CN203670331U - Pilot-operated type inverse proportion decompression solenoid valve - Google Patents
Pilot-operated type inverse proportion decompression solenoid valve Download PDFInfo
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- CN203670331U CN203670331U CN201420010312.6U CN201420010312U CN203670331U CN 203670331 U CN203670331 U CN 203670331U CN 201420010312 U CN201420010312 U CN 201420010312U CN 203670331 U CN203670331 U CN 203670331U
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Abstract
The utility model relates to a pilot-operated type inverse proportion decompression solenoid valve which is composed of a main valve, a pilot valve and a proportion electromagnet. The main valve is composed of a valve body, a valve element located in the valve body, a valve seat riveted to one end of the valve body, a reset spring located at the end, close to the valve seat, in the valve element, and a filter screen, wherein the valve body is sleeved with the filter screen. The pilot valve is composed of a valve body and an ejector rod in contact with the plane at one end of the valve body. The proportion electromagnet is composed of a sliding bearing, a bearing seat, a pole shoe, an armature, an ejector rod, a connecting pipe, a stroke gasket, stop iron, a magnetic circuit board, an adjusting screw, a coil, an adjusting spring, a coil cover and yoke iron. The pilot-operated type inverse proportion decompression solenoid valve solves the problems that an existing pilot-operated type inverse proportion decompression solenoid valve is narrow in control frequency range, high in oil consumption and failure rate and complex in manufacturing process, and has the advantages of being wide in control frequency range, low in oil consumption and failure rate and easy to manufacture.
Description
Technical field
The utility model patent relates to a kind of inverse proportion vacuum solenoid valve, in particular for the leading type inverse proportion vacuum solenoid valve of the accurate pressure control of vehicular automatic transmission hydraulic system.
Background technique
Inverse-proportion pressure reducing valve is the core parts of automatic speed variator hydraulic system, is widely used in the accurate pressure control of automatic transmission oil pressure.Compared with general direct action type proportional vacuum solenoid valve, it is large that leading type inverse proportion vacuum solenoid valve has negotiability, and working pressure high is widely used in high pulling torque vehicle.Representative leading type inverse proportion vacuum solenoid valve is that the General Corporation that is applied to the vehicles such as brave horse produces 4L60E type automatic transmission.
The 4L60E of General Corporation type automatic transmission by the forming of switching mode electromagnet, pilot valve and main valve, wherein forms pilot valve by armature and valve body with leading type inverse proportion vacuum solenoid valve, and electromagnetism ouput force is exported by armature.Its working procedure is: input to the electrical signal of solenoid valve, change into the electromagnetic attraction output acting on the moving iron core armature of electromagnet through switching mode electromagnet, in armature inside, spring is set, produce by the decrement of control spring the spring force needing.Electromagnetic attraction be positioned at armature inside spring produce effective electromagnetic force of spring force and the hydraulic feedback power isoequilibrium of guide's valve pocket, the hydraulic feedback power of guide's feedback cavity and the hydraulic feedback equilibrium of forces of main valve chamber, obtain the corresponding relation of input signal and main valve chamber control mouth pressure thus.In the leading type inverse proportion vacuum solenoid valve of the type, the size of electromagnetic force is not only relevant with the size of input electrical signal, has direct relation, the existing larger difference of electromagnetic force in the time of the alternate position spike of 0.01mm magnitude with the relative position of armature and static iron core simultaneously.The size (accurate relative distance between corresponding armature and valve body) that the pressure of first guide cavity relies on the guide's flow-off forming between armature and valve body determines.Due to the pressure of main valve control mouth and the one-to-one relationship of making a concerted effort into of pressure that should first guide cavity and electromagnet output, in order to realize the linearity of main valve control mouth pressure, need between effective electromagnetic force of electromagnet output and input signal linearly proportional.And its output electromagnetic force of switch electromagnet is relevant with the position of moving iron core armature, this has very high required precision with regard to causing to the position of armature.Meanwhile, export the linearity of effective electromagnetic force in order to realize electromagnet, also need the spring force to being positioned at armature inside accurately to control.In order to reduce the fluctuation of the electromagnetic valve pressure that input signal etc. causes, on armature, be provided with vibration damping diaphragm.
