CN110425331A - Motor-driven valve - Google Patents
Motor-driven valve Download PDFInfo
- Publication number
- CN110425331A CN110425331A CN201910727378.4A CN201910727378A CN110425331A CN 110425331 A CN110425331 A CN 110425331A CN 201910727378 A CN201910727378 A CN 201910727378A CN 110425331 A CN110425331 A CN 110425331A
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- China
- Prior art keywords
- port
- valve
- motor
- tapered portion
- internal diameter
- 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.)
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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
- 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
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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
- 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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The present invention provides a kind of motor-driven valve.It is being opened and closed in motor-driven valve of the valve port to control the flow of refrigerant by needle-valve, is reducing noise caused by the flowing of the refrigerant at valve port.In valve casing (1) Formation cross-section round and the first port (11) of internal diameter D1, the second port (12) of internal diameter D2, the third port (13) of internal diameter D3, the first tapered portion (14) and the second tapered portion (15).When the refrigerant of flowing flows out second port (12) from the gap of first port (11) and needle-valve (5a), restore pressure sharp in second port (12), flowing is rectified stablize flowing.Thus inhibit the rupture of vacuole.When flowing from second port (12) to the second tapered portion (15) and third port (15), flow velocity is carried out slowing down to reduce flow velocity sound.
Description
The application is divisional application；Its female case application No. is " 2016109732269 ", it is entitled " motor-driven valve ".
Technical field
The present invention relates to the motor-driven valves of the needle valve type for the flow that refrigerant is controlled in air conditioner etc., more particularly to improve
Motor-driven valve of the valve port relative to the shape of needle-valve.
Background technique
In the past, in refrigerating cycle, fluid generate from the motor-driven valve of the flow of control refrigerant, adjoint is by generating
Noise can usually become problem sometimes.As the motor-driven valve of the such noise counter plan of implementation, such as there is Japan Patent 5696093
Motor-driven valve disclosed in number bulletin (patent document 1).
In the motor-driven valve of patent document 1, valve port is made of first port and second port, and in first port and second end
Tapered portion is equipped between mouthful.In addition, keeping the internal diameter of second port more slightly larger than the internal diameter of first port, and make the length of second port
It spends sufficiently longer than the length of first port.
Moreover, in the scheme of patent document 1, as shown in figure 5, the refrigerant behind the gap for passing through needle-valve a and first port b
It is flowed by tapered portion c and second port d to secondary joint pipe side.At this point, behind the gap for passing through needle-valve a and first port b
Refrigerant flowing to imitate the shape of tapered portion c and along the inner wall of second port d in the form of flow.Second port d's
Internal diameter is only more slightly larger than the internal diameter of first port b, to will not make pressure during flowing to second port d from first port b
Sharp restore.Also, since the length of second port d is sufficiently long, so the flowing of refrigerant is whole at second port d
Stream.Therefore, it is able to suppress the rupture of vacuole, and the flowing of refrigerant can be made to stabilize, so as to reduce noise.
Existing technical literature
Patent document 1: No. 5696093 bulletins of Japan Patent
In the invention of patent document 1, it is also reduced the effect of noise, but there is generation to make an uproar under specific refrigerant condition
A possibility that sound.For example, can be rectified at second port to the flowing of fluid in the scheme of patent document 1, but this
The internal diameter of Two-port netwerk is more slightly larger than the internal diameter of first port, and its length is sufficiently longer than first port.Therefore, fluid is rectified,
But the case where thering is the flow velocity in the second port not slow down, generating noise because of flow velocity sound (due to the higher sound of flow velocity).
Especially, the differential pressure in high load capacity before and after valve port is higher, so that the flow velocity sound becomes the larger key factor of noise.
Summary of the invention
The issue of the present invention is to provide reduce the motor-driven valve of noise by improving valve port.
The motor-driven valve of scheme 1 is the valve chamber for being connected to a junction block and secondary connector via the valve port being opened and closed with needle-valve
And the motor-driven valve that can be connected to, it is bigger than the internal diameter of first port to have the first port of valve chamber side, internal diameter in above-mentioned valve port
Second port and the first tapered portion for linking up above-mentioned first port and above-mentioned second port, the feature of said electric valve
It is have positioned at the third port of above-mentioned secondary joint pipe side and by above-mentioned second port and above-mentioned the in above-mentioned valve port
The second tapered portion that three ports are linked up, the internal diameter D1 of above-mentioned first port, the internal diameter D2 of above-mentioned second port and above-mentioned
The relationship of the internal diameter D3 of three ports is D1 < D2 < D3.
