide screw portion 47.
The guide screw portion 47 is formed with an upper end stopper 47a that defines the uppermost end position of the magnetic rotor 44, and a lower end stopper 47b that defines the lowermost end position of the magnetic rotor 44. When the movable slider 48 that has descended with the normal rotation of the magnetic rotor 44 comes into contact with the lower end stopper 47b, the movable slider 48 cannot rotate at the contact position, and the rotation of the magnetic rotor 44 is restricted, and the descent of the sub-valve body 3 is also stopped. On the other hand, when the movable slider 48 that has risen as the magnetic rotor 44 rotates reversely contacts the upper end stopper 47a, the movable slider 48 cannot rotate at the contact position, and thus the rotation of the magnetic rotor 44 is restricted, and the rise of the sub-valve body 3 is also stopped.
Next, a detailed structure of the motor-operated valve 10 and an operation thereof will be described with reference to fig. 3 and 4. Fig. 3 (a) and (B) are longitudinal sectional views showing a part of the electric valve 10 in an enlarged manner, and are longitudinal sectional views showing the tip end portions of the main valve body 2 and the sub valve body 3 in an enlarged manner. Fig. 4 is a graph showing a relationship between the valve opening degree and the flow rate of the electric valve 10.
As shown in fig. 3, the sub valve portion 31 of the sub spool 3 is formed to have: a cylindrical columnar portion 31 a; and a truncated cone-shaped conical portion 31b having a diameter gradually smaller toward the front end than the cylindrical portion 31 a. The diameter of the cylindrical portion 31a is formed smaller than the inner diameter of the sub-valve port 22 of the main valve element 2, and a flow path R through which the refrigerant passes is formed by a gap between the outer peripheral surfaces of the cylindrical portion 31a and the conical portion 31b and the inner peripheral surface of the sub-valve port 22. Fig. 3 (a) shows the sub-valve body 3 at a first position closest to the sub-valve port 22, where the cylindrical portion 31a is located inside the sub-valve port 22 corresponding to the lowest end position of the magnetic rotor 44. Fig. 3 (B) shows the sub-valve body 3 in a second position engaged with the main valve body 2, where the sub-valve body 3 is raised from the first position by the rotation of the magnetic rotor 44 and the thrust washer 34 abuts against the engaged portion 23. When the sub-valve body 3 moves upward from the first position toward the second position, the conical portion 31b is positioned inside the sub-valve port 22, the opening degree of the sub-valve port 22 gradually increases, and the flow rate of the refrigerant passing through the flow path R increases.
The above motor-operated valve 10 operates as follows. First, in the state of fig. 1 and 3 (a), the main valve portion 21 of the main valve 2 is seated on the main valve seat 1b, and the main valve port 1c is closed. On the other hand, in the sub-valve body 3 located at the first position, the columnar portion 31a is located inside the sub-valve port 22, and a flow path R is formed in a slit thereof. Therefore, the refrigerant that flows into the valve chamber 1A from the primary joint pipe 11 and flows into the sub valve chamber 2A from the through hole 25 flows from the flow path R into the main valve body 2 through the sub port 22, flows out to the tip end side of the sub valve body 3 through the through flow path 35 of the sub valve body 3, and then flows out from the main valve port 1c toward the secondary joint pipe 12. That is, the through flow path 35 of the sub-valve body 3 forms a bypass flow path R' that bypasses the contact surface between the thrust washer 34 and the engaged portion 23. By passing the refrigerant through the flow path R and the bypass flow path R' in this manner, a minute flow rate is generated even if the valve opening degree is zero as shown in fig. 4.
