CN209586568U - A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve - Google Patents
A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve Download PDFInfo
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- CN209586568U CN209586568U CN201920349232.6U CN201920349232U CN209586568U CN 209586568 U CN209586568 U CN 209586568U CN 201920349232 U CN201920349232 U CN 201920349232U CN 209586568 U CN209586568 U CN 209586568U
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Abstract
The utility model relates to a kind of marine low-speed mechanical electronic hydraulics to control oil inlet proportioning valve, including SERVO CONTROL valve module and fuel regulator valve component.SERVO CONTROL valve module includes servo oil oil inlet, servo oil oil return opening, pressure reducing valve component, proportion electro-magnet, proportional pressure-reducing valve component and piston component.SERVO CONTROL valve module can be flowed into directly from low speed machine servo system high pressure fuel source for adjusting servo oil pressure, servo oil, without additional configuration Hydraulic servo system.Fuel oil is introduced from fuel regulator valve component, and fuel oil is different from the oil duct of servo oil, avoids servo oil and fuel oil from mixing, to prevent fuel oil by servo oily pollution.By using electro-hydraulic servo control mode, the electromagnetic component that can avoid pilot valve is directly contacted with heavy oil with anticorrosion.Fuel regulator valve component is controlled by SERVO CONTROL valve module, realizes and fuel flow ratio is measured and is exported, while playing the role of adjusting rail pressure of common rail.
Description
Technical field
The utility model relates to electric hydraulic control valves, and in particular to a kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve.
Background technique
With the development of technology, because having many advantages, such as high pressure and flexible spray regime, high-pressure common-rail fuel system is got over
Come more applied on the marine low speed diesel engine of high power density.Injection pressure influences injection rate, mist within the system
Change the indexs such as characteristic, circulating fuel injection quantity, therefore the adjusting of injection pressure is key technology.
Oil inlet proportioning valve is one of the key part for adjusting injection pressure, is connected to oil transfer pump and (also known as sprays with high-pressure oil pump
Oil pump) between be mounted on the oil inlet position of high-pressure oil pump, according to the demand of common rail pressure to the oil inlet quantity for entering high-pressure oil pump
It is measured, keeps the amount of fuel for being transported to common rail consistent with the demand of system, and play the role of adjusting rail pressure.
Compared to light diesel fuel, the main selection of heavy oil peculiar to vessel because inexpensively becoming foreign-going ship mid low speed diesel fuel machine fuel oil, but
The high temperature corrosion characteristic of heavy oil can be stable to fuel system element function and the service life adversely affects, especially to electromagnetic component.
Therefore, how to avoid or reduce the problem of high temperature corrosion characteristic of heavy oil stablizes the adverse effect generated to electromagnetic component performance has
It is to be solved.
CN204628140U discloses combination valve, specifically a kind of to be made of safety valve, check valve and precursor overflow valve
Combination valve.Safety valve in combination valve is located at the left side of valve body, and check valve is located at the centre of valve body, is used to connection safety valve and elder generation
Overflow valve is led, precursor overflow valve is located at the right side of valve body.Its valve body is equipped with deflector hole A and deflector hole B, and deflector hole A connection is first
Overflow valve and check valve, deflector hole B connection check valve and safety valve are led, with structure is simple, easy to maintenance, leakage rate is low, rings
Answer the advantages that fast.
CN102506217B discloses a kind of controlled high-pressure common-rail fuel injection system of diesel engine proportion magnetic valve, electromagnetism
At the secured core of valve and moving iron core actuation be Conical pole surface, then with include conduit, helical spring, electromagnetic coil, rectangular iron
Core, shell, valve body, are assembled into solenoid valve jointly.When having driving current to input electromagnetic coil, magnetic field is generated through valve internal magnetic circuit, it is right
Moving iron core generates size electromagnetic force proportional to driving current, unrelated with stroke, it is made to overcome spring force mobile, and
Stop movement on the equalization point of two power, is maintained at moving iron core on one stable position, moving iron core can be by driving
The size of electric current is proportional, continuously moves, and the aperture of control valve is accurately proportionally controlled the stream of oil circuit according to driving current
Amount.
Above patent document is not directed to design for the structure of fuel oil oil duct different from servo oil.
