CN209818410U - Deep sea buoy hydraulic system - Google Patents
Deep sea buoy hydraulic system Download PDFInfo
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- CN209818410U CN209818410U CN201920004482.6U CN201920004482U CN209818410U CN 209818410 U CN209818410 U CN 209818410U CN 201920004482 U CN201920004482 U CN 201920004482U CN 209818410 U CN209818410 U CN 209818410U
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Abstract
A deep sea buoy hydraulic system comprising: the oil outlet of the inner oil bag is connected with a bidirectional gear pump, the bidirectional gear pump is respectively connected with an oil tank and an oil inlet of the outer oil bag through a pressurizing unit, the oil outlet of the outer oil bag is connected with the bidirectional gear pump to form a closed hydraulic oil path, and the bidirectional gear pump is matched with the pressurizing unit for use, so that the problem of insufficient self-priming capacity caused by a plunger pump is solved, the energy consumption is reduced by the low-pressure bidirectional gear pump and the pressurizing unit, and the underwater working time is prolonged; the double-acting booster pump is adopted, the boosting is realized by adopting a mechanical structure in the double-acting booster pump, the flexibility of floating and submerging is high, and the problems of overlarge space occupation and overlarge load caused by an air pump and auxiliary structures such as an installation driving air pump are solved.
Description
Technical Field
The utility model relates to an ocean detects technical field, especially relates to a deep sea buoy hydraulic system.
Background
The ocean profile buoy is also called as an Argo buoy, is mainly used for profile parameter detection, data sampling and data transmission, and can automatically complete floating and submerging motions in the detection process.
At present, most of ocean section buoys in China are 2000-meter section buoys, the research and development of the ocean section buoys are in a mature stage, the research on the 4000-meter section buoys and the 6000-meter section buoys is still in a theoretical and experimental stage, and especially the research on a hydraulic system of the section buoys in deep sea areas is still in a primary stage. In addition, U.S. Teledyne Webb company has developed 4000-meter APEX-type section buoys, Scripps oceanographic research institute has successfully developed 6000-meter Deep SOLO-type buoys, and has been put into observation, the hydraulic systems of the section buoys, whether COPEX-type section buoys developed in China or APEX-type buoys developed in the U.S., most of the hydraulic systems of the section buoys adopt a buoyancy hydraulic adjusting system using a high-pressure plunger pump as power to adjust the volume of oil between inner and outer oil bags so as to control the section buoys to float upwards and downwards, for example, the utility model of CN2014106186201 discloses a Deep sea buoyancy adjusting system which adopts a 70-100MPa positive displacement high-pressure plunger pump, and the product is imported and very expensive. In addition, the profile buoy has different pressures at different depths, the pressure is increased along with the increase of the ocean depth, the larger the depth is, the larger the acting force of the external seawater pressure on the external oil bag is, and therefore the larger the driving force of the hydraulic pump for driving oil in the internal oil bag to enter the external oil bag is. The problem that self-priming capability is insufficient often exists due to the self structural characteristics of a plunger pump, and in order to solve the problem, in the prior art, a high-pressure plunger pump is usually matched with an air pump to improve the pressure of an oil inlet so as to ensure that the pump can work stably; meanwhile, the energy consumption is increased due to the adoption of the high-pressure plunger pump, and the underwater working time of the section buoy is reduced.
The above description is included in the technical recognition scope of the inventors, and does not necessarily constitute the prior art.
SUMMERY OF THE UTILITY MODEL
The utility model provides a deep sea buoy hydraulic system, it has not only solved the not enough problem of self priming force because of the plunger pump brings, has the energy consumption moreover little, has prolonged operating time under water, and two effect booster pumps light in weight, small, the flexibility of diving is high for the come-up, has avoided occupying too big condition because of the space that auxiliary structure such as the motors of installation air pump and drive air pump brought, has solved the problem among the prior art.