The motor-driven valve of scheme 2 motor-driven valve according to scheme 1, which is characterized in that
D2-D1≤D3-D2.
The motor-driven valve of scheme 3 motor-driven valve according to scheme 1 or 2, which is characterized in that
The cone angle of above-mentioned first tapered portion is set as θ 1, the cone angle of above-mentioned second tapered portion is set as to θ 2, by above-mentioned
The length of Single port is set as L1, the length of above-mentioned first tapered portion and second port is set as to L2 and by above-mentioned second tapered portion
When being set as L3 with the length of above-mentioned third port, become following relationship:
1mm≤D1≤4.5mm,
1≤150 ° of 60 °≤θ,
2≤90 ° of 20 °≤θ,
0.1mm≤L1≤0.5mm,
1≤L2/L1≤39,
0.57≤L3/L2≤38,
1.03≤D2/D1≤1.5,
1.02≤D3/D2≤5.52。
The effect of invention is as follows.
According to the motor-driven valve of scheme 1 to 3, when the refrigerant of flowing flows out to second end from the gap of first port and needle-valve
When mouth, restore pressure sharp in second port, can stablize to the flowing that rectified to make refrigerant is flowed, from
And it is able to suppress the rupture of vacuole.In addition, when being flowed from second port to the second tapered portion and third port, flow velocity slow down from
And flow velocity sound can be reduced.Therefore, noise can be reduced.
According to the motor-driven valve of scheme 2, due to becoming D2-D1≤D3-D2, so relative to second port, from the second cone
Shape portion is significantly expanding to third port, so that the slowing effect of flow velocity is got higher, can be further reduced flow velocity sound.
According to the motor-driven valve of scheme 3, by meeting the size of each section and the condition of angle, thus even if before valve port
In the higher situation of pressure difference afterwards, noise can be also reduced in a effective manner.
Detailed description of the invention
Fig. 1 is the longitudinal section view of the motor-driven valve of embodiments of the present invention.
Fig. 2 is the major part amplification longitudinal section view near the valve port of the motor-driven valve of embodiments of the present invention.
Fig. 3 is the figure for illustrating the effect of the valve port of motor-driven valve of embodiments of the present invention.
Fig. 4 is the figure for indicating to have used an example of air conditioner for the motor-driven valve of embodiments of the present invention.
Fig. 5 is the figure for illustrating the effect of valve port of previous motor-driven valve.
In figure:
1-valve casing, 1A-valve chamber, 11-first ports, 12-second ports, 13-third ports, the 14-the first taper
Portion, the 15-the second tapered portion, 21-junction block, 22-secondary joint pipes, 3-support members, 4-valve supports, 5-valves
Core, 5a-needle-valve, 6-stepper motors, X-axis.
Specific embodiment
Next, being illustrated referring to embodiment of the attached drawing to motor-driven valve of the invention.Fig. 1 is the electronic of embodiment
The longitudinal section view of valve, Fig. 2 are the major part amplification longitudinal section views near the valve port of the motor-driven valve of embodiment, and Fig. 3 is explanation
The figure of the effect of the valve port of the motor-driven valve of embodiment, Fig. 4 be indicate to have used the motor-driven valve of embodiment air conditioner one
The figure of a example.
Firstly, being illustrated based on air conditioner of the Fig. 4 to embodiment.Air conditioner have embodiment motor-driven valve 10,
Be equipped on the outdoor heat exchanger 20 of outdoor unit 100, the indoor heat exchanger 30 for being equipped on indoor unit 200, flow channel switching valve 40,
And compressor 50, these each elements pass through conduit respectively and connect as illustrated, to constitute the refrigerating cycle of heat-pump-type.
The refrigerating cycle is using an example of the refrigerating cycle of motor-driven valve of the invention, and motor-driven valve of the invention can also apply to
The others system such as throttling set of indoor pusher side of the multi-connected air conditioner of high building etc..