Summary of the invention
The purpose of the utility model is to provide a kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valves, it can be achieved that fuel flow
Ratio metering, adjusts rail pressure of common rail；Mode is indirectly controlled using hydraulic servo, to fuel oil and servo oil stream, avoids high temperature rotten
The fuel medium of erosion directly contacts electromagnetic component, and the structure is enable to be suitable for the requirement of high temperature corrosion media environment.With constantly
It can avoid servo oil and fuel oil mixing, to prevent fuel oil by servo oily pollution.
A kind of marine low-speed mechanical electronic hydraulic described in the utility model controls oil inlet proportioning valve, including SERVO CONTROL valve module and
Fuel regulator valve component；
The SERVO CONTROL valve module includes servo oil oil inlet, servo oil oil return opening, pressure reducing valve component, ratio electromagnetism
Iron, proportional pressure-reducing valve component and piston component；
The piston component includes plunger shaft, the piston in plunger shaft and the piston rod being connected with the piston；
The proportional pressure-reducing valve component includes the first valve body, is arranged in intracorporal first valve port of the first valve, is located at the first valve
First oil inlet of mouth upstream, the first oil outlet positioned at the first valve port downstream and setting are in first valve intracorporal first
Spool, the proportion electro-magnet is for driving first valve core movement to adjust the aperture of first valve port；
The oil inlet of the pressure reducing valve component is communicated with the servo oil oil inlet, the oil outlet of the pressure reducing valve component with
First oil inlet communicates, and first oil outlet is communicated with the oil inlet of the plunger shaft；
The fuel regulator valve component exists including the second valve body, setting in intracorporal second valve port of second valve, setting
The fuel oil oil inlet of second valve port upstream, the fuel oil oil outlet that the second valve port downstream is arranged in and setting are in second valve body
The second interior spool, the piston rod protrude into second valve body, and the piston rod is for driving second valve core movement
To control the aperture of second valve port.
Further, slide bar chamber is equipped in second valve body, the piston rod and second spool protrude into the cunning
In rod cavity, the slide bar is intracavitary equipped with slide opening and the slide bar that is slidably matched with the slide opening, one end of the slide bar with it is described
The end of piston rod offsets, and the other end of the slide bar offsets with second spool, sets between the slide bar and the slide opening
There is band, the slide bar chamber is separated into the first chamber and the second chamber by the band.
Further, it is equipped in second valve body and is returned for the described first intracavitary servo oil to be drained into the servo oil
First drainage channel of hydraulic fluid port.
Further, it is equipped in second valve body for the described second intracavitary fuel oil to be drained to outside second valve body
The second drainage channel.
Further, the fuel oil control that there is second spool towards slide bar direction movement tendency is equipped in second valve body
Valve spring processed.
Further, first valve body is fixedly connected by screw element with second valve body.
Further, the plunger shaft is arranged in the first valve body, the oil inlet of first oil outlet and the plunger shaft
Between be equipped with servo oil duct.
Further, the pressure sensor for detecting fuel path oil pressure is connected on the fuel regulator valve component.
The beneficial effects of the utility model are:
Due to using modular designs structure, mainly it is made of SERVO CONTROL valve module and fuel regulator valve component, conveniently
Installation, maintenance.
Due to the depressurization of SERVO CONTROL valve module, servo oil can be directly from low speed machine servo system high pressure oil source stream
Enter, without additional configuration Hydraulic servo system.Fuel oil is different from the oil duct of servo oil, avoids servo oil and fuel oil from mixing, to prevent from firing
Oil is by servo oily pollution.Fuel oil is introduced from fuel regulator valve component, and uses electro-hydraulic servo control mode, can avoid SERVO CONTROL
The electromagnetic component of valve is directly contacted with heavy oil with anticorrosion.
Fuel regulator valve component is controlled by SERVO CONTROL valve module, realizes and fuel flow ratio is measured and is exported, together
When play the role of adjust rail pressure of common rail.
Detailed description of the invention
Fig. 1 is the top view of the utility model；
Fig. 2 is structural schematic diagram shown in C-C in Fig. 1；
Fig. 3 is the structural schematic diagram of SERVO CONTROL valve module in the utility model.