Existing structure mainly contains following some deficiency:
1) the numerous and numerous parts of number of spare parts need very high machining accuracy, processing difficulties, and assembly process needs numerous governing loops, and single product is carried out to armature position adjusting, and initial tension of spring regulates, and assembly process is consuming time, manufactures difficulty and manufacture cost higher.
2) the larger quality of armature, its movement inertia is larger, when work speed of response there is partially slowly and easily overshooting problem, the excess flow in electromagnetic valve guide chamber is bigger than normal, causes the load of the engine-driving oil pump measurement oil consumption that makes to apply this solenoid valve bigger than normal higher.
3) due to processing and too complexity of dress assembly process, homogeneity of product is poor, characteristic relation scattered error between different product between input signal and control mouth pressure is larger, due to the limitation of tcu signal compatibility, causes applying this solenoid valve product vehicle trouble rate higher.
4) because switch electromagnet cannot execution at high-frequency controling signal, in the time of low frequency signal, operating frequency is too low, makes the use control frequency scope of this solenoid valve narrower.
Therefore the leading type inverse proportion vacuum solenoid valve that, designs a kind of reduction oil consumption for high pulling torque automatic transmission, reduces manufacture difficulty, reduces rate of fault and control frequency wide ranges is the technical problem that related domain is needed solution badly.
Model utility content
The utility model patent object is to provide that a kind of oil consumption for high pulling torque automatic transmission is low, manufacture difficulty is little, the leading type inverse proportion vacuum solenoid valve of failure rate is low and control frequency wide ranges.
For realizing technical purpose of the present utility model, the technical solution adopted in the utility model is: a kind of leading type inverse proportion vacuum solenoid valve, formed by main valve, pilot valve and proportion electro-magnet, it is characterized in that: described main valve comprises valve body, and be positioned at the spool of valve inner, and be riveted on the valve seat on valve body, and be positioned at the Returnning spring of valve core inside near valve seat one side, and be socketed in intake screen and outlet filter screen outside valve body; In described pilot valve, be provided with the push rod with valve body one end plane contact; Described proportion electro-magnet comprises diaphragm, the first sliding bearing, the second sliding bearing, bearing support, pole shoe, armature, push rod, connecting tube, pad, buting iron, magnetic circuit plate, adjusting screw, coil, Regulation spring, coil housing and yoke; Described yoke is the tubular structure of hollow, and one end is fixed on valve body, and the other end is sealed by magnetic circuit plate; Described pole shoe, armature, buting iron, magnetic circuit plate, coil are positioned at yoke inside; Between described pole shoe and buting iron and connecting tube, riveted joint is integrated; Described armature and push rod riveted joint are integrated; Described the first sliding bearing is embedded in buting iron inside and is socketed on push rod; Described the second sliding bearing is embedded in bearing support inside and is integrated and is socketed on push rod by bearing support and pole shoe riveted joint; Described push rod is arranged between sliding bearing and sliding bearing
As preferably, described valve body, push rod and spool form guide's valve pocket.
As preferably, described diaphragm, between valve body and pole shoe, and is socketed on push rod.
As preferably, described spool is provided with the concentric circle pass guide tracting pressuring hole that multistage is adjacent, and be communicated with the first guide cavity oil inlet hole of the two sections of concentric cylindrical radially arranging, and be communicated with guide's valve pocket, valve core diameter's direction is provided with circular hole control mouth tracting pressuring hole, and be provided with eccentric circle pass control mouth tracting pressuring hole with axial direction and be communicated with, and be communicated with main valve pilot pressure feedback cavity; On described valve body, be provided with import, control mouth, main valve drain tap and first guide cavity drain tap.
Useful technique effect of the present utility model is:
1, the utility model patent adopts attractive proportion electro-magnet, and part difficulty of processing is moderate, and assembly process does not need to regulate, and assembly process is simple.
