CN115507187A - Electric valve - Google Patents

Electric valve Download PDF

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Publication number
CN115507187A
CN115507187A CN202210348039.7A CN202210348039A CN115507187A CN 115507187 A CN115507187 A CN 115507187A CN 202210348039 A CN202210348039 A CN 202210348039A CN 115507187 A CN115507187 A CN 115507187A
Authority
CN
China
Prior art keywords
valve
rectifying
shaft portion
valve seat
hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210348039.7A
Other languages
Chinese (zh)
Inventor
矢泽将志
大内共存
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujikoki Corp filed Critical Fujikoki Corp
Publication of CN115507187A publication Critical patent/CN115507187A/en
Pending legal-status Critical Current

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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
    • F16K1/02—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 with screw-spindle
    • 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
    • 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
    • F16K1/38—Valve members of conical shape
    • F16K1/385—Valve members of conical shape contacting in the closed position, over a substantial axial length, a seat surface having the same inclination
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0254—Construction of housing; Use of materials therefor of lift valves with conical shaped valve members
    • 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
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • 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
    • F16K31/44—Mechanical actuating means
    • F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)

Abstract

The invention provides an electrically operated valve capable of further reducing noise. The electric valve has: a valve body which can be connected to a pipe and is provided with a valve chamber; a valve seat member attached to the valve main body and including a valve seat; a valve element disposed in the valve chamber and capable of being seated on the valve seat; a valve holder disposed in the valve chamber and holding the valve body, the valve seat member having a cylindrical portion that protrudes into the valve chamber and in which a rectifying hole communicating with the valve seat is formed, the valve body including: a holding shaft portion held by the valve holder; a conical portion which can be seated on the valve seat; and a rectifying shaft portion disposed between the holding shaft portion and the conical portion, wherein an inner diameter of the rectifying hole is smaller than an outer diameter of an end portion of the valve holder on a side close to the rectifying hole, the rectifying shaft portion is positioned in the rectifying hole at least when the valve is closed, and a cross-sectional area of a gap between the rectifying shaft portion and the rectifying hole is larger than a cross-sectional area of a gap between the valve element and the valve seat when an end portion of the rectifying shaft portion on the conical portion side is positioned in the rectifying hole as viewed in an axial direction of the motor-operated valve.