The flow path of refrigerating cycle is switched to heating mode and refrigeration mode both flow paths by flow channel switching valve 40, is making
In heat pattern as shown in the arrow of solid line, indoor heat exchanger is flowed into from flow channel switching valve 40 by the compressed refrigerant of compressor 50
30, and motor-driven valve 10 is flowed by pipeline 60 from the refrigerant that indoor heat exchanger 30 flows out.Moreover, refrigerant is in the motor-driven valve
It expands at 10, and is successively recycled to outdoor heat exchanger 20, flow channel switching valve 40, compressor 50.In refrigeration mode, such as dotted line
Shown in arrow, outdoor heat exchanger 20 is flowed into from flow channel switching valve 40 by the compressed refrigerant of compressor 50, and from outdoor heat exchange
The refrigerant that device 20 flows out expands at motor-driven valve 10, and flowing is in pipeline 60 to flow into indoor heat exchanger 30.Flow into the room
The refrigerant of interior heat exchanger 30 flows into compressor 50 via flow channel switching valve 40.In addition, being made in the example shown in Fig. 4
When heat pattern, become the structure for flowing refrigerant to secondary joint pipe 22 from a junction block 21 of motor-driven valve 10, but can also
So that the connection of piping is on the contrary, in heating mode, as flowing refrigerant from 22 Xiang Yici junction block 21 of secondary joint pipe
Structure.
Motor-driven valve 10 works as the throttling set that the flow to refrigerant is controlled, outdoor in heating mode
Heat exchanger 20 is functioned as evaporator, and indoor heat exchanger 30 is functioned as condenser, thereby executing indoor heating.
Also, in refrigeration mode, outdoor heat exchanger 20 is functioned as condenser, and indoor heat exchanger 30 plays function as evaporator
Can, thereby executing indoor cooling supply.
Next, being illustrated based on motor-driven valve 10 of the Fig. 1 and Fig. 2 to embodiment.The motor-driven valve 10 has valve casing
1, the valve chamber 1A of circle cylinder tubular is formed in valve casing 1.Also, valve casing 1 be formed with first port 11, second port 12 and
Third port 13.Also, the first tapered portion 14 is formed between first port 11 and second port 12, second port 12 with
The second tapered portion 15 is formed between third port 13.The primary of valve chamber 1A is connected in addition, being equipped in valve casing 1 from side
Junction block 2, and secondary joint pipe 22 is installed in the unilateral end in the axis X direction of valve chamber 1A.Moreover, via first port
11, the first tapered portion 14, second port 12, the second tapered portion 15 and third port 13, valve chamber 1A and 22 energy of secondary joint pipe
Enough conductings.
Support member 3 is installed on the top of valve casing 1.The longer guiding on axis X direction is formed in support member 3
Hole 3a, cylindric valve support 4 can slidably be embedded in pilot hole 3a along axis X direction.Valve support 4 and valve chamber 1A are coaxial
Installation is fixed with the spool 5 for having needle-valve 5a in end in the lower end of the valve support 4.Also, in valve support 4, Neng Gouyan
Axis X direction is movably equipped with spring base 41, between spring base 41 and spool 5, to give the defined state peace loaded
Equipped with compression helical spring 42.
In the upper end of valve casing 1, the shell 61 of stepper motor 6 is airtightly fixed with by welding etc..It, can in shell 61
It is rotatably equipped with peripheral part and is geomagnetic into the magnet rotor 62 of multipole, and be fixed with armature spindle 63 in the magnet rotor 62.Rotor
The upper end of axis 63 can be rotatably entrenched in out of, the top wall portion of shell 61 hangs down cylindric guide part 64.Also, In
The periphery of shell 61 is equipped with stator coil 65, by giving pulse signal to the stator coil 65, come make magnet rotor 62 with
The umber of pulse accordingly rotates.Moreover, being rotated because of the rotation of the magnet rotor 62 with the armature spindle 63 of 62 one of magnet rotor.
In addition, being equipped with the rotation preventive mechanism 66 relative to magnet rotor 62 in the periphery of guide part 64.