Next, the stepping motor 41 of the drive unit 4 is driven to rotate the magnetic rotor 44 in the reverse direction to raise the sub-valve body 3, so that the conical portion 31b of the sub-valve body 3 is positioned inside the sub-valve port 22, and a flow path R is formed in a gap thereof. Here, since the diameter of the conical portion 31b gradually decreases, the gap with the inner peripheral surface of the sub-valve port 22 increases, the flow path R expands, and the flow rate gradually increases as shown in fig. 4. At this time, since the main valve portion 21 of the main valve body 2 remains seated on the main valve seat 1b, the flow rate increases slightly until the second position where the sub valve body 3 engages with the main valve body 2. In this way, the control region in which the opening degree is changed by moving the sub-valve body 3 between the first position and the second position is a small flow rate control region in which the flow rate changes very slightly with respect to the opening degree of the sub-valve body 3 (the amount of rotation of the stepping motor 41).
Next, when the sub-valve body 3 that has risen to the second position and engaged with the main valve body 2 is further raised, the main valve body 2 is pulled up by the sub-valve body 3, and the main valve portion 21 is separated from the main valve seat 1B and opened, as shown in fig. 2 and 3 (B). Thus, the control region for raising main valve element 2 from the seated position (closed position) to the valve-open position (open position) is a large flow rate control region in which the flow rate greatly changes with respect to the opening degree of main valve element 2 (the amount of rotation of stepping motor 41). In the fully open state shown in fig. 2 and 3 (B), in which the main valve 2 is raised to the valve open position, the flow rate is maximized. Here, as the flow rate in the fully open state, the opening area of the gap between the main valve portion 21 and the main valve seat 1b is set to be equal to or larger than the opening areas of the primary joint pipe 11 and the secondary joint pipe 12, and the flow rate is set to a state where the main valve portion 21 and the main valve port 1c do not throttle, that is, an opening degree at which the electric valve 10 functions as a simple flow path. Then, the stepping motor 41 of the driving unit 4 is driven to rotate the magnetic rotor 44 in the normal direction to lower the sub-valve body 3, so that the main valve body 2 biased by the main valve spring 26 also lowers, the main valve portion 21 is seated on the main valve seat 1b, the main valve port 1c is closed, and a small flow control region is formed.
According to the present embodiment described above, the sub-valve body 3 disposed inside the main valve body 2 has the through flow path 35, and at the time of small flow rate control, the refrigerant flows through the through flow path 35 toward the tip side of the sub-valve body 3, so that it is possible to prevent foreign matter from being caught between the main valve body 2 and the sub-valve body 3. Therefore, a malfunction of the sub-valve body 3 is less likely to occur, and the flow rate in the small flow rate control region can be appropriately controlled.
Further, since the through flow path 35 is provided, the refrigerant does not pass through a gap between the thrust washer 34, which is the locking portion of the sub-valve body 3, and the inner peripheral surface of the main valve body 2, and the gap can be set small, and the gap can function as a slide guide portion for guiding the thrust washer 34 and the inner peripheral surface of the main valve body 2 to slide with each other. Further, since the bypass flow path R' is formed by the through flow path 35, a sliding contact surface where the inner peripheral surface of the main valve element 2 and the outer peripheral surface of the sub valve element 3 slide against each other can be continuous over the entire circumference. This allows the sub-valve body 3 to be guided by the inner peripheral surface of the main valve body 2 during the forward and backward movement, and thus suppresses the vibration of the sub-valve body 3, thereby improving the accuracy of the flow rate control. Further, the main valve 2 is restricted in vibration by the thrust washer 34 even when seated on the main valve seat 1b, so that the valve closing performance is improved and the valve leakage amount can be reduced.
Further, the male screw portion 50b of the rotor shaft 50 integrally connected to the sub-valve body 3 is guided by the female screw portion 13b to drive the sub-valve body 3 to advance and retreat, so that the sub-valve body 3 can be directly driven by the driving portion 4, and further, the fluctuation of the sub-valve body 3 can be suppressed to improve the accuracy of flow rate control in the small flow rate control region.