Description

Electric valve
Technical Field
The present invention relates to an electrically operated valve.
Background
An electrically operated valve used as a flow rate control valve in a refrigeration cycle includes a screw mechanism in which a male screw portion of a valve shaft rotated by an electric motor is screwed into a female screw hole provided in a valve body, and the valve shaft is displaced in an axial direction by converting a rotational motion into an axial motion by the screw mechanism to control a flow rate. In such an electrically operated valve, it is required to suppress the sound of refrigerant passing therethrough.
For example, patent document 1 discloses an electrically operated valve in which a passage a formed from a valve chamber to a valve port side in a first refrigerant cycle system is formed in a conical shape, and a passage B formed from a tip end of the passage B to the valve port side in a second refrigerant cycle system is formed in a conical shape, thereby reducing fluid flow noise caused by a vortex.
Documents of the prior art
Patent literature
Patent document 1: japanese patent laid-open No. 2008-128603
Technical problem to be solved by the invention
In particular, in recent years, automobiles have been driven to be electrically powered, and in electrically powered vehicles, the requirement for noise reduction is becoming more severe because operating sound of air conditioners and the like is easily transmitted to occupants in the vehicle interior. Therefore, further improvement in silencing is also required in the motor-operated valve.
In the refrigeration cycle, the refrigerant generally flows in a two-phase gas-liquid state from the pipe into the valve body of the motor-operated valve. As a result of the study by the present inventors, it was found that there are cases: when the refrigerant passing through the orifice is in a gas phase state, the sound passing through the orifice changes and may be recognized as noise as compared to when in a liquid phase state.
Disclosure of Invention
Therefore, an object of the present invention is to provide an electrically operated valve capable of further reducing noise.
Means for solving the problems
In order to solve the above-described problems, an electrically operated valve according to the present invention includes:
a valve body that can be connected to a pipe and includes a valve chamber;
a valve seat member attached to the valve main body and including a valve seat;
a valve body disposed in the valve chamber and capable of being seated on the valve seat; and
a valve holder disposed in the valve chamber and holding the valve element,
the valve seat member has a cylindrical portion that protrudes into the valve chamber and has a rectifying hole formed inside the cylindrical portion so as to communicate with the valve seat,
the valve element has: a holding shaft portion held by the valve holder, a conical portion capable of seating on the valve seat, and a flow regulating shaft portion disposed between the holding shaft portion and the conical portion,
the inner diameter of the rectifying hole is smaller than the outer diameter of the end part of the valve retainer close to one side of the rectifying hole,
at least when the valve is closed, the rectifying shaft part is positioned in the rectifying hole,
when the end portion of the rectifying shaft portion on the side of the conical portion is positioned in the rectifying hole, the cross-sectional area of the gap between the rectifying shaft portion and the rectifying hole is larger than the cross-sectional area of the gap between the valve element and the valve seat, as viewed in the axial direction of the motor-operated valve.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, it is possible to provide an electrically operated valve capable of further reducing noise.
Drawings
Fig. 1 is a longitudinal sectional view showing an electrically operated valve according to a first embodiment of the present invention.
Fig. 2 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a valve closed state.
Fig. 3 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a state in which the needle valve is positioned at an intermediate position between a valve-closed state and a valve-opened state.
Fig. 4 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a fully opened state of the valve.
Fig. 5 is a longitudinal sectional view showing an electrically operated valve according to a second embodiment of the present invention.
Fig. 6 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a valve closed state.
Fig. 7 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a state in which the needle valve is positioned at an intermediate position between a valve-closed state and a valve-opened state.
Fig. 8 is an enlarged vertical sectional view of the periphery of the valve seat member of the present embodiment, showing a fully opened state of the valve.
Description of the symbols
1. Electric valve
10. Valve body
11. 11A valve seat member
11k valve seat
15. Guide rod
21. Valve shaft
23. Valve retainer
24. Spiral spring
25. Needle valve
26. Spring bearing member
27. Ring-shaped member
29. Valve chamber
30. Rotor
35. Movable stopper for valve closing direction
36. Movable stopper for valve opening direction
55. Fixed stop piece for closing valve direction
56. Fixed stopper for valve opening direction
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[ first embodiment ]