In figure:
1- SERVO CONTROL valve module:
10- pressure reducing valve component, 100- valve base of pressure reducing valve, 101- pressure-relief valve spring, 102- depressurize valve follower, 103- pressure reducing valve
Valve pocket, 104- depressurize valve core；
11- proportion electro-magnet；
12- proportional pressure-reducing valve component, 120- proportional pressure-reducing valve spring base, 121- proportional pressure-reducing valve spring, the first valve of 122-
Core, 123- proportional pressure-reducing valve valve pocket；
The first valve body of 13-；
14- piston component, 140- piston guide bush, 141- sealing ring, 142- piston rod；
2- fuel regulator valve component:
The second valve body of 20-, 21- fuel regulator valve guide sleeve, 22- slide bar, 23- fuel regulator valve valve pocket, the second spool of 24-,
25- fuel regulator valve spring base, 26- fuel regulator valve spring, 27- plug screw；
3- sensor.
Specific embodiment
The technical program is described further with reference to the accompanying drawings and examples.
Referring to Fig. 1 to Fig. 3, shown in a kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve, matched using plug-in unit and couple
The modularized design of conjunction is in order to dismounting, including SERVO CONTROL valve module 1 and fuel regulator valve component 2.
The SERVO CONTROL valve module 1 includes servo oil oil inlet P 1, servo oil oil return inlet T, pressure reducing valve component 10, ratio
Electromagnet 11, proportional pressure-reducing valve component 12 and piston component 14.
The piston component 14 includes plunger shaft, the piston in plunger shaft and the piston rod being connected with the piston
142。
The proportional pressure-reducing valve component 12 include the first valve body 13, be arranged in first valve body 13 the first valve port,
The first oil inlet positioned at the first valve port upstream, the first oil outlet C3 positioned at the first valve port downstream and setting are described first
The first spool 122 in valve body 13, the proportion electro-magnet 11 adjust described for driving first spool 122 movement
The aperture of one valve port.
Further, the proportional pressure-reducing valve component 12 further includes proportional pressure-reducing valve spring base 120, proportional pressure-reducing valve spring
121 and proportional pressure-reducing valve valve pocket 123.
First spool 122 is arranged in proportional pressure-reducing valve valve pocket 123, proportional pressure-reducing valve valve pocket 123 and described first
Valve body 13, which is formed, to be threadedly coupled.The mesoporous of proportional pressure-reducing valve spring base 120 and first spool 122, which is formed, to be interference fitted and makes
The left side of first spool 122 described in its right end face contact.The proportional pressure-reducing valve spring base 120 is equipped with towards first valve
The proportional pressure-reducing valve spring 121 of core 122.The proportional pressure-reducing valve spring 121 uses pyramidal structure to save the installation of spring sky
Between, and when using magnetic separator to prevent the proportion electro-magnet 11 to be powered push rod to lighter in weight and inertia lesser described the
One spool 122 generates suction and is formed by change first spool 122 and match with the proportional pressure-reducing valve valve pocket 123
The aperture of valve port, push rod use non-magnet material.
Further, the plunger shaft is arranged in first valve body 13.The piston component 14 further includes piston guide bush
140 and sealing ring 141, piston guide bush 140 is arranged in the plunger shaft.One end of the piston rod 142 is arranged in the work
It fills in guide sleeve 140, the other end protrudes into the fuel regulator valve component 2.Between the piston rod 142 and the piston guide bush 140
Realized and sealed by the sealing ring 141, keep the mobile frictional resistance generated of the piston rod 142 smaller and have it is good from
Lubrication property.The sealing ring 141 uses Glais ring.
Further, wet type proportion electro-magnet, including coil, armature, push rod and shell can be used in the proportion electro-magnet 11,
And it is fixedly connected with first valve body 13.The course of work of the proportion electro-magnet 11 is: when there is electric signal input coil,
Magnetic field generates active force to armature in coil, and size and Orientation of the armature in magnetic field by signal code is proportional, continuously moves
It is dynamic, then the drive push rod movement of the pin by linking together, push rod is for pushing first spool 122.
Further, the proportional pressure-reducing valve component 12 further includes the oil pocket C1 and Oil Guide communicated with first spool 122
Chamber C2.The Oil Guide chamber C2 is arranged in the proportional pressure-reducing valve valve pocket 123, is used for and first oil inlet and described first
Oil outlet 3 communicates.The oil pocket C1 is also communicated with the servo oil oil return inlet T.