Further, by providing the thrust washer 34 as the engagement portion at the distal end portion of the sub-valve body 3 and forming the thrust washer 34, the sub-valve portion 31, and the male screw portion 50b to have successively smaller diameters, the sub-valve body 3 can be assembled by inserting the male screw portion 50b, the sub-valve portion 31, the thrust washer 34, and the flange portion 33 in this order from the upper end side of the rotor shaft 50 into the main valve body 2, which is cylindrical as a whole, and the manufacturing efficiency of the motor-operated valve 10 can be improved.
The support member 13 fixed to the valve main body 1 has a main valve guide 13a, a female screw portion 13b, and a spring seat portion 13c, and the main valve 2 is guided by the main valve guide 13a to advance and retreat in the direction of the axis L, so that vibration of the main valve 2 can be suppressed, and valve leakage can be prevented by reliably seating the main valve 2 on the main valve seat 1 b. Therefore, the influence on the flow rate at the time of small flow rate control for opening the sub-port 22 can be reduced, and the flow rate in the small flow rate control region can be appropriately controlled. Further, since the support member 13 is formed of a resin molded member, abrasion of the support member 13 and the main valve element 2 can be suppressed, and durability of the motor-operated valve 10 can be improved.
Further, by forming the flow path R by a gap between the outer peripheral surface of the columnar portion 31a of the sub-valve body 3 located at the first position and the inner peripheral surface of the main valve body 2, the valve-opening type motor-operated valve 10 that always ensures a flow rate can be configured by the flow path R. The valve-opening type motor-operated valve 10 can be suitably applied to an air conditioner having a dehumidifying function such as a home air conditioner. Further, by forming the flow path R by a gap between the outer peripheral surface of the columnar portion 31a and the inner peripheral surface of the main valve element 2, the opening area of the flow path R can be strictly defined, and a small flow rate when the sub-valve element 3 is at the first position can be appropriately secured.
Next, a refrigeration cycle system of the present invention will be described with reference to fig. 5. The refrigeration cycle 90 is applied to, for example, an air conditioner such as a home air conditioner. The motor-operated valve 10 of the above embodiment is provided between the first indoor-side heat exchanger 91 (which operates as a cooler during dehumidification) and the second indoor-side heat exchanger 92 (which operates as a heater during dehumidification) of the air conditioner, and constitutes a heat pump refrigeration cycle together with the compressor 93, the four-way valve 94, the outdoor-side heat exchanger 95, and the electronic expansion valve 96. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated valve 10 are installed indoors, and the compressor 93, the four-way valve 94, the outdoor heat exchanger 95, and the electronic expansion valve 96 are installed outdoors, thereby constituting a cooling/heating apparatus.
The present invention is not limited to the above-described embodiments, and 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 described below. For example, in the above-described embodiment, the electrically operated valve 10 used in an air conditioner such as a home air conditioner is exemplified, but the electrically operated valve of the present invention is not limited to the home air conditioner, and may be a commercial air conditioner, and may be applied to various refrigerators and the like without being limited to the air conditioner.
Further, in the above embodiment, the screw feeding mechanism 42 is constituted by the male screw portion 50b of the rotor shaft 50 and the female screw portion 13b of the support member 13, but the configuration of the screw feeding mechanism that drives the sub-valve 3 to advance and retreat is not limited to the above embodiment, and any configuration may be adopted. The mechanism for driving the sub-valve body to advance and retreat is not limited to the screw feed mechanism, and an appropriate mechanism can be applied.
In the above embodiment, the stopper mechanism 43 is constituted by the guide 46, the guide screw portion 47, and the movable slider 48 provided on the top portion of the housing 15, but the stopper mechanism may be configured to restrict the rotation of the magnetic rotor 44, and the arrangement position and the structure thereof are not particularly limited. For example, the magnetic rotor may be provided with a stopper mechanism on the inner side and the lower side.
