CN211810092U

CN211810092U - Mechanical timing release device applied in full sea depth

Info

Publication number: CN211810092U
Application number: CN202020327986.4U
Authority: CN
Inventors: 夏雪; 陈兴山; 王林; 张莹莹; 高平; 王培强
Original assignee: Shandong Top Hydraulic & Pneumatic Co ltd
Current assignee: Shandong Top Hydraulic & Pneumatic Co ltd
Priority date: 2020-03-16
Filing date: 2020-03-16
Publication date: 2020-10-30
Anticipated expiration: 2030-03-16

Abstract

The utility model discloses a mechanical timing release who uses at full sea depth, including unhook mechanism, power unit and withstand voltage cabin, power unit is sealed to be set up in withstand voltage under-deck, wherein, unhook mechanism includes: the eccentric shaft comprises an eccentric section and two basic shaft sections positioned at two ends of the eccentric section; a pin shaft; and a certain part of the hook deviating from the first pin shaft hole can be lapped on the top of the eccentric section of the eccentric shaft. The mechanical timing release device applied in the full sea depth has small volume and weight, reduces the total weight of the detection equipment, and improves the working reliability of the detection equipment. And part of the side wall of the pressure-resistant cabin is composed of the elastic compensation diaphragm, the pressure-resistant cabin is filled with insulating oil, and then the pressure in the pressure-resistant cabin can be regulated and balanced through the deformation of the elastic compensation diaphragm, so that the pressure difference between the inside and the outside of the pressure-resistant cabin is reduced, the pressure-resistant capability of the pressure-resistant cabin is improved, and the water tightness of the release device is ensured.

Description

Mechanical timing release device applied in full sea depth

Technical Field

The utility model relates to a mechanical timing release who uses at full sea depth belongs to the general technical field of marine survey.

Background

During the exploration, research and development of marine mineral resources, detection equipment needs to be submerged into the marine environment to complete various detection tasks. The detection equipment needs to be recovered to the sea surface after detection work is completed, the counter weight on the detection equipment is thrown off during recovery, the weight of the detection equipment is reduced after the counter weight is thrown off, the detection equipment can float out of the sea surface by using the buoyancy facility, then the detection equipment sends a position signal to a sea surface ship, the sea surface ship searches the detection equipment according to the position signal and salvages and recovers the detection equipment, and a mechanical device which regularly throws off the counter weight on the detection equipment is a mechanical timing release device. At present, the volume and the weight of a domestic mechanical timing release device applied to deep sea are generally large, on one hand, the total weight of the detection equipment can be increased, on the other hand, under the condition that the total bearing capacity of the detection equipment is limited, the volume and the weight of the release device can be increased, the weight of the detection equipment bearing a balance weight can be reduced, the operation flexibility of the detection equipment in the submergence and recovery process can be reduced under the comprehensive effect of the two aspects, and the failure of the equipment is easily caused. In addition, most of the existing releasing devices adopt a dry sealing structure, and the pressure generated by the working water depth completely acts on the sealing shell and the transmission shaft, so that the counterweight capable of being loaded is limited, and the capability of bearing the counterweight of the detection equipment is limited. Thirdly, the existing release device has poor water tightness, and is easy to seep water in deep sea to cause failure, so that the phenomenon of equipment failure frequently occurs.

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

An object of the utility model is to solve the problem that prior art exists, provide a mechanical timing release who uses in the deep full sea, volume and weight are little, have pressure automatic compensation function moreover, can bear the deep pressure in full sea, and operational reliability is high.

The utility model discloses an adopt following technical scheme to realize above-mentioned purpose:

a mechanical timing release device applied in full sea depth comprises a unhooking mechanism, a power mechanism and a pressure-resistant cabin, wherein the power mechanism is arranged in the pressure-resistant cabin in a sealing mode, and the unhooking mechanism comprises:

the eccentric shaft comprises an eccentric section and two basic shaft sections positioned at two ends of the eccentric section, the axes of the two basic shaft sections are overlapped, the axis of the eccentric section deviates from the axes of the two basic shaft sections, and the power mechanism is in transmission connection with one of the basic shaft sections and is used for driving the eccentric shaft to make rotary motion around the axial direction of the basic shaft section;

the pin shaft is directly or indirectly fixed on the pressure-resistant cabin;

the hook is provided with a first pin shaft hole, the pin shaft penetrates through the first pin shaft hole, a certain part of the hook, which deviates from the first pin shaft hole, can be lapped on the top of the eccentric section of the eccentric shaft, and the eccentric shaft rotates around the axis of the base shaft section so that the hook and the eccentric section are removed from a lapping state;

the flange plate is provided with a first mounting hole, the end part of the eccentric shaft is rotatably supported in the first mounting hole on the flange plate, and the flange plate is directly or indirectly fixed on the pressure-resistant cabin.