2, in the utility model, the moving element movement inertia such as armature is less, fast response time, good stability, and the leakage of first guide cavity is less, and product energy consumption is low.
3, in the utility model, adopted proportional electromagnetic valve structure as driving element, product scattered error is little, high conformity, failure rate is low.
4, the utility model patent has adopted proportional electromagnetic valve structure as driving element, and applied control signal wide frequency range can arrive 300Hz to 1500Hz scope.
Accompanying drawing explanation
In order to be illustrated more clearly in the utility model embodiment or technological scheme of the prior art, to the accompanying drawing of required use in embodiment or description of the Prior Art be briefly described below, apparently, accompanying drawing in the following describes is only embodiments more of the present utility model, for those of ordinary skills, do not paying under the prerequisite of creative work, can also obtain according to these accompanying drawings other accompanying drawing.
Fig. 1 is the structural representation of the utility model patent leading type inverse proportion vacuum solenoid valve;
The schematic diagram of oil circuit when Fig. 2 is the utility model patent leading type inverse proportion vacuum solenoid valve no electric circuit;
(the schematic diagram of oil circuit when rated maximum current when Fig. 3 is the energising of the utility model patent leading type inverse proportion vacuum solenoid valve;
Principle schematic when Fig. 4 is the work of the utility model patent leading type inverse proportion vacuum solenoid valve;
Wherein reference character is: 1-valve seat, 2-Returnning spring, 3-spool, 4-valve body, 5-diaphragm, 6a-the first sliding bearing, 6b-the second sliding bearing, 7-bearing support, 8-pole shoe, 9-armature, 10-push rod, 11-connecting tube, 12-pad, 13-buting iron, 14-magnetic circuit plate, 15-adjusting screw, 16a-the first electric mortiser pin, 16b-the second electric mortiser pin, 17-Regulation spring, 18-coil housing, 19-yoke, 20a-the first filter screen, 20b-the second filter screen, 3a-guide's tracting pressuring hole, 3b-controls a mouthful tracting pressuring hole, 3c--controls a mouthful tracting pressuring hole, the first guide cavity imported oil of 3d-, 3e-pilot pressure feedback cavity, 4a-filler opening, 4b-controls mouth, 4c-control chamber drain tap, the first guide cavity drain tap of 4d-, 4e-pilot pressure feedback cavity,
f t -Regulation spring power,
f f -Returnning spring power,
f i -electromagnetic force,
f yx -first guide cavity hydraulic feedback power,
f yxz -first guide cavity hydraulic driving power,
f yz -control oral fluid to press feedback force,
s x -guide feedback cavity feedback area,
s z main valve chamber hydraulic pressure area,
p p -solenoid valve input pressure,
-electromagnetic valve mouth A mouth pressure,
p x -guide cavity pressure.
Embodiment
Below in conjunction with accompanying drawing, preferred embodiment of the present utility model is described in detail, thereby so that advantage of the present utility model and feature can be easier to be it will be appreciated by those skilled in the art that, protection domain of the present utility model is made to more explicit defining.
Consult Fig. 1, the utility model provides a kind of leading type inverse proportion vacuum solenoid valve, a kind of leading type inverse proportion vacuum solenoid valve, formed by main valve, pilot valve and proportion electro-magnet, described main valve is by valve body 4 and be positioned at the spool 3 of valve body 4 inside, and be riveted on the valve seat 1 on valve body 4, and be positioned at the inner Returnning spring 2 near valve seat 1 one sides of spool 3, and the intake screen 20a and the outlet filter screen 20b that are socketed in outside valve body 4 form;
Valve body 4 is provided with import 4a, controls mouthful 4b, main valve drain tap 4c and first guide cavity drain tap 4d.The first guide cavity oil inlet hole of the two sections of concentric cylindrical 3d that spool 3 radially arranges, and the concentric circle pass guide chamber tracting pressuring hole 3a adjacent with multistage is set in spool is communicated with backward guide's valve pocket 4e fuel feeding, spool 3 diametric(al)s are provided with circular hole control mouth tracting pressuring hole 3b, and are provided with eccentric circle pass control mouth tracting pressuring hole 3c with axial direction and are communicated with and are communicated with main valve pilot pressure feedback cavity 3e.When work, between spool 3 and valve body 4, under the effect of driving force, produce displacement, realize the switching of oil circuit, utilize spool 3 to realize the controllable adjustment to electromagnetic valve mouth pressure to the closed-loop feedback effect of pressure.