Further, in the above-described embodiment, the bypass flow path R 'is constituted by the through flow path 35, but as shown in fig. 6 and 7, the bypass flow path R' may be constituted by the sub-valve notch 36 and the main valve notch 37, and the through flow path 35, the sub-valve notch 36, and the main valve notch 37 may be appropriately combined. Specifically, as shown in fig. 6, the sub-valve notch portion 36 is formed as a D-shaped cut surface in which a part of the outer peripheral surface is cut away from the small diameter portion 32 to the flange portion 33 of the sub-valve body 3. Therefore, the bypass flow path R' is formed to pass through the small diameter portion 32 and the inside of the thrust washer 34. On the other hand, as shown in fig. 7, the bypass flow path R' is formed by cutting a part of the inner peripheral surface from the engaged portion 23 of the main valve 2 to the main valve portion 21. Therefore, the bypass flow path R' is formed to pass through the small diameter portion 32 of the sub-valve body 3, outside the thrust washer 34, and outside the flange portion 33.
While the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to the embodiments, and the present invention includes design changes and the like within a range not departing from the gist of the present invention.
Claims (6)
1. An electrically operated valve comprising: a main valve element for opening and closing a main valve port of the valve chamber; an auxiliary valve element which can change the opening degree of an auxiliary valve port arranged on the main valve element; and a driving part for driving the auxiliary valve core to move forward and backward along the axial direction,
the electric valve has two-stage flow control regions, i.e., a small flow control region in which the opening of the sub valve port is changed by the sub valve body and a large flow control region in which the main valve body opens and closes the main valve port,
the above-mentioned electric valve is characterized in that,
in the small flow rate control region, the sub-valve body moves between a first position where the sub-valve body is closest to the sub-valve port and a second position where the sub-valve body moves in an opening direction for opening the sub-valve port by the driving force of the driving portion and engages with the main valve body,
in the large flow rate control region, the main valve element moves between a closed position where the main valve element is seated on the main valve port and an open position where the main valve element moves integrally with the sub valve element moved to the second position by the driving force of the driving portion to open the main valve port,
the main valve core is provided with the sub-valve port and an engaged part closer to the main valve port than the sub-valve port on an inner peripheral surface which is formed in a cylindrical shape as a whole,
the sub valve body is formed in a columnar shape as a whole, is disposed inside the main valve body, and has a sub valve portion provided on an outer peripheral surface of the sub valve body and changing an opening degree of the sub valve port, and a locking portion provided on a front end side of the sub valve portion and capable of locking the locked portion,
in the first position, a flow path through which the fluid in the valve chamber flows out to the main valve port through a gap between an outer peripheral surface of the sub valve portion and an inner peripheral surface of the sub valve port is provided, and a bypass flow path that bypasses a contact surface between the engaged portion and the engagement portion and reaches a tip end portion of the sub valve body is formed in at least one of the main valve body and the sub valve body.
2. Electrically operated valve according to claim 1,
the bypass route is constituted by at least one of:
a through flow path that penetrates from a side surface between the sub valve portion and the engagement portion to a distal end portion of the sub valve body;
a sub valve notch portion formed by cutting out an outer peripheral surface of the sub valve body including the engagement portion; and
and a main valve notch formed by cutting off an inner peripheral surface of the main valve body.
3. Electrically operated valve according to claim 1 or 2,
the drive portion includes a screw feed mechanism having a male screw portion integrally connected to the sub-valve body and a female screw portion screwed and guided by the male screw portion,
the external thread portion is guided and rotated by the internal thread portion by the driving of the driving portion, and the sub-valve body is driven to advance and retreat in the axial direction.
4. Electrically operated valve according to claim 3,
the locking portion, the sub-valve portion, and the male screw portion are formed so that the diameters thereof become smaller in order.
5. Electrically operated valve according to claim 3,
further comprising a valve body constituting the valve chamber, a support member fixed to the valve body, and a main valve spring biasing the main valve element in a closing direction,
the support member is formed of a resin molded member and includes: the internal thread portion; a spring seat portion that holds the main valve spring in a compressed state between the main valve element and the main valve seat; and a main valve guide portion for guiding the main valve core to advance and retreat along the axial direction.