The upper end of valve support 4 is sticked in the lower end of the armature spindle 63 of stepper motor 6, and valve support 4 passes through armature spindle 63
And it is supported with the state that can rotatably dangle.Also, it is formed with external thread part 63a in armature spindle 63, external thread part 63a
It is screwed with the internal thread part 3b for being formed in support member 3.
According to above structure, with the rotation of magnet rotor 62, armature spindle 63 is moved along axis X direction.It is somebody's turn to do because adjoint
The axis X direction of the armature spindle 63 of rotation is mobile and spool 5 is moved along axis X direction together with valve support 4.Moreover, spool 5 exists
The opening area for increasing and decreasing first port 11 at the part of needle-valve 5a, to what is flowed from a junction block 21 to secondary joint pipe 22
The flow of fluid is controlled.
First port 11, second port 12 and third port 13 are formed as the side of the cylinder centered on axis X
Shape, as shown in Fig. 2, the internal diameter D1 of first port 11 is the size with the cooperation of the periphery of needle-valve 5a.Also, second port 12
Internal diameter D2 is the internal diameter D1 slightly larger dimensions than first port 11.The internal diameter D3 of third port 13 is than the internal diameter of second port 12
D21 big size, and be the size smaller than the internal diameter D4 of secondary joint pipe 22.In addition, marking table to each diameter D1~D4 in Fig. 2
Show " φ " of diameter.The length L1 of first port 11 is the size smaller than internal diameter D1, and the first tapered portion 14 and second port 12 add
The length L2 to get up is the size bigger than the length L1 of first port 11.The length that second tapered portion 15 and third port 13 add up
Spending L3 is the size bigger than the length L2 that the first tapered portion 14 and second port 12 add up.
First tapered portion 14 and the second tapered portion 15 are formed as the shape of the side of the frustum of a cone centered on axis X,
The medial surface of first tapered portion 14 is internal diameter from first port 11 to the widened shape of second port 12, the second tapered portion 15 it is interior
Side is internal diameter from second port 12 to the widened shape of third port 13.Moreover, suitably setting is used as the first tapered portion 14
Subtended angle taper angle theta 1, as the second tapered portion 15 subtended angle taper angle theta 2.In addition, these sizes and angle are not limited to
The condition of these sizes and angle will be described hereinafter in example illustrated in Fig. 2.
As shown in figure 3, passing through the first tapered portion 14, second by the refrigerant behind the gap of needle-valve 5a and first port 11
Port 12, the second tapered portion 15 and third port 13 and to secondary joint pipe 22 flow.At this point, needle-valve 5a and first port 11
Gap be most narrow position, flow velocity becomes maximum herein, but the length L1 of first port 11 is short as far as possible, behind the gap
The flowing of refrigerant to imitate the shape of the first tapered portion 14 and immediately along the inner wall of second port 12 in the form of flow.Second
The internal diameter D2 of port 12 is only more slightly larger than the internal diameter D1 of first port 11, thus flowing to second port 12 from first port 11
Period will not be such that pressure sharp restores.Also, since the length of second port 12 is longer, so the flowing of refrigerant is
It is rectified at Two-port netwerk 12.Therefore, it is able to suppress the rupture of vacuole, and the flowing of refrigerant can be made to stablize.
The shape of the second tapered portion 15 is imitated to restore to improve on one side by the flowing of the refrigerant after second port 12
Pressure is flowed to third port 13 on one side.Since the internal diameter D3 of the third port 13 is bigger than the internal diameter D2 of second port 12, so
Slow down during copying the shape of the second tapered portion 15 to flow to flow velocity.That is, due to one side at second port 12 with
Certain degree is rectified, and is slowed down immediately to flow velocity on one side, so flow velocity sound is reduced.In addition, passing through the second tapered portion 15
The flowing of the refrigerant to have slowed down to third port 13 flow, but due to the flowing of refrigerant at second port 12 it is whole
Stream, so the Flowing Hard of refrigerant is to become sinuous flow, in the third port 13 so as to inhibit the rupture of vacuole.
In this way, by being rectified at second port 12 with certain degree, and via the second tapered portion 15 to third port
13 flowings, so as to keep the state of rectification to slow down flow velocity at the second tapered portion 15.Thereby, it is possible to reduce
Sinuous flow at three ports 13 inhibits the rupture of vacuole, and can slow down to flow velocity at the second tapered portion 15 to reduce
Flow velocity sound.That is, the length of second port 12 is shorter than the length of the second port in patent document 1, flow velocity correspondingly can be realized
The reduction of sound.