Fig. 1 is a longitudinal sectional view of an electrically operated valve 1 according to a first embodiment of the present invention. Here, the rotor side of the motor-operated valve 1 is referred to as an upper side, and the needle valve side is referred to as a lower side. The "orifice" is a gap between the needle valve and the valve seat when the valve is opened, and the area of an annular surface formed by the outer diameter of the needle valve and the inner diameter of the valve seat at the position where the gap is the smallest is the "orifice cross-sectional area".
(construction of flow control valve)
The motor-operated valve 1 includes: a bottomed cylindrical valve body 10 having an open upper end, a top cylindrical housing 45 having a lower end portion hermetically joined to an upper end surface of the valve body 10 by welding or the like, a guide rod 15 fixed to the inside of the valve body 10, a valve shaft 21 disposed inside the guide rod 15, and a rotor 30 connected and fixed to the valve shaft 21 so as to be rotatable integrally with the valve shaft 21. A stator fitted around the outer periphery of the housing 45 is disposed around the rotor 30 to drive the rotor 30 to rotate, but not shown here. The rotor 30 and the stator constitute a stepping motor. The axis of the motor-operated valve 1 (line coincident with the rotation axis of the rotor) is designated as L.
The valve body 10 is formed by continuously providing a hollow cylindrical portion 10a and a bottom wall portion 10 b. The valve body 10 can be formed by press-forming a plate material made of SUS, but may be formed by pressing a SUS material.
A circular opening 10d is formed in the bottom wall 10b at the center thereof, and a seat member 11 is fixed to the opening 10d by brazing or the like.
Fig. 2 to 4 are vertical sectional views showing the periphery of the valve seat member 11 in an enlarged manner.
The substantially cylindrical valve seat member 11 is formed by continuously providing an upper cylindrical portion 11a, a middle cylindrical portion 11b having a larger diameter than the upper cylindrical portion 11a, and a lower cylindrical portion 11c having a larger diameter than the middle cylindrical portion 11 b.
The valve seat member 11 includes an opening hole 11g, and the opening hole 11g is formed by coaxially arranging a cylindrical upper opening portion (also referred to as a rectifying hole) 11d having a constant inner diameter, a middle opening portion 11e having a larger diameter than the upper opening portion 11d, and a lower opening portion 11f having a diameter that is increased in a tapered manner as going downward from a lower end of the middle opening portion 11 e. Therefore, the seat member 11 has a cylindrical portion that protrudes into the valve chamber 29 and has a rectifying hole formed therein to communicate with the seat 11k. As shown by reference numeral 11Ad in fig. 5 to 8, the upper opening 11d may have a tapered shape whose diameter increases upward.
A valve seat 11k is formed on the upper inner periphery of the middle opening 11e constituting the orifice portion. The thickness between the upper cylindrical portion 11a and the upper opening portion 11d is larger than the thickness of the valve main body 10, and is preferably 1.2 times or more thick. Therefore, the rigidity of the upper cylindrical portion 11a can be increased, vibration during refrigerant passage can be suppressed, and noise reduction can be achieved.
The middle cylindrical portion 11b is fitted in the opening 10d of the valve main body 10, the upper cylindrical portion 11a protrudes into the valve main body 10, and the lower cylindrical portion 11c is disposed outside the valve main body 10. An annular recess 11h is formed in the lower end surface of the lower cylindrical portion 11c coaxially with the axis L. The end of the first pipe T1 that enters the annular recess 11h is connected by brazing or the like.
An inlet opening 10e is formed in the hollow cylindrical portion 10a of the valve main body 10, and an end portion of the second pipe T2 is inserted into the inlet opening 10e and connected thereto by brazing or the like. The axis of the inlet opening 10e is set to O.
In fig. 1, in a state where the lower end of the housing 45 is in contact with the upper end of the valve main body 10, a flange-shaped disc 18 is fitted to the inner periphery of the lower end of the housing 45, and these are joined by welding. Thereby, the valve main body 10 and the housing 45 are integrated in a sealed state.
The flange-like disk 18 includes a plurality of through holes (shown by broken lines), and the refrigerant can move between the valve main body 10 side and the housing 45 side through the through holes.
The resin guide bar 15 disposed inside the rotor 30 is formed by a solid cylindrical main body 15a and a hollow cylindrical portion 15b continuously provided. The body 15a has an internally threaded hole 15c along the axis L. Further, a movable stopper 35 for closing the valve is provided above the guide rod 15.
A flange-like disc 18 welded to the upper end of the valve main body 10 is disposed on the outer periphery of the middle portion of the hollow cylindrical portion 15b, and the guide rod 15 is fixed to the valve main body 10 via the flange-like disc 18. The hollow cylindrical portion 15b is formed with a pressure equalizing hole 15d.
Further, in order to set the control origin positions of the rotor 30 and the valve shaft 21, a valve closing direction fixing stopper 55 having a rectangular cross section is provided to protrude upward from the upper surface of the main body 15a of the guide lever 15, and a valve opening direction fixing stopper 56 having a rectangular cross section is provided to protrude downward from the lower surface of the main body 15a of the guide lever 15. Here, the control origin position of the rotor 30 and the valve shaft 21 is a position at which the rotor 30 and the valve shaft 21 reach the lowermost position by the movable stopper 35 for the valve closing direction abutting against and being locked to the fixed stopper 55 for the valve closing direction.