6. A refrigeration cycle system comprises a compressor, a condenser, an expansion valve and an evaporator, and is characterized in that,
an electrically operated valve as claimed in any one of claims 1 to 5 is used as the expansion valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-016785 | 2018-02-01 | ||
| JP2018016785A JP6857624B2 (en) | 2018-02-01 | 2018-02-01 | Electric valve and refrigeration cycle system |
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| Publication Number | Publication Date |
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| CN110107724A CN110107724A (en) | 2019-08-09 |
| CN110107724B true CN110107724B (en) | 2021-02-19 |
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| CN201910032327.XA Active CN110107724B (en) | 2018-02-01 | 2019-01-14 | Electric valve and refrigeration cycle system |
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| JP (1) | JP6857624B2 (en) |
| CN (1) | CN110107724B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7208127B2 (en) * | 2019-10-11 | 2023-01-18 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
| JP7337666B2 (en) * | 2019-11-07 | 2023-09-04 | 愛三工業株式会社 | valve device |
| CN111022653B (en) * | 2019-11-18 | 2022-03-22 | 宁波奥克斯电气股份有限公司 | Electronic expansion valve, adjusting method and air conditioner |
| JP7361628B2 (en) * | 2020-02-19 | 2023-10-16 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
| CN212079907U (en) * | 2020-03-30 | 2020-12-04 | 盾安环境技术有限公司 | Nut assembly and electronic expansion valve |
| JP7349963B2 (en) * | 2020-07-01 | 2023-09-25 | 株式会社鷺宮製作所 | Flow control valve and refrigeration cycle system |
| JP7372885B2 (en) * | 2020-08-07 | 2023-11-01 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
| JP7485962B2 (en) * | 2021-10-25 | 2024-05-17 | ダイキン工業株式会社 | Air Conditioning Equipment |
| WO2023208036A1 (en) * | 2022-04-29 | 2023-11-02 | 浙江三花汽车零部件有限公司 | Electric valve, and integrated assembly |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5076424U (en) * | 1973-11-15 | 1975-07-03 | ||
| JP2014020457A (en) * | 2012-07-18 | 2014-02-03 | Rinnai Corp | Electric flow rate regulating valve |
| JP2014142073A (en) * | 2014-04-23 | 2014-08-07 | Fuji Koki Corp | Motor valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009036182A (en) * | 2007-08-03 | 2009-02-19 | Fuji Koki Corp | Control valve for variable capacity compressor |
| JP3145048U (en) * | 2008-07-11 | 2008-09-25 | 株式会社鷺宮製作所 | Electric expansion valve and refrigeration cycle |
| JP5726506B2 (en) * | 2010-12-21 | 2015-06-03 | 株式会社不二工機 | Electric pilot type control valve |
| JP5684746B2 (en) * | 2012-02-10 | 2015-03-18 | 株式会社鷺宮製作所 | Expansion valve |
| JP5627612B2 (en) * | 2012-02-10 | 2014-11-19 | 株式会社鷺宮製作所 | Expansion valve |
| JP6721175B2 (en) * | 2016-06-13 | 2020-07-08 | 株式会社不二工機 | Motorized valve |
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2018
- 2018-02-01 JP JP2018016785A patent/JP6857624B2/en active Active
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5076424U (en) * | 1973-11-15 | 1975-07-03 | ||
| JP2014020457A (en) * | 2012-07-18 | 2014-02-03 | Rinnai Corp | Electric flow rate regulating valve |
| JP2014142073A (en) * | 2014-04-23 | 2014-08-07 | Fuji Koki Corp | Motor valve |
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|---|---|
| JP6857624B2 (en) | 2021-04-14 |
| CN110107724A (en) | 2019-08-09 |
| JP2019132393A (en) | 2019-08-08 |
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