Motor-driven valve 10 in embodiment is in the higher situation of pressure difference of a junction block 21 and secondary joint pipe 22
The reduction effect of flow velocity sound is higher, first port 11, second port 12, third port 13, the first tapered portion 14, the second tapered portion
15 and secondary connector 22 each section size and angle be set to meet condition below.
Hereinafter, indicating the reduction of the flow velocity sound in the higher situation of pressure difference of a junction block 21 and secondary joint pipe 22
The size of each section of the higher embodiment of effect and the condition of angle.The internal diameter D1 of first port 11 be 1mm≤D1≤
4.5mm
The internal diameter D2 of second port 12 is 1.15mm≤D2≤4.9mm,
The internal diameter D3 of third port 13 is 4.6mm≤D3≤6.35mm,
The internal diameter D4 of secondary connector 22 is 6.35mm≤D4.
Also, the range that the taper angle theta 1 of the first tapered portion 14 is 1≤150 ° of 60 °≤θ,
The range that the taper angle theta 2 of second tapered portion 15 is 2≤90 ° of 20 °≤θ.
Also, the length L1 of first port 11 is 0.1mm≤L1≤0.5mm, and the L1 the short, and then noise is lower.
The length L2 of first tapered portion 14 and second port 12 is 0.5mm≤L2≤3.9mm,
The combination of above-mentioned length L1, L2, L1+L2 are set according to this condition of 1mm≤L1+L2≤4mm.
Also, the length L2 and the second taper of the length L1 of first port 11, the first tapered portion 14 and second port 12
The summation L1+L2+L3 of the length L3 of portion 15 and third port 13 is 6mm≤L1+L2+L3≤23mm.
Also, the length L2 of the first tapered portion 14 and second port 12, it is with the ratio L2/L1 of the length L1 of first port 11
The range of 1≤L2/L1≤39,
The length L3's of the second tapered portion 15 and third port 13 and length L2 of the first tapered portion 14 and second port 12
It is the range of 0.57≤L3/L2≤38 than L3/L2,
The size ratio D2/D1 of the internal diameter D1 of the internal diameter D2 and first port 11 of second port 12 is 1.03≤D2/D1≤1.5
Range,
The size ratio D3/D2 of the internal diameter D2 of the internal diameter D3 and second port 12 of third port 13 be 1.02≤D3/D2≤
5.52 range.
Next, to each size of the motor-driven valve of embodiment than and the actual measurement example of noise decrease be illustrated.The actual measurement
It is 2.8~3.4 (MPa), the pressure in secondary joint pipe 22 in the pressure in a junction block 21 is 1.2~1.8 in example
(MPa) under operating condition, to the noise determined in the motor-driven valve of embodiment and in motor-driven valve (its of patent document 1
Condition) in the noise that determines compared.That is, being noise under conditions of indicating to be easy to produce flow velocity sound when high load capacity
The effect of reduction especially significantly surveys example.The actual measurement example is indicated into table 6 in table 1 below.In table 1 into table 6, with " zero
00 " it indicates the case where reducing 2dB or more acoustic pressure compared with the noise in the motor-driven valve of patent document 1, is indicated with " 00 "
The case where 1~2dB acoustic pressure is reduced compared with the noise in the motor-driven valve of patent document 1.Also, the drop of acoustic pressure is indicated with "○"
The low situation for 1dB or less.In addition, evaluating acoustic pressure using A characteristic.
The relationship of the expression of table 1 L2/L1 and θ 1.
[table 1]
(L2/L1) with the relationship of θ 1
The relationship of the expression of table 2 L2/L1 and D2/D1.[table 2]
(L2/L1) with the relationship of (D2/D1)
The relationship of the expression of table 3 L2/L1 and θ 2.
[table 3]
(L2/L1) with the relationship of θ 2
The relationship of the expression of table 4 L2/L1 and D3/D2.
[table 4]
(L2/L1) with the relationship of (D3/D2)
The relationship of the expression of table 5 D3/D2 and θ 2.