Pilot valve is by valve body 4, form with the push rod 10 of valve body 4 one end plane contact, and the Main Function of pilot valve is the output electromagnetic force of amplifying electromagnet, changes electromagnetic force dress into hydraulic driving power and drives main valve work.Its working principle is that overflow-type pressure regulates, the less first guide cavity filler opening 3d of diameter is to guide's valve pocket 4e fuel feeding, thereby the aperture size adjustment excess flow by the flow-off of formation between push rod 10 and valve body 4 is realized the control to first guide cavity 4e pressure, and overflow fluid is discharged by the first guide cavity drain tap 4d arranging on valve body 4.
Proportion electro-magnet is made up of diaphragm 5, the first sliding bearing 6a, the second sliding bearing 6b, bearing support 7, pole shoe 8, armature 9, push rod 10, connecting tube 11, pad 12, buting iron 13, magnetic circuit plate 14, adjusting screw 15, coil 16, Regulation spring 17, coil housing 18 and yoke 19; Pole shoe 8, armature 9, buting iron 13, magnetic circuit plate 14 and yoke 19 are made by soft magnetic material; Pole shoe 8, armature 8, buting iron 13, magnetic circuit plate 14, coil 16 are positioned at yoke 19 inside, the flux loop in the magnetic field producing while energising as coil 19.The tubular structure that yoke 19 is hollow, one end is fixed on valve body 4, and the other end is sealed by magnetic circuit plate 14.Between pole shoe 8 and buting iron 13 and connecting tube 11, rivet and be integrated, guarantee that electromagnet performance makes to install more easy simultaneously.Armature 9 is integrated with push rod 10 riveted joints, and armature institute is stressed push rod transmission, and install convenient.The first sliding axle 6a holds and is embedded in buting iron 13 inside and is socketed on push rod 10, and push rod 10 is played a supportive role.The second sliding bearing 6b is embedded in bearing support 7 inside and is integrated and is socketed on push rod 10 by bearing support 7 and pole shoe 8 riveted joints, and push rod 10 can slide between the first sliding bearing 6a and the second sliding bearing 6b.Push rod 10, as the part of electromagnetic force output, regulates the pressure of pilot pressure feedback cavity 4e simultaneously as pilot valve regulating element.Diaphragm 5 is between valve body 4 and pole shoe 8 and be socketed on push rod 10, following push rod 10 moves, play isolation pilot pressure feedback cavity 4e medium and flow into electromagnet inside, diaphragm 5 frequency of adjustable movement part simultaneously makes pilot pressure feedback cavity 4e pressure more stable in solenoid-driven signal frequency range.
Give when coil power supply, the ouput force value of electromagnet only with the size of input current about and location-independent with armature.Because proportional electromagnetic valve driving force has strict requirement, the deviation of electromagnetic force has directly determined the deviation of electromagnetic valve pressure.It is without accurate control to the position of armature 9 that the characteristic that the electromagnetic force of aforementioned proportion electromagnet and armature 9 displacements have nothing to do substantially makes electromagnet manufacture process, the assembly process of electromagnet is simplified greatly, and can export the work of accurate electromagnetic force driving pilot valve.Electromagnet part is provided with the pretension compressive force of adjusting screw 15 for Regulation spring 17, and this pretension compressive force and electromagnetic valve mouth pressure initial set value are one-to-one relationship.Thereby be applied to different user demands by realizing different initial setting pressure to the adjusting that regulates screw position when practical application.