The utility model discloses a solve the technical scheme that above-mentioned technical problem adopted and be:
the utility model provides a deep sea buoy hydraulic system, includes interior oil bag, the oil-out of interior oil bag links to each other with two-way gear pump, two-way gear pump is driven by servo motor, two-way gear pump passes through the pressure boost unit is connected with oil tank and outer oil bag oil inlet respectively, the oil-out of outer oil bag links to each other with two-way gear pump and forms closed hydraulic circuit, sets up not only can solve the not enough problem of self priming that the plunger pump brought, and two-way gear pump helps simplifying hydraulic system moreover for can realize the switching-over with less electromagnetic directional valve.
The pressurizing unit comprises a reversing unit and a double-acting pressurizing cylinder which are respectively connected with the bidirectional gear pump, the reversing unit is connected with the double-acting pressurizing cylinder, and an oil outlet of the double-acting pressurizing cylinder is connected with an oil inlet of the outer oil bag.
The reversing unit is a reversing slide valve, an oil inlet of the reversing slide valve is connected with the bidirectional gear pump, and an oil outlet of the reversing slide valve is connected with the double-acting pressure cylinder.
The double-acting pressure cylinder is sequentially provided with a first hydraulic cavity, a second hydraulic cavity and a third hydraulic cavity from one end to the other end at intervals, the sectional area of the second hydraulic cavity is larger than that of the first hydraulic cavity and that of the third hydraulic cavity, the structure and the sectional area of the first hydraulic cavity are the same as those of the third hydraulic cavity, cross sliders are movably mounted in the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity and penetrate through the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity to enable the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity to move in two directions;
the second hydraulic cavity is divided into a fourth hydraulic cavity and a fifth hydraulic cavity by a crosshead shoe, the fourth hydraulic cavity and the fifth hydraulic cavity are connected with a reversing slide valve, an oil inlet of the reversing slide valve is connected with a bidirectional gear pump, and an oil return port is connected with an oil tank through a one-way valve on an oil pipe;
the first hydraulic cavity is connected with the bidirectional gear pump and the outer oil bag through two first one-way valves respectively, and the third hydraulic cavity is connected with the bidirectional gear pump and the outer oil bag through two second one-way valves respectively.
An overflow valve is arranged between the oil outlet of the outer oil bag and the oil inlet of the inner oil bag.
And a damping hole is also arranged between the electromagnetic switch and the oil outlet of the bidirectional gear pump.
And an electromagnetic valve or a pressure switch is arranged between the oil outlet of the outer oil bag and the bidirectional gear pump.
The oil outlet of the inner oil bag is also connected with a control device, and the control device is connected with a servo motor.
The control device comprises an amplifier connected with an oil outlet of the inner oil bag, and the amplifier is also connected with the servo motor through an encoder.
And magnetostrictive displacement sensors are respectively arranged in the first hydraulic cavity and the third hydraulic cavity, the magnetostrictive displacement sensors are connected with an amplifier, and the amplifier controls the reversing slide valve to act.