The metal valve shaft 21 is formed by coaxially and continuously providing an end portion 21a to which an annular coupling body 32 attached to the rotor 30 is externally fitted, an external thread portion 21b screwed into the internal thread hole 15c, a flange-shaped portion 21c formed near the lower end, and a lower end coupling portion 21 d.
The movable stopper 35 for the valve closing direction fixed to the valve shaft 21 is disposed near the upper end of the male screw portion 21b, and is locked to the upper wall lower surface of the rotor 30. A stopper portion 35a having a rectangular cross section is formed on the lower surface of the movable stopper 35 in the valve closing direction.
Further, a movable stopper 36 for the valve opening direction is screwed into the vicinity of the lower end of the male screw portion 21b of the valve shaft 21 so as to abut on the upper surface of the flange-like portion 21 c. A stopper portion 36a having a rectangular cross section is formed on the upper surface of the movable stopper 36 for valve opening direction. Here, the movable stopper 36 for valve opening direction and the valve shaft 21 are fixed by forming a female thread on the inner periphery of the movable stopper 36 for valve opening direction and screwing the female thread to the male thread portion 21 b.
A valve holder 23 is slidably fitted and disposed inside the hollow cylindrical portion 15b below the valve shaft 21. The valve holder 23 has a top cylindrical shape in which a hollow cylindrical portion 23a and an upper wall 23b are continuously provided. A stepped opening 23c is formed in the center of the upper wall 23b, and the hollow cylindrical portion 23a has a communication hole 23d. The open lower end of the hollow cylindrical portion 23a of the valve holder 23 is disposed below the second pipe T2 in the valve-closed state, and is closed by an annular member 27 that is swaged and fixed.
In a state where the flange-shaped portion 21c of the valve shaft 21 abuts against the stepped portion of the stepped opening 23c, the lower end coupling portion 21d penetrates through the stepped opening 23c, and the lower end coupling portion 21d is caulked so as to expand the diameter, whereby the valve shaft 21 and the valve holder 23 are fixedly coupled. A valve chamber 29 is defined between the valve body 10 and the valve holder 23.
As shown in fig. 2 to 4, a needle valve (also referred to as a valve body) 25 is disposed so as to protrude from the lower end of the valve holder 23 through an annular member 27. The needle valve 25 is formed by continuously providing a cylindrical shaft portion (also referred to as a holding shaft portion) 25a, a valve cylindrical portion (also referred to as a flow straightening shaft portion) 25b having a constant outer diameter, and a first conical portion 25c and a second conical portion 25d which are reduced in diameter as they face downward. The taper angle (angle intersecting the axis L) of the first conical portion 25c is larger than that of the second conical portion 25 d. The first conical portion 25c is seated on the valve seat 11k.
Referring to fig. 3, when the inside diameter of the upper opening portion 11d of the valve seat member 11 is defined as Φ a, the inside diameter of the middle opening portion 11e is defined as Φ a, the outside diameter of the valve cylindrical portion 25B of the needle valve 25 is defined as Φ B, and the outside diameter of the second conical portion 25d is defined as Φ B, the following formula is preferably satisfied in a range from at least the valve closing point of the needle valve 25 to 40% of the full opening. Here, the "open point" refers to a position where the needle valve 25 is raised from a position where the lower limit abuts against the stopper, and a predetermined flow rate of refrigerant flows, and the "fully open" refers to an upper limit stopper position of the needle valve 25. The full open of 40% corresponds to, for example, "the maximum valve opening degree in the steady operation (the adjustment stage from the room temperature approaching the set temperature) during the cooling and heating operation of the air conditioner.
1＜{(φA 2 -φB 2 )·π/4}/{(φa 2 -φb 2 )·π/4}＜100 (1)
Wherein (φ A) 2 -φB 2 ) π/4 is the cross-sectional area S1 of the gap between the valve cylinder 25b and the upper opening 11d, (φ a) 2 -φb 2 ) π/4 is the orifice cross-sectional area S2.
The inner diameter of the upper opening 11d of the valve seat member 11 is preferably smaller than the outer diameter of the valve holder 23, and more preferably smaller than the inner diameter of the hollow cylindrical portion 23 a. The axial length of the upper opening 11d of the valve seat member 11 is shorter than the axial length of the valve cylindrical portion 25 b.
The annular member 31 is fitted to the outer periphery of the shaft portion 25a of the needle valve 25 by press fitting or the like. The outer diameter of the annular member 31 is larger than the inner diameter of the annular member 27, and therefore, the needle valve 25 is prevented from falling off the valve holder 23. A washer 28 is disposed between the annular member 31 and the annular member 27, thereby reducing friction when the annular member 31 and the annular member 27 rotate relative to each other.