Consult Fig. 2 also by reference to the accompanying drawings shown in 1, when no electric circuit, inlet pressure P enters pilot pressure feedback cavity (sequence number 4e in Fig. 1) by first guide cavity filler opening (sequence number 3d in Fig. 1), act on push rod (sequence number 10 in Fig. 1), the spring-force driven dual of Regulation spring (sequence number 17 in Fig. 1) is on push rod (sequence number 10 in Fig. 1), the two balance obtains the pressure of pilot pressure feedback cavity (sequence number 4e in Fig. 1), pilot valve overflow, and fluid is discharged by guide's drain tap (sequence number 4d in Fig. 1), the pressure-acting of pilot pressure feedback cavity (sequence number 4e in Fig. 1) is on spool (sequence number 3 in Fig. 1), produce downward first guide cavity hydraulic driving power, under formerly drain pressure driving force effect of spool (sequence number 3 in Fig. 1), move downward, between filler opening (sequence number 4a in Fig. 1) and control mouthful (sequence number 4b in Fig. 1), passage is opened, control pathway closure between mouthful (sequence number 4b in Fig. 1) and control chamber drain tap (sequence number 4c in Fig. 1), filler opening (sequence number 4a in Fig. 1) oil pressure enters pilot pressure feedback cavity (sequence number 3e in Fig. 1) by controlling a mouthful tracting pressuring hole (sequence number 3b in Fig. 1), produce the pilot pressure feedback force upwards to spool (sequence number 3 in Fig. 1), simultaneously, the spring force (much smaller than pilot pressure feedback force) of Returnning spring (sequence number 2 in Fig. 1) upwards acts on spool (sequence number 3 in Fig. 1).Under the formerly effect of guide cavity hydraulic driving power, Returnning spring power and pilot pressure feedback force of spool (sequence number 3 in Fig. 1), move up and down, alternately open and close between filler opening (sequence number 4a in Fig. 1), control mouthful (sequence number 4b in Fig. 1) and control chamber drain tap (sequence number 4c in Fig. 1), until spool (sequence number 3 in Fig. 1) reaches balance, obtain stable control mouth (sequence number 4b in Fig. 1) pressure.The pressure initiation of the pressure of first guide cavity like this and electromagnetic valve mouth relation one to one.
Consult Fig. 3 and in conjunction with shown in Fig. 1, in the time of energising and electric current increase, proportion electro-magnet produces the electromagnetic force compression adjustment spring (sequence number 17 in Fig. 1) that moves upward, the pilot pressure feedback cavity opening (sequence number 4e in Fig. 1) forming between push rod (sequence number 10 in Fig. 1) and valve body (sequence number 4 in Fig. 1) increases, pilot valve draining increases, because first guide cavity filler opening (sequence number 3d in Fig. 1) circulation area is limited, cause pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure decreased, pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure-acting after final reduction is on push rod (sequence number 10 in Fig. 1), the balance of making a concerted effort with the spring force of Regulation spring (sequence number 17 in Fig. 1) and the electromagnetic attraction of electromagnetic force, obtain pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure reducing.Because pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure is corresponding one by one with electromagnetic valve mouth (sequence number 4b in Fig. 1) pressure, electromagnetic valve mouth (sequence number 4b in Fig. 1) pressure being reduced.
In the time that electric current reaches maximum operating currenbt, pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure decreased is to approaching 0, and electromagnetic valve mouth (sequence number 4b in Fig. 1) pressure is 0.When electric current is from large to small time, electromagnet suction reduces, push rod (sequence number 10 in Fig. 1) moves down under the spring-force driven dual of Regulation spring (sequence number 17 in Fig. 1), push rod (sequence number 10 in Fig. 1) reduces with pilot pressure feedback cavity (sequence number 4e in Fig. 1) the overflow aperture that valve body (sequence number 4 in Fig. 1) forms, pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure increases, due to the one-to-one relationship of pilot pressure feedback cavity (sequence number 4e in Fig. 1) pressure and electromagnetic valve mouth (sequence number 4b in Fig. 1) pressure, electromagnetic valve mouth (sequence number 4b in Fig. 1) pressure increases.