The utility model adopts the technical scheme that the pump has the advantages of light weight and long service life, and in order to solve the problem of insufficient self-suction force caused by the plunger pump, the low-pressure bidirectional gear pump and the double-acting pressure cylinder are matched to solve the problem of insufficient self-suction force caused by the plunger pump; and the adoption of the bidirectional gear pump can simplify a hydraulic system, so that fewer electromagnetic reversing valves can be adopted to realize reversing, and the energy consumption and the weight of the whole hydraulic system are reduced. Meanwhile, the inside of the double-acting pressure cylinder utilizes the characteristics of large section, small flow velocity and small pressure; the principle of small section, large flow velocity and large pressure is that the low-pressure oil of the low-pressure bidirectional gear pump is pressurized to high-pressure oil with a ratio of at least 1:6 through a mechanical structure, so that the energy consumption is reduced, and the underwater working time of the section buoy is prolonged; in addition, the installation of the air pump is reduced in the application, so that auxiliary devices such as a motor and an air delivery pipe for providing power for the air pump are reduced, and the double-acting pressure cylinder has the characteristics of light weight and small volume compared with an air pump auxiliary pressure device of the air pump, reduces the load of a section buoy and small floating resistance in space, and improves the flexibility of floating and submerging; in order to protect the whole system from pressure-bearing overload, an overflow valve is arranged in the system to protect an oil way; the damping hole is arranged, so that the oil quantity of an oil way can be controlled in the submergence process, and the instant impact and the damage to a hydraulic element are prevented.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of the present invention;
FIG. 2 is a schematic structural view of a double-acting pressure cylinder according to the present invention;
FIG. 3 is a logic control diagram of the hydraulic system for adjusting the floating of the section buoy;
FIG. 4 is a logic control diagram of the submergence of the hydraulic system adjusting profile buoy.
In the figure, 1, a bag is arranged in the machine, 2, a bidirectional gear pump, 3, a servo motor, 4, an amplifier, 5, an encoder, 6, a reversing slide valve, 7, a double-acting pressure cylinder, 8, a second one-way valve, 9, a first one-way valve, 10, an electromagnetic valve, 11, an outer oil bag, 12, a damping hole, 13, an overflow valve, 14, a linear displacement sensor, 15, a cross slide block, 16, a first hydraulic cavity, 17, a fourth hydraulic cavity, 18, a fifth hydraulic cavity, 19, a third hydraulic cavity, 20, a one-way valve, 21 and a magnetostrictive displacement sensor.
Detailed Description
In order to clearly illustrate the technical features of the present invention, the present invention is explained in detail by the following embodiments with reference to the accompanying drawings.
As shown in fig. 1-4, a deep sea buoy hydraulic system includes: interior oil pocket 1, the oil-out of interior oil pocket 1 links to each other with two-way gear pump 2, adopts operating pressure to be 7-15MPa, the low pressure two-way gear pump 2 that the discharge capacity is 0.75ml/r in this embodiment, and the plunger pump is generally more expensive than two-way gear pump 2, under the same operating pressure, accomplishes the same working oil volume, and the energy consumption of low pressure two-way gear pump 2 is 1/5 of high pressure plunger pump, greatly reduced the energy consumption to utilize this two-way gear pump 2 can shorten operating time and improve system work efficiency. This two-way gear pump 2 is driven by servo motor 3, two-way gear pump 2 passes through the pressure cell and is connected with oil tank and 11 oil inlets of outer oil pocket respectively, and this pressure cell cooperates with the two-way gear pump of low pressure, has solved the not enough problem of plunger pump self priming, is equipped with solenoid valve 10 or pressure switch and links to each other and form closed hydraulic pressure oil circuit between the oil-out of outer oil pocket 11 and the oil-out of two-way gear pump 2.
Further, the pressurizing unit comprises a reversing unit connected with the bidirectional gear pump 2 and a double-acting pressurizing cylinder 7 connected with the bidirectional gear pump 2, the reversing unit adopts a reversing slide valve 6 to realize reversing function, the pressurizing ratio of the double-acting pressurizing cylinder 7 is at least 6:1, the working pressure of a high-pressure cavity can at least reach 60MPa, the reversing slide valve 6 is connected with the double-acting pressurizing cylinder 7, hydraulic oil in the bidirectional gear pump 2 enters the double-acting pressurizing cylinder 7 through the reversing slide valve 6 to drive the double-acting pressurizing cylinder 7 to reverse and pressurize the internal hydraulic oil, the pressurized hydraulic oil enters the external oil sac 11 from the oil outlet of the double-acting pressurizing cylinder 7, the hydraulic oil for driving the double-acting pressurizing cylinder 7 to reverse enters the oil tank gear pump through the reversing slide valve 6 and the one-way valve 20 on the oil pipe, and the problem of insufficient self-priming force of the high-pressure plunger pump in deep sea area is effectively solved through the cooperation of the, meanwhile, the pressurizing unit increases the pressure of the hydraulic oil entering the outer oil bag in a mechanical structure mode, the traditional air pump is replaced to increase the pressure of the hydraulic oil, and therefore the air pump is reduced, and the auxiliary devices needed by the motor for providing power for the air pump, the air conveying pipe and the like are reduced, so that the internal load and the internal space of the whole section buoy are reduced.