In fig. 1, a cylindrical spring receiving member 26 is disposed between the upper wall 23b of the valve holder 23 and the needle valve 25, and the spring receiving member 26 has a lower end flange portion 26a. Further, a coil spring 24 is disposed between the upper wall 23b and the lower end flange portion 26a, and the coil spring 24 biases the spring receiving member 26 downward with respect to the valve holder 23.
The first conical portion 25c is seated on the valve seat 11k of the valve seat member 11, and when a reaction force directed upward is received, the spring receiving member 26 biased upward by the needle valve 25 abuts against the lower surface (or the lower end connecting portion 21 d) of the upper wall 23b of the valve holder 23, whereby the needle valve 25 is locked in the axial direction with respect to the valve shaft 2.
In a state where the needle valve 25 is separated from the valve seat 11k (a valve-opened state), the valve shaft 21, the valve holder 23, the needle valve 25, and the coil spring 24 are lifted and lowered while being substantially integrally rotated with respect to the guide rod 15.
(operation of flow control valve)
The operation of the motor-operated valve 1 will be specifically described.
Here, the refrigerant (fluid) enters the valve chamber 29 from the second pipe T2.
The rotor 30 and the valve shaft 21 are driven to rotate in one direction by pulse power supply from an external control device to a stator, not shown, and the valve shaft 21 and the movable stopper 35 for the valve closing direction are lowered while rotating by a screw feed mechanism including the female screw hole 15c and the male screw portion 21b, so that the needle valve 25 is seated on the valve seat 11k to close the orifice as shown in fig. 2. This cuts off the flow of the refrigerant from the valve chamber 29 toward the first pipe T1.
At this point, the movable stopper 35 has not yet come into contact with the fixed stopper 55, the lowering of the rotation of the rotor 30 and the valve shaft 21 has not stopped, and the pulse power supply is continued until the coil spring 24 is compressed by a predetermined amount. Thereby, the needle valve 25 is stopped from rotating in a state of being seated on the valve seat 11k, and the rotor 30, the valve shaft 21, the valve holder 23, and the like further rotate and descend.
At this time, the valve shaft 21 and the valve holder 23 are lowered with respect to the seated needle valve 25, and therefore the coil spring 24 is compressed and shortened, thereby absorbing the lowering force of the valve shaft 21 and the valve holder 23. Thereafter, when the compression amount of the coil spring 24 reaches a predetermined amount, the movable stopper 35 abuts and is locked to the fixed stopper 55, the rotor 30 and the valve shaft 21 reach the lowermost position, and the descent of the rotor 30 and the valve shaft 21 is forcibly stopped even if the power supply to the stator pulse is continued.
As described above, even after the needle valve 25 is seated on the valve seat 11k to close the orifice, the rotational lowering of the rotor 30, the valve shaft 21, and the valve holder 23 is continued until the control origin position where the movable stopper 35 abuts and is locked to the fixed stopper 55 is reached, and thereby the coil spring 24 is compressed. Therefore, the needle valve 25 is strongly pressed against the valve seat 11k by the biasing force of the coil spring 24, and leakage of the refrigerant and the like can be reliably prevented.
On the other hand, when pulse power of opposite polarity is supplied to the stator from the control origin position, the rotor 30 and the valve shaft 21 are driven to rotate in the opposite direction to the valve closing time, and the rotor 30, the valve shaft 21, the valve holder 23, and the movable stopper 36 for valve opening direction are raised while rotating by the screw feed mechanism including the female screw hole 15c and the male screw portion 21 b.
Accordingly, the pressing force against the needle 25 becomes weak, the coil spring 24 expands, and as shown in fig. 3, when the needle 25 is separated from the valve seat 11k, the orifice is opened. Thus, the refrigerant that has entered the valve chamber 29 from the second pipe T2 flows into the first pipe T1 through the gap between the first conical portion 25c and the valve seat 11k, and through the middle opening portion 11e and the lower opening portion 11 f.
Here, referring to fig. 2, in a state immediately after the needle valve 25 is separated from the valve seat 11k, the valve cylindrical portion 25b is held at a position overlapping the upper opening portion 11d of the valve seat member 11 in the axial direction. Therefore, the refrigerant in the valve chamber 29 passes through the gap between the valve cylindrical portion 25b and the upper opening portion 11d, and then flows to the orifice through the large space SP defined between the first conical portion 25c and the upper opening portion 11 d. The cross-sectional area of the space SP in the direction orthogonal to the axis is larger than the cross-sectional area of the gap between the valve cylindrical portion 25b and the upper opening portion 11d, and the space SP functions as a buffer space for improving the rectifying effect of the refrigerant entering the orifice. That is, when the end portion of the valve cylindrical portion 25b on the conical portion side, which is the rectifying shaft portion, is positioned in the upper opening portion 11d, which is the rectifying hole, the cross-sectional area of the gap between the valve cylindrical portion 25b and the upper opening portion 11d is larger than the cross-sectional area of the gap between the needle valve 25 and the valve seat 11k, as viewed in the axial direction of the motor-operated valve 1.