Thus, obtain and control one to one mouthful (sequence number 4b in a Fig. 1) pressure by the control to solenoid valve input signal, control inversely proportional relation between mouthful (sequence number 4b in Fig. 1) pressure and input signal (equivalent electric flow valuve), the initial tension of spring that changes Regulation spring (sequence number 17 in Fig. 1) by adjusting screw (sequence number 15 in Fig. 1) can regulate the size of controlling mouthful (sequence number 4b in Fig. 1) no electric circuit state initial pressure.
In said process, first guide cavity drain tap (sequence number 4d in Fig. 1) is outwards oil extraction always, and between control chamber drain tap or outwards oil extraction (sequence number 4c in Fig. 1), oil-feed port (sequence number 4a in Fig. 1) continues fuel feeding.
This valve working method is if Fig. 4 is in conjunction with as shown in Fig. 1: electromagnet part output electromagnetic force
f i , act on armature (sequence number 12 in Fig. 1) upper, simultaneously the spring force of Regulation spring power
f t also act on armature, by the push rod output connecting as one with armature, guide's cavity pressure
p x act on the guide's hydraulic feedback area on push rod
s x form guide's hydraulic coupling
f yx , electromagnetic force
with guide's hydraulic coupling
f yx make a concerted effort and joint spring force spring force
f t balance.Guide's cavity pressure
p x act on the main valve hydraulic feedback area on spool
s z form downward guide's hydraulic driving power
f yz , with action of reset spring power spring force on spool
f f and electromagnetic valve mouth pressure
act on spool main valve hydraulic feedback area
s z the control hydraulic feedback power upwards forming
f yz balance.Electromagnetic valve mouth pressure
and the pass between input current I is
, the ratio electromagnetic force coefficient that wherein K is proportion electro-magnet, I is input current (being Equivalence value electric current while adopting pwm signal),
and inversely proportional relation between input current I.
Practical application shows, this valve has very high control accuracy, and manufacture process difficulty is moderate, stable performance, good product consistency, failure rate is low, be applicable in the multiple hydraulic system that needs accurate pressure control, in the hydraulic system of the automatic transmission case such as AT, AMT, DCT and CVT.
To the above-mentioned explanation of the disclosed embodiments, make professional and technical personnel in the field can realize or use the utility model.To be apparent for those skilled in the art to these embodiments' multiple modification, General Principle as defined herein can, in the situation that not departing from spirit or scope of the present utility model, realize in other embodiments.Therefore, the utility model will can not be limited to these embodiments shown in this article, but will accord with principle disclosed herein and features of novelty the widest consistent scope.
Claims (4)
1. a leading type inverse proportion vacuum solenoid valve, formed by main valve, pilot valve and proportion electro-magnet, it is characterized in that: described main valve comprises valve body, and be positioned at the spool of valve inner, and be riveted on the valve seat on valve body, and be positioned at the Returnning spring of valve core inside near valve seat one side, and be socketed in intake screen and outlet filter screen outside valve body; In described pilot valve, be provided with the push rod with valve body one end plane contact; Described proportion electro-magnet comprises diaphragm, the first sliding bearing, the second sliding bearing, bearing support, pole shoe, armature, push rod, connecting tube, pad, buting iron, magnetic circuit plate, adjusting screw, coil, Regulation spring, coil housing and yoke; Described yoke is the tubular structure of hollow, and one end is fixed on valve body, and the other end is sealed by magnetic circuit plate; Described pole shoe, armature, buting iron, magnetic circuit plate, coil are positioned at yoke inside; Between described pole shoe and buting iron and connecting tube, riveted joint is integrated; Described armature and push rod riveted joint are integrated; Described the first sliding bearing is embedded in buting iron inside and is socketed on push rod; Described the second sliding bearing is embedded in bearing support inside and is integrated and is socketed on push rod by bearing support and pole shoe riveted joint; Described push rod is arranged between sliding bearing and sliding bearing.
2. a kind of leading type inverse proportion vacuum solenoid valve according to claim 1, is characterized in that: described valve body, push rod and spool form guide's valve pocket.
3. a kind of leading type inverse proportion vacuum solenoid valve according to claim 1, is characterized in that: described diaphragm, between valve body and pole shoe, and is socketed on push rod.