Further, as shown in fig. 2, the double-acting pressure cylinder 7 is sequentially provided with a first hydraulic chamber 16, a second hydraulic chamber and a third hydraulic chamber 19 from left to right at intervals, the sectional area of the second hydraulic chamber is larger than the sectional areas of the first hydraulic chamber 16 and the third hydraulic chamber 19, the pressure of hydraulic oil is increased by changing the sectional areas, the structure and the sectional area of the first hydraulic chamber 16 are the same as those of the third hydraulic chamber 19, a cross slider 15 is movably installed in the first hydraulic chamber 16, the second hydraulic chamber and the third hydraulic chamber 19, the cross slider 15 penetrates through the first hydraulic chamber 16, the second hydraulic chamber and the third hydraulic chamber 19 to enable the first hydraulic chamber 16, the second hydraulic chamber and the third hydraulic chamber 19 to move in two directions, the sectional areas of the first hydraulic chamber 16 and the third hydraulic chamber 19 are the same to enable the first hydraulic chamber 16 and the third hydraulic chamber 19 to form hydraulic oil with the same pressure at two ends of the double-acting pressure cylinder 7, the cross slider 15 moves left and right between the first hydraulic chamber 16 and the third hydraulic chamber 19 to alternately increase the, high-pressure oil is continuously supplied to the outer oil bag 11.
The first hydraulic cavity 16 is respectively connected with the bidirectional gear pump 2 and the outer oil bag 11 through two first one-way valves 9, and the third hydraulic cavity 19 is respectively connected with the bidirectional gear pump 2 and the outer oil bag 11 through two second one-way valves 8; when the crosshead 15 moves from the first hydraulic chamber 16 to the third hydraulic chamber 19, the crosshead 15 pressurizes the hydraulic oil in the third hydraulic chamber 19 and presses the hydraulic oil into the outer oil bag 11 through the second check valve 8; at this time, negative pressure is formed in the first hydraulic cavity 16, and the first check valve 9 can make hydraulic oil in the bidirectional gear pump 2 enter the first hydraulic cavity 16 to supplement oil to the first hydraulic cavity 16; when the crosshead 15 moves from the third hydraulic chamber 19 to the first hydraulic chamber 16, the crosshead 15 pressurizes the hydraulic oil in the first hydraulic chamber 16 and presses the hydraulic oil into the outer oil bag 11 through the first check valve 9; at this time, negative pressure is formed in the third hydraulic chamber 19, and the second check valve 8 can introduce the hydraulic oil in the bidirectional gear pump 2 into the third hydraulic chamber 19 to replenish the third hydraulic chamber 19 with the oil.