The oil inlet of the pressure reducing valve component 10 is communicated with the servo oil oil inlet P 1, and the pressure reducing valve component 10 goes out
Hydraulic fluid port is communicated with first oil inlet, and the first oil outlet C3 is communicated with the oil inlet of the plunger shaft.
Further, servo oil duct is equipped between the first oil outlet C3 and the oil inlet of the plunger shaft.
Further, the pressure reducing valve component 10 include valve base of pressure reducing valve 100, pressure-relief valve spring 101, decompression valve follower 102,
Pressure reducing valve valve pocket 103 and decompression valve core 104.
The valve base of pressure reducing valve 100 is assembled in a manner of plug-in unit from the upper surface of first valve body 13 from top to bottom
It is threadedly engaged in first valve body 13 with being formed, the downward decompression is equipped in the empty slot of the valve base of pressure reducing valve 100
Valve spring 101, the decompression valve follower 102 form coaxial mobile cooperation, the decompression valve core with the pressure-relief valve spring 101
104 are arranged in the pressure reducing valve valve pocket 103.
The mesoporous of the decompression valve follower 102 and the decompression valve core 104, which is formed, to be interference fitted, in the pressure reducing valve bullet
Under the pretightning force effect of spring 101, the bottom surface of the decompression valve core 104 is concordant with the bottom of the pressure reducing valve valve pocket 103, with
Guarantee valve port initial opening.Described in being pushed under the elastic force effect of the pressure-relief valve spring 101 by the decompression valve follower 102
Valve core 104 is depressurized, to realize that valve port opening is adjusted.
Further, the pressure reducing valve component 10 further includes oil pocket B1, the oil pocket communicated respectively with the decompression valve core 104
B2, oil pocket B3 and output cavity B4.The oil pocket B2 is communicated with the oil inlet of the pressure reducing valve component 10.The one end the output cavity B4
It is sequentially communicated with oil pocket B3, oil pocket B2, the other end is communicated with the oil outlet of the pressure reducing valve component 10.The oil pocket B1 with it is described
Servo oil oil return inlet T communicates.
The fuel regulator valve component 2 includes the second valve body 20, the second valve port being arranged in second valve body 20, sets
Set the second valve port upstream fuel oil oil inlet P 2, be arranged in the second valve port downstream fuel oil oil outlet A1 and be arranged described
The second spool 24 in second valve body 20, the piston rod 142 protrude into second valve body 20, and the piston rod 142 is used for
The movement of the second spool 24 is driven to control the aperture of second valve port.
Further, by making the end face of the fuel regulator valve spring base 25 and second spool 24 being in contact with it
The stepped hole bottom surface of shoulder and the fuel regulator valve valve pocket 23 alignment, to guarantee the initial opening of the second valve port.
Further, slide bar chamber is equipped between fuel regulator valve guide sleeve 21 in second valve body 20, the slide bar is intracavitary
Equipped with slide opening and the slide bar being slidably matched with the slide opening 22.The piston rod 142 and second spool 24 protrude into institute
It is intracavitary to state slide bar, second spool 24 is simultaneously arranged in fuel regulator valve valve pocket 23.One end of the slide bar 22 and the work
The end of stopper rod 142 offsets, and the other end of the slide bar 22 offsets with second spool 24.
Band is equipped between the slide bar 22 and the slide opening, the slide bar chamber is separated into the first chamber by the band
With the second chamber.It is equipped in second valve body 20 for the described first intracavitary servo oil to be drained into the servo oil oil return opening
The first drainage channel of T.By axial hole and radial hole in second valve body 20, equipped with for by the described second intracavitary combustion
Oil is drained to the second drainage channel outside second valve body 20.Fuel oil is different from the oil duct of servo oil, avoids servo oil and combustion
Oil mixing, to prevent fuel oil by servo oily pollution.
Further, the fuel regulator valve component 2 further includes fixed structure, which is assembled to institute from outside to inside
It states in the second valve body 20 and forms closing cooperation with second spool 24.
The fixed structure includes fuel regulator valve spring base 25, fuel regulator valve spring 26 and plug screw 27.The fuel oil
The side in second spool 24 backwards to the slide bar 22, the fuel regulator valve spring base is arranged in control valve spring seat 25
The fuel regulator valve spring 26 that there is second spool 24 towards 22 direction movement tendency of slide bar, the plug screw are connected on 25
27 are assembled in second valve body 20 from outside to inside and form immovable fitting with the fuel regulator valve spring 26, make described
Fuel regulator valve spring 26 plays the role of return to second spool 24.