If the gap between the valve cylindrical portion 25b and the upper opening portion 11d is formed to be large, the refrigerant passes through the upper opening portion 11d without being sufficiently rectified and enters the orifice, and therefore, the sound when the refrigerant in the gas phase state or the refrigerant in the liquid phase state passes through the orifice is not uniform, and the noise may be recognized. This noise is particularly likely to be generated immediately after the needle valve 25 is separated from the valve seat 11k.
In contrast, according to the present embodiment, the refrigerant is rectified while passing through the narrow gap between the valve cylindrical portion 25b and the upper opening portion 11d, and approaches a two-phase state that is uniform over the entire circumference. Therefore, the sound when passing through the orifice can be reduced.
If the diameter of the upper opening 11d is larger than the valve holder 23, the refrigerant that has entered the valve chamber 29 from the second pipe T2 contacts the outer peripheral surface of the valve holder 23, then flows downward along the outer peripheral surface, and directly enters the gap between the valve cylindrical portion 25b and the upper opening 11d, so that the flow regulation effect may be weakened.
In contrast, according to the present embodiment, since the diameter of the upper opening portion 11d is smaller than the outer diameter of the lower end of the valve holder 23, the refrigerant that has entered the valve chamber 29 from the second pipe T2 first comes into contact with the upper end surface of the valve seat member 11 when heading downward along the outer circumferential surface of the valve holder 23, and the momentum is weakened, and after the refrigerant has made a certain degree of uniformity by surrounding along the entire circumference, the refrigerant enters the gap between the valve cylindrical portion 25b and the upper opening portion 11 d. Therefore, the rectification effect can be further improved.
Further, according to the present embodiment, in the cross-sectional view (fig. 3) of the valve-closed state, the extension line of the lower end outer peripheral surface (the tapered swaged surface) of the valve holder 23 is shielded by the upper end surface of the valve seat member 11 before entering the upper opening portion 11 d. Therefore, even when the refrigerant flows downward along the tapered surface, the refrigerant contacts the upper end surface of the valve seat member 11, and the momentum is weakened, thereby further improving the above-described flow regulation effect.
In addition, according to the present embodiment, since the relationship of the above equation (1) is established between the valve seat member 11 and the needle valve 25, the cross-sectional area S1 of the gap between the valve cylindrical portion 25b and the upper opening portion 11d is always larger than the orifice cross-sectional area S2, and thus the flow rate of the refrigerant can be accurately controlled regardless of the lift amount of the needle valve 25.
According to the present embodiment, the lift amount of the needle valve 25 is determined by pulse power supply to the stator, and therefore the flow rate of the refrigerant can be controlled. Further, by the continuous pulse power supply, as shown in fig. 4, the valve cylinder portion 25b is separated from the upper opening portion 11d, and finally the needle valve 25 is in a fully opened state. Further, in the case of the continuous pulse power supply, the movable stopper 36 abuts and is locked to the fixed stopper 56 for the valve opening direction, and thereby the rotation and the elevation of the rotor 30, the valve shaft 21, and the valve holder 23 are forcibly stopped.
[ second embodiment ]
Fig. 5 is a longitudinal sectional view of the electric valve 1A of the second embodiment. The motor-operated valve structure other than the seat member 11A is the same as that of the first embodiment, and therefore, redundant description is omitted.
Fig. 6 to 8 are vertical sectional views showing the periphery of the valve seat member 11A in an enlarged manner. The valve seat member 11A of the present embodiment is different from the first embodiment mainly in the shape of the upper opening portion 11 Ad. The same reference numerals are given to the same components as those of the first embodiment, and redundant description thereof is omitted.
The inner peripheral surface of the upper opening 11Ad of the valve seat member 11A has a tapered shape (tapered surface) whose diameter increases upward. In the present embodiment, the sectional area S1 of the gap between the valve cylindrical portion 25b and the upper opening portion 11Ad changes according to the lift amount of the needle valve 25, but the relationship of the above equation (1) is satisfied regardless of the lift amount. Further, the outer peripheral surface of the valve cylindrical portion 25b may be formed into a tapered shape (tapered surface) that decreases in diameter as it goes downward. By making both the inner peripheral surface of the upper opening 11Ad as the rectifying hole and the outer peripheral surface of the valve cylindrical portion 25b as the rectifying shaft portion tapered, the flow path of the gap between the valve cylindrical portion 25b and the upper opening 11d at the time of low flow rate can be extended, and the effect of reducing noise can be improved.