The second hydraulic cavity is divided into a fourth hydraulic cavity 17 and a fifth hydraulic cavity 18 by a crosshead 15, the fourth hydraulic cavity 17 and the fifth hydraulic cavity 18 are connected with a reversing slide valve 6, an oil inlet of the reversing slide valve 6 is connected with a bidirectional gear pump 2, and an oil return port is connected with an oil tank by a one-way valve 20 on an oil pipe. The hydraulic oil output by the bidirectional gear pump 2 enters the reversing slide valve 6, the hydraulic oil of the reversing slide valve 6 enters the fourth hydraulic cavity 17, the crosshead 15 is driven to move towards the fifth hydraulic cavity 18, the volume of the fifth hydraulic cavity 18 is reduced, the hydraulic oil in the fifth hydraulic cavity is pressed into the reversing slide valve 6, and the hydraulic oil is pressed into an oil tank through the reversing slide valve 6 and a check valve 20 on an oil pipe. After the reversing slide valve 6 is reversed, the hydraulic oil output by the bidirectional gear pump 2 enters the reversing slide valve 6, the hydraulic oil of the reversing slide valve 6 enters the fifth hydraulic cavity 18 to drive the crosshead 15 to move towards the fourth hydraulic cavity 17, the volume of the fourth hydraulic cavity 17 is reduced, the hydraulic oil in the fourth hydraulic cavity is pressed into the reversing slide valve 6 and is pressed into an oil tank through the reversing slide valve 6 and the check valve 20 on an oil pipe.
Further, an overflow valve 13 is arranged between the oil outlet of the outer oil bag 11 and the oil inlet of the inner oil bag 1, the working pressure of the overflow valve 13 is 60MPa, the whole oil way is protected, and damage to a hydraulic element caused by overlarge oil way pressure is prevented.
Further, a damping hole 12 is further arranged between the electromagnetic valve 10 and an oil outlet of the bidirectional gear pump 2, and the damping hole 12 is arranged in the submergence loop and used for system flow, so that instantaneous impact is prevented, and damage to hydraulic elements is prevented.
Further, the oil outlet of the inner oil bag 1 is connected with a control device, the control device comprises an amplifier 4 connected with the oil outlet of the inner oil bag 1, the amplifier 4 is connected with the servo motor 3 through an encoder 5, the encoder 5 can detect the rotating speed of the servo motor 3 and send a signal to the amplifier 4, the amplifier 4 controls the rotating speed of the servo motor 3 to control the oil way to adjust the speed, and then the floating and submerging speeds of the section buoy are controlled.
Further, the control of the reversing operation of the reversing spool 6 is controlled by a control device, and by providing a magnetostrictive displacement sensor 21 or an ultrasonic displacement sensor in each of the first hydraulic chamber 16 and the third hydraulic chamber 19, in this embodiment, the magnetostrictive displacement sensor 21 is adopted, the magnetostrictive displacement sensor 21 is installed in each of the first hydraulic chamber 16 and the third hydraulic chamber 19, and the amplifier 4 receives a signal from the magnetostrictive displacement sensor 21 and controls the reversing spool 6 to reverse.
Further, still be equipped with the linear displacement sensor 14 that detects interior oil bag 1 fluid volume in the oil bag 1 outside, interior oil bag 1 is the bellows form, linear displacement sensor 14 can detect the fluid volume of interior oil bag 1 through the length that detects interior oil bag 1 bellows, linear displacement sensor 14 links to each other with amplifier 4, handle and receive interior oil bag 1's volume signal, control servo motor 3 rotational speed regulation volume between interior oil bag 1 and the outer oil bag 11, realize buoyancy change, and then control section buoy come up the float and dive.
The working stage of the hydraulic system is mainly divided into three stages, namely a floating stage, a hovering stage and a submerging stage.