[table 5]
(D3/D2) with the relationship of θ 2
The relationship of the expression of table 6 D3/D2 and L3/L2.
The relationship of [table 6] (D3/D2) and (L3/L2)
It is compared with the past more to realize noise from above-mentioned table it is found that by setting third port and the second tapered portion
Reduction.Also, even if in the higher situation of pressure difference of junction block 21 and secondary joint pipe 22, as long as in " 00 "
And in the range of " 000 ", it will be able to 1dB or more noise is reduced, so as to obtain more significant effect.
More than, embodiments of the present invention are illustrated in detail referring to attached drawing, but specific structure does not limit
In these embodiments, does not depart from the design alteration etc. in the range of purport of the invention and be also included in the present invention.
Claims (1)
1. a kind of motor-driven valve, be the valve chamber for being connected to a junction block and secondary joint pipe via the valve port being opened and closed with needle-valve and
The motor-driven valve that can be connected to has second bigger than the internal diameter of first port of the first port of valve chamber side, internal diameter in above-mentioned valve port
Port and the first tapered portion for linking up above-mentioned first port and above-mentioned second port, said electric valve be characterized in that,
Have in above-mentioned valve port positioned at the third port of above-mentioned secondary joint pipe side and by above-mentioned second port and above-mentioned third
The second tapered portion that port is linked up, the internal diameter D1 of above-mentioned first port, the internal diameter D2 of above-mentioned second port and above-mentioned third
The relationship of the internal diameter D3 of port is D1 < D2 < D3 and 1.02≤D3/D2≤5.52.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-252068 | 2015-12-24 | ||
| JP2015252068A JP6479648B2 (en) | 2015-12-24 | 2015-12-24 | Motorized valve |
| CN201610973226.9A CN106917913B (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610973226.9A Division CN106917913B (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110425331A true CN110425331A (en) | 2019-11-08 |
| CN110425331B CN110425331B (en) | 2022-06-10 |
Family
ID=59232184
Family Applications (6)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610973226.9A Active CN106917913B (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910726725.1A Pending CN110388506A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910727380.1A Pending CN110388508A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910727378.4A Active CN110425331B (en) | 2015-12-24 | 2016-10-28 | Electric valve |
| CN201910727376.5A Pending CN110388507A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910726673.8A Active CN110388505B (en) | 2015-12-24 | 2016-10-28 | Electric valve |
Family Applications Before (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610973226.9A Active CN106917913B (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910726725.1A Pending CN110388506A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910727380.1A Pending CN110388508A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
Family Applications After (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910727376.5A Pending CN110388507A (en) | 2015-12-24 | 2016-10-28 | Motor-driven valve |
| CN201910726673.8A Active CN110388505B (en) | 2015-12-24 | 2016-10-28 | Electric valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6479648B2 (en) |
| CN (6) | CN106917913B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6726124B2 (en) * | 2017-03-23 | 2020-07-22 | 株式会社鷺宮製作所 | Motorized valve and refrigeration cycle system using the same |
| JP6740179B2 (en) * | 2017-06-23 | 2020-08-12 | 株式会社鷺宮製作所 | Motorized valve and refrigeration cycle system |
| JP6738775B2 (en) * | 2017-07-24 | 2020-08-12 | 株式会社鷺宮製作所 | Motorized valve and refrigeration cycle system |
| CN109780317B (en) * | 2019-01-07 | 2020-04-21 | 珠海市广源信科技有限公司 | Pressure compensation device of speed regulating valve |
| JP2019070449A (en) * | 2019-02-05 | 2019-05-09 | 株式会社鷺宮製作所 | Motor valve and refrigeration cycle system |
| JP7199335B2 (en) * | 2019-10-25 | 2023-01-05 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN110388508A (en) | 2019-10-29 |
| JP6479648B2 (en) | 2019-03-06 |
| CN110425331B (en) | 2022-06-10 |
| CN110388505B (en) | 2023-02-28 |
| CN110388505A (en) | 2019-10-29 |
| CN106917913B (en) | 2019-09-06 |
| CN110388507A (en) | 2019-10-29 |
| CN106917913A (en) | 2017-07-04 |
| JP2017115989A (en) | 2017-06-29 |
| CN110388506A (en) | 2019-10-29 |
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