Further, first valve body 13 is fixedly connected by screw element with second valve body 20.
Further, the work that detection fuel path oil pressure is played on the fuel regulator valve component 2 is arranged in sensor 3
With pressure sensor can be used.
Further, high-pressure oil pump leakage return flow oil outlet R is additionally provided on the fuel regulator valve component 2.
A kind of specific work process of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve is as described below:
Servo oil is introduced from low speed machine servo system high pressure fuel source (about 200bar), through the servo oil oil inlet P 1
Oil pocket B2 is flowed to, oil pocket B3 is flowed to by the mesoporous of the decompression valve core 104, the inclined hole through 104 lower end of the first spool
Flow to output cavity B4.Servo oil backflows from oil pocket B1 by the servo oil oil return inlet T to servo fuel tank when excessive.
When the servo Chuck Steak in output cavity B4, when oil pressure is more than the preload force value of the pressure-relief valve spring 101, oil pocket
Servo oil in B3 is damped gap and flows to the bottom surface of the decompression valve core 104 and push depressurized valve core 104 upwards
Mobile, flow area and spillway discharge by changing valve port finally make the oil of output cavity B4 to reduce the oil pressure in oil pocket B3
Pressure and the pretightning force of the pressure-relief valve spring 101 reach balance, and oil pressure is about 20bar at this time, to keep output oil pressure steady
It is fixed.
Original state, the proportion electro-magnet 11 are not powered on, and the first oil outlet C3 is through oil pocket C1 and servo oil
Oil return inlet T communicates, and is in blocking state with the output cavity B4.In this case, the oil pressure in the first oil outlet C3
It is zero.When the proportion electro-magnet 11 receives input electrical signal and exports corresponding electromagnetic push, the proportional pressure-reducing valve bullet
Spring abutment 120 and first spool 122 overcome the preload masterpiece of the proportional pressure-reducing valve spring 121 under the action of electromagnetic push
It with moving right jointly, communicates Oil Guide chamber C2 gradually with first oil inlet and the first oil outlet C3, keeps servo oily
The oil inlet for flowing to the plunger shaft pushes the piston rod 142.
The piston rod 142 protrudes into second valve body 20, keeps second spool 24 mobile to control by slide bar 22
The aperture for making the second valve port is connected to and disconnects fuel path by changing the gap between the second spool and valve seat, realizes combustion
The adjusting of oil stream amount controls and output.
Fuel oil is flowed into second spool 24 from the fuel oil oil inlet P 2 on the fuel regulator valve component 2, and is led to
It crosses the second valve port and flows to fuel oil oil outlet A1, high-pressure oil pump is flowed to by fuel oil oil outlet A1, can play and adjust common rail rail
The effect of pressure.
It is proportional to input electrical signal that the proportion electro-magnet 11 drives the proportional pressure-reducing valve component 12 to be allowed to output
Servo pressure, servo oil acts on the piston rod 142, and pushes second spool 24 to move by the slide bar 22, makes
The fuel flow of output relationship proportional to the input electrical signal of the proportion electro-magnet 11, can be realized the ratio of fuel flow
Function of measuring.
The marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve indirectly controls mode using hydraulic servo, avoids heavy oil direct
Proportion electro-magnet is contacted, so that it is unstable not preferably to solve the performance generated by the high temperature corrosion characteristic of heavy oil to electromagnetic component
The difficulties such as benefit influence.
The above is only the preferred embodiment of the utility model, it is noted that for the common skill of the art
For art personnel, without deviating from the technical principle of the utility model, several improvement and replacement can also be made, these change
It also should be regarded as the protection scope of the utility model into replacement.