As shown in fig. 4, in the floating stage, the servo motor 3 rotates forward to drive the bidirectional gear pump 2 to rotate, the oil in the inner oil bag 1 enters the bidirectional gear pump 2, enters the reversing slide valve 6 through the bidirectional gear pump 2, enters the fourth hydraulic cavity 17 through the reversing slide valve 6, the pressure of the oil in the fourth hydraulic cavity 17 is increased to drive the cross slide block 15 to move towards the fifth hydraulic cavity 18, the volume of the fifth hydraulic cavity 18 is reduced, the pressure is increased, and the hydraulic oil enters the oil tank through the reversing slide valve 6 and the check valve 20 on the oil path. When the crosshead 15 moves to the fifth hydraulic chamber 18, negative pressure is formed in the first hydraulic chamber 16, meanwhile, the pressure in the third hydraulic chamber 19 increases, the hydraulic oil output by the bidirectional gear pump 2 enters the first hydraulic chamber 16 through the first check valve 9, the hydraulic oil in the third hydraulic chamber 19 is pressed into the outer oil bag 11 through the second check valve 8, when the crosshead 15 moves to the rightmost end in the third hydraulic chamber 19, the magnetostrictive displacement sensor 21 positioned in the third hydraulic chamber 19 sends a signal to the amplifier 4, the amplifier 4 receives and processes the signal, the reversing slide valve 6 is controlled to reverse, so that the hydraulic oil output by the bidirectional gear pump 2 enters the reversing slide valve 6 and then enters the fifth hydraulic chamber 18, the pressure in the fifth hydraulic chamber 18 increases, the crosshead 15 is driven to move to the fourth hydraulic chamber 17, the volume in the fourth hydraulic chamber 17 decreases, the pressure increases, and the hydraulic oil is pressed into the outer oil bag 11 through the first check valve 9, with this circulation, continuously carry out the pressure boost with the low pressure hydraulic oil of interior oil pocket 1 hydraulic oil through two-way gear pump 2 output, the pressure boost is input to outer oil pocket 11 to 6 times of low pressure oil pressure, and outer oil pocket 11 fluid volume increase, buoyancy increase, section buoy realize the come-up, can impress low pressure oil easily in outer oil pocket 11 from this, effectively solve the not enough problem of plunger pump self priming force.
As shown in fig. 4, in the submergence stage, the servo motor 3 rotates reversely to drive the bidirectional gear pump 2 to rotate, the electromagnetic valve 10 is opened, hydraulic oil in the outer oil bag 11 enters the bidirectional gear pump 2 through the electromagnetic valve 10 and the damping hole 12, and then enters the inner oil bag 1 through the bidirectional gear pump 2, the oil volume of the inner oil bag 1 is increased, the volume of the outer oil bag 11 is reduced, the buoyancy is reduced, and the section buoy begins to submerge.
In the hovering stage, before submergence, a hovering depth is preset in the control device, the control device calculates the volume of the corresponding inner oil bag 1 in the hovering depth, in the submergence process, the linear displacement sensor 14 detects the volume of the inner oil bag 1 in real time, when the preset volume is reached, the linear displacement sensor 14 sends a signal to the amplifier 4, the amplifier 4 controls the servo motor 3 to be powered off, the electromagnetic valve 10 is powered off, and the section buoy hovers at the hovering depth.
The above-mentioned specific embodiments can not be regarded as the restriction to the scope of protection of the utility model, to technical personnel in this technical field, it is right the utility model discloses any replacement improvement or transform that embodiment made all fall within the scope of protection of the utility model.
The parts of the present invention not described in detail are the known techniques of those skilled in the art.
Claims (10)
1. The deep sea buoy hydraulic system is characterized in that: the oil outlet of the inner oil bag is connected with a bidirectional gear pump, the bidirectional gear pump is driven by a servo motor, the bidirectional gear pump is respectively connected with an oil tank and an oil inlet of an outer oil bag through a pressurizing unit, and the oil outlet of the outer oil bag is connected with the bidirectional gear pump to form a closed hydraulic oil circuit.
2. The deep sea buoy hydraulic system as claimed in claim 1, wherein: the pressurizing unit comprises a reversing unit and a double-acting pressurizing cylinder which are respectively connected with the bidirectional gear pump, the reversing unit is connected with the double-acting pressurizing cylinder, and an oil outlet of the double-acting pressurizing cylinder is connected with an oil inlet of the outer oil bag.
3. The deep sea buoy hydraulic system as claimed in claim 2, wherein: the reversing unit is a reversing slide valve, an oil inlet of the reversing slide valve is connected with the bidirectional gear pump, and an oil outlet of the reversing slide valve is connected with the double-acting pressure cylinder.