4. a kind of leading type inverse proportion vacuum solenoid valve according to claim 1, it is characterized in that: described spool is provided with the concentric circle pass guide tracting pressuring hole that multistage is adjacent, and be communicated with the first guide cavity oil inlet hole of the two sections of concentric cylindrical radially arranging, and be communicated with guide's valve pocket, valve core diameter's direction is provided with circular hole control mouth tracting pressuring hole, and be provided with eccentric circle pass control mouth tracting pressuring hole with axial direction and be communicated with, and be communicated with main valve pilot pressure feedback cavity; On described valve body, be provided with import, control mouth, main valve drain tap and first guide cavity drain tap.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420010312.6U CN203670331U (en) | 2014-01-08 | 2014-01-08 | Pilot-operated type inverse proportion decompression solenoid valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420010312.6U CN203670331U (en) | 2014-01-08 | 2014-01-08 | Pilot-operated type inverse proportion decompression solenoid valve |
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| Publication Number | Publication Date |
|---|---|
| CN203670331U true CN203670331U (en) | 2014-06-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420010312.6U Expired - Fee Related CN203670331U (en) | 2014-01-08 | 2014-01-08 | Pilot-operated type inverse proportion decompression solenoid valve |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727083A (en) * | 2014-01-08 | 2014-04-16 | 浙江弘驰科技股份有限公司 | Pilot-operated type inverse proportional reducing solenoid valve |
| CN106763994A (en) * | 2017-02-28 | 2017-05-31 | 浙江工业大学 | The oblique wing torque-motor of coil external |
| CN106931169A (en) * | 2017-04-17 | 2017-07-07 | 天津华宁电子有限公司 | Mining electromagnetic pilot valve core |
-
2014
- 2014-01-08 CN CN201420010312.6U patent/CN203670331U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727083A (en) * | 2014-01-08 | 2014-04-16 | 浙江弘驰科技股份有限公司 | Pilot-operated type inverse proportional reducing solenoid valve |
| CN106763994A (en) * | 2017-02-28 | 2017-05-31 | 浙江工业大学 | The oblique wing torque-motor of coil external |
| CN106763994B (en) * | 2017-02-28 | 2022-11-25 | 浙江工业大学 | Inclined wing torque motor with external coil |
| CN106931169A (en) * | 2017-04-17 | 2017-07-07 | 天津华宁电子有限公司 | Mining electromagnetic pilot valve core |
| CN106931169B (en) * | 2017-04-17 | 2023-07-21 | 天津华宁电子有限公司 | Mining electromagnetic pilot valve core |
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| C14 | Grant of patent or utility model | ||
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| TR01 | Transfer of patent right |
Effective date of registration: 20170825 Address after: 321000, Jinhua 697 Yongkang street, Wucheng District, Zhejiang Province, Asia Pacific incubation base, room 1558 Patentee after: Jinhua Hongbo magnetron Technology Co. Ltd. Address before: 321000, No. two, Section 161, Rainbow Road, Jinhua, Zhejiang Patentee before: ZHEJIANG HONGCHI TECHNOLOGY CO., LTD. |
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Effective date of registration: 20180806 Address after: 321017 Jinhua, Zhejiang Wucheng District, Wucheng Binlin Street South Street Patentee after: ZHEJIANG HONGCHI TECHNOLOGY CO., LTD. Address before: 321000 room 1558, Yatai incubation base, 697 Yongkang street, Wucheng District, Jinhua, Zhejiang. Patentee before: Jinhua Hongbo magnetron Technology Co. Ltd. |
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| TR01 | Transfer of patent right |
Effective date of registration: 20181012 Address after: 321000 Jinhua, Zhejiang Wucheng District, Wucheng Binlin Street South Street Patentee after: JINHUA HONGCHANG ELECTRICAL EQUIPMENT CO., LTD. Address before: 321017 Jinhua, Zhejiang Wucheng District, Wucheng Binlin Street South Street Patentee before: ZHEJIANG HONGCHI TECHNOLOGY CO., LTD. |
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