Claims (9)

1. An electrically operated valve, comprising:
a valve body that can be connected to a pipe and includes a valve chamber;
a valve seat member attached to the valve main body and including a valve seat;
a valve body disposed in the valve chamber and capable of being seated on the valve seat; and
a valve holder disposed in the valve chamber and holding the valve element,
the valve seat member has a cylindrical portion that protrudes into the valve chamber and has a rectifying hole formed inside the cylindrical portion so as to communicate with the valve seat,
the valve core is provided with: a holding shaft portion held by the valve holder, a conical portion capable of seating on the valve seat, and a flow regulating shaft portion disposed between the holding shaft portion and the conical portion,
the inner diameter of the rectifying hole is smaller than the outer diameter of the end part of the valve retainer close to one side of the rectifying hole,
at least when the valve is closed, the rectifying shaft part is positioned in the rectifying hole,
when the end portion of the rectifying shaft portion on the conical portion side is positioned in the rectifying hole, the sectional area of the gap between the rectifying shaft portion and the rectifying hole is larger than the sectional area of the gap between the valve element and the valve seat when viewed in the axial direction of the motor-operated valve.
2. Electrically operated valve according to claim 1,
the cross-sectional area of the gap between the rectifying shaft portion and the rectifying hole is 1 time and 100 times larger than the cross-sectional area of the gap between the valve element and the valve seat in the range from the valve closing point of the valve element to 40% of the full opening.
3. Electrically operated valve according to claim 1 or 2,
the wall thickness of the cylindrical portion of the valve seat member is thicker than the wall thickness of the valve main body.
4. Electrically operated valve according to any of claims 1 to 3,
the valve retainer is cylindrical, and the inner diameter of the rectifying hole is smaller than the inner diameter of the lower end of the valve retainer.
5. Electrically operated valve according to any of claims 1 to 4,
the fairing shaft portion has a constant outer diameter.
6. Electrically operated valve according to one of the claims 1 to 5,
the flow straightening hole has a constant inner diameter.
7. Electrically operated valve according to any of claims 1 to 5,
the flow straightening hole has a conical shape.
8. Electrically operated valve according to one of the claims 1 to 4,
the rectifying hole and the rectifying shaft portion each have a tapered shape.
9. Electrically operated valve according to one of the claims 1 to 8,
the rectifying shaft portion is disengaged from the rectifying hole in accordance with a valve opening amount of the valve body.
CN202210348039.7A 2021-06-07 2022-03-23 Electric valve Pending CN115507187A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021-095203 2021-06-07
JP2021095203A JP2022187265A (en) 2021-06-07 2021-06-07 electric valve

Publications (1)

Publication Number Publication Date
CN115507187A true CN115507187A (en) 2022-12-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210348039.7A Pending CN115507187A (en) 2021-06-07 2022-03-23 Electric valve

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JP (1) JP2022187265A (en)
CN (1) CN115507187A (en)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4043076B2 (en) * 1997-07-25 2008-02-06 株式会社不二工機 Flow control valve
JP4285155B2 (en) * 2003-08-27 2009-06-24 ダイキン工業株式会社 Multistage electric expansion valve and refrigeration system
JP4285156B2 (en) * 2003-08-27 2009-06-24 ダイキン工業株式会社 Multistage electric expansion valve and refrigeration system
JP2005351605A (en) * 2004-06-14 2005-12-22 Daikin Ind Ltd Expansion valve and refrigeration device
JP2008232290A (en) * 2007-03-20 2008-10-02 Saginomiya Seisakusho Inc Needle valve, and refrigerating cycle device having the same
JP6643292B2 (en) * 2017-09-28 2020-02-12 株式会社不二工機 Electric valve
JP7029169B2 (en) * 2018-07-25 2022-03-03 株式会社不二工機 Solenoid valve

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