Claims (8)
1. a kind of marine low-speed mechanical electronic hydraulic controls oil inlet proportioning valve, it is characterised in that: including SERVO CONTROL valve module (1) and fuel oil
Control valve group (2)；
The SERVO CONTROL valve module (1) include servo oil oil inlet (P1), servo oil oil return opening (T), pressure reducing valve component (10),
Proportion electro-magnet (11), proportional pressure-reducing valve component (12) and piston component (14)；
The piston component (14) includes plunger shaft, the piston in plunger shaft and the piston rod being connected with the piston
(142)；
The proportional pressure-reducing valve component (12) includes the first valve of the first valve body (13), setting in first valve body (13)
Mouth, the first oil inlet positioned at the first valve port upstream, the first oil outlet (C3) positioned at the first valve port downstream and setting are in institute
The first spool (122) in the first valve body (13) is stated, the proportion electro-magnet (11) is for driving first spool (122) to transport
The dynamic aperture to adjust first valve port；
The oil inlet of the pressure reducing valve component (10) is communicated with the servo oil oil inlet (P1), the pressure reducing valve component (10)
Oil outlet is communicated with first oil inlet, and first oil outlet (C3) communicates with the oil inlet of the plunger shaft；
The fuel regulator valve component (2) include the second valve body (20), be arranged the second valve port in second valve body (20),
The fuel oil oil inlet (P2) of second valve port upstream, the fuel oil oil outlet (A1) that the second valve port downstream is arranged in and setting are set
The second spool (24) in second valve body (20), the piston rod (142) is protruded into second valve body (20), described
The aperture that piston rod (142) is used to drive the second spool (24) movement to control second valve port.
2. marine low-speed mechanical electronic hydraulic according to claim 1 controls oil inlet proportioning valve, which is characterized in that second valve body
(20) slide bar chamber is equipped in, it is intracavitary that the piston rod (142) and second spool (24) protrude into the slide bar；The slide bar
The intracavitary slide bar (22) for being equipped with slide opening and being slidably matched with the slide opening, one end of the slide bar (22) and the piston rod
(142) end offsets, and the other end of the slide bar (22) offsets with second spool (24), the slide bar (22) and described
Band is equipped between slide opening, the slide bar chamber is separated into the first chamber and the second chamber by the band.
3. marine low-speed mechanical electronic hydraulic according to claim 2 controls oil inlet proportioning valve, which is characterized in that second valve body
(20) the first drainage channel for the described first intracavitary servo oil to be drained into the servo oil oil return opening (T) is equipped in.
4. marine low-speed mechanical electronic hydraulic according to claim 2 controls oil inlet proportioning valve, which is characterized in that second valve body
(20) it is equipped in for the described second intracavitary fuel oil to be drained to the second drainage channel of second valve body (20) outside.
5. marine low-speed mechanical electronic hydraulic according to claim 2 controls oil inlet proportioning valve, which is characterized in that second valve body
(20) the fuel regulator valve spring (26) that there is second spool (24) towards slide bar (22) direction movement tendency is equipped in.
6. marine low-speed mechanical electronic hydraulic according to claim 1 controls oil inlet proportioning valve, which is characterized in that first valve body
(13) it is fixedly connected by screw element with second valve body (20).
7. marine low-speed mechanical electronic hydraulic according to claim 1 controls oil inlet proportioning valve, which is characterized in that the plunger shaft is set
It sets in the first valve body (13), servo oil duct is equipped between first oil outlet (C3) and the oil inlet of the plunger shaft.
8. marine low-speed mechanical electronic hydraulic according to claim 1 controls oil inlet proportioning valve, which is characterized in that the fuel oil control
The pressure sensor for detecting fuel path oil pressure is connected on valve module (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920349232.6U CN209586568U (en) | 2019-03-19 | 2019-03-19 | A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920349232.6U CN209586568U (en) | 2019-03-19 | 2019-03-19 | A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve |
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| Publication Number | Publication Date |
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| CN209586568U true CN209586568U (en) | 2019-11-05 |
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ID=68374603
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| CN201920349232.6U Active CN209586568U (en) | 2019-03-19 | 2019-03-19 | A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109812365A (en) * | 2019-03-19 | 2019-05-28 | 重庆红江机械有限责任公司 | A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve |
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2019
- 2019-03-19 CN CN201920349232.6U patent/CN209586568U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109812365A (en) * | 2019-03-19 | 2019-05-28 | 重庆红江机械有限责任公司 | A kind of marine low-speed mechanical electronic hydraulic control oil inlet proportioning valve |
| CN109812365B (en) * | 2019-03-19 | 2024-01-19 | 重庆红江机械有限责任公司 | Marine low-speed electromechanical hydraulic control oil inlet proportional valve |
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