4. The deep sea buoy hydraulic system of claim 3, wherein: the double-acting pressure cylinder is sequentially provided with a first hydraulic cavity, a second hydraulic cavity and a third hydraulic cavity from one end to the other end at intervals, the sectional area of the second hydraulic cavity is larger than that of the first hydraulic cavity and that of the third hydraulic cavity, the structure and the sectional area of the first hydraulic cavity are the same as those of the third hydraulic cavity, cross sliders are movably mounted in the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity and penetrate through the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity to enable the first hydraulic cavity, the second hydraulic cavity and the third hydraulic cavity to move in two directions;
the second hydraulic cavity is divided into a fourth hydraulic cavity and a fifth hydraulic cavity by a crosshead shoe, the fourth hydraulic cavity and the fifth hydraulic cavity are connected with a reversing slide valve, an oil inlet of the reversing slide valve is connected with a bidirectional gear pump, and an oil return port is connected with an oil tank through a one-way valve on an oil pipe;
the first hydraulic cavity is connected with the bidirectional gear pump and the outer oil bag through two first one-way valves respectively, and the third hydraulic cavity is connected with the bidirectional gear pump and the outer oil bag through two second one-way valves respectively.
5. The deep sea buoy hydraulic system as claimed in claim 1, wherein: an overflow valve is arranged between the oil outlet of the outer oil bag and the oil inlet of the inner oil bag.
6. The deep sea buoy hydraulic system as claimed in claim 1, wherein: and an electromagnetic valve or a pressure switch is arranged between the oil outlet of the outer oil bag and the bidirectional gear pump.
7. The deep sea buoy hydraulic system as claimed in claim 6, wherein: and a damping hole is also arranged between the electromagnetic valve and the oil outlet of the bidirectional gear pump.
8. The deep sea buoy hydraulic system as claimed in claim 1, wherein: the oil outlet of the inner oil bag is also connected with a control device, and the control device is connected with a servo motor.
9. The deep sea buoy hydraulic system of claim 8, wherein: the control device comprises an amplifier connected with an oil outlet of the inner oil bag, and the amplifier is also connected with the servo motor through an encoder.
10. The deep sea buoy hydraulic system as claimed in claim 4, wherein: and magnetostrictive displacement sensors are respectively arranged in the first hydraulic cavity and the third hydraulic cavity, the magnetostrictive displacement sensors are connected with an amplifier, and the amplifier controls the reversing slide valve to act.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920004482.6U CN209818410U (en) | 2019-01-02 | 2019-01-02 | Deep sea buoy hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920004482.6U CN209818410U (en) | 2019-01-02 | 2019-01-02 | Deep sea buoy hydraulic system |
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| CN209818410U true CN209818410U (en) | 2019-12-20 |
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| CN201920004482.6U Active CN209818410U (en) | 2019-01-02 | 2019-01-02 | Deep sea buoy hydraulic system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109578347A (en) * | 2019-01-02 | 2019-04-05 | 山东大学 | A kind of deep ocean buoy hydraulic system |
| CN111505985A (en) * | 2020-04-23 | 2020-08-07 | 杭州浅海科技有限责任公司 | Power module of efficient ocean profile measuring instrument |
| CN109578347B (en) * | 2019-01-02 | 2024-04-19 | 山东大学 | Deep sea buoy hydraulic system |
-
2019
- 2019-01-02 CN CN201920004482.6U patent/CN209818410U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109578347A (en) * | 2019-01-02 | 2019-04-05 | 山东大学 | A kind of deep ocean buoy hydraulic system |
| CN109578347B (en) * | 2019-01-02 | 2024-04-19 | 山东大学 | Deep sea buoy hydraulic system |
| CN111505985A (en) * | 2020-04-23 | 2020-08-07 | 杭州浅海科技有限责任公司 | Power module of efficient ocean profile measuring instrument |
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