In order to ensure that the hook can be disengaged from the support of the eccentric section, the straight-line distance between the center of the pin shaft hole and the farthest point on the hook should be smaller than the farthest straight-line distance between the center of the pin shaft hole and the eccentric section.

In a preferred embodiment, the number of the flanges is two, the two base shaft sections are respectively rotatably supported in the first mounting holes of the two flanges, a distance rod is arranged between the two flanges to prevent the two flanges from approaching along the axial direction of the eccentric shaft, and the hook is arranged between the two flanges.

In a preferred embodiment, a second pin shaft hole is formed in the flange plate, and the pin shaft penetrates through the second pin shaft hole in the flange plate.

In a preferred embodiment, at least a part of the surface of the eccentric section is lower than the surface of the base shaft section at both ends to form an inner concave part for the hook to overlap, and the stability of the hook and the eccentric shaft in the overlapping state can be further improved when the surface of the inner concave part is arranged to be a plane.

In a preferred embodiment, the first mounting hole and the second pin shaft hole are arranged near the bottom of the flange, and the bottom of the flange is provided with a notch which is at least partially positioned between the first mounting hole and the second pin shaft hole. The arrangement of the gap enables the hook to be exposed outside the flange plate, and the rope for hanging the balance weight is conveniently hung on the hook and then the hook is lapped on the eccentric section.

In a preferred embodiment, the hook is an arc-shaped structure with a smooth surface, so that the rope can be conveniently separated from the hook.

In a preferred embodiment, the pressure-resistant chamber comprises a chamber body with two ports, one port of the chamber body is sealed and sealed by a first end cap, the other port of the chamber body is sealed and sealed by an elastic compensation membrane, and the chamber body is filled with insulating oil, usually silicone oil, which has the characteristics of stable chemical properties and good electrical insulation.

In a preferred embodiment, a second end cover is disposed outside the elastic compensation diaphragm, the second end cover compresses and seals the elastic compensation diaphragm and the port of the cabin, the second end cover also plays a role in protecting the elastic compensation diaphragm, and a water pressure balance hole is formed in the second end cover and used for communicating with fluid outside the cabin.

Further, the cabin body is provided with a signal transmission hole for leading out a signal wire for signal transmission.

In a preferred embodiment, the elastic compensation diaphragm is convex towards the outer side of the cabin; furthermore, a sealing ring is arranged on the edge of the inner surface of the elastic compensation membrane.

In a preferred embodiment, one of the base shaft sections of the eccentric shaft is in transmission connection with the output shaft of the power mechanism through a transition shaft, the first end cover is provided with a second mounting hole, the first end cover is in sealing connection with the cabin body through a neck flange, the neck flange comprises a radial pipe and a disk body arranged on the periphery of the radial pipe, and the transition shaft is rotatably supported in the second mounting hole and the radial pipe through a first bearing and a second bearing.

Furthermore, the transition shaft penetrates through the second mounting hole and is fixedly connected with the base shaft section of the eccentric shaft, and the other end of the transition shaft is fixedly connected with the output shaft of the power mechanism; and sealing rings are arranged on the contact surfaces of the transition shaft and the second mounting hole and on the contact surfaces of the neck flange, the inner wall of the cabin body and the inner wall of the first end cover, so that the water tightness of the cabin body is ensured.

The mechanical timing release device applied in full sea depth also comprises a fixed frame for mounting the cabin body on the detection equipment.

Benefits of the present application include, but are not limited to:

(1) the application provides a mechanical timing release at full sea depth application, whole volume and weight are little, have reduced the gross weight of detecting equipment, have improved detecting equipment's operational reliability.

(2) The application provides a mechanical timing release at full sea depth application, the partial lateral wall of withstand voltage cabin comprises the elastic compensation diaphragm, and the pressure in the withstand voltage cabin is adjusted to the deformation of accessible elastic compensation diaphragm after being full of insulating oil in the withstand voltage cabin, has reduced the pressure differential inside and outside the withstand voltage cabin, has improved the withstand voltage ability in withstand voltage cabin, has guaranteed release's water proofness, has improved release's operational reliability.

(3) The application provides a mechanical timing release at full sea depth application, withstand voltage under-deck is full of insulating oil, makes power mechanism and unhook mechanism's main dynamic seal position form wet-type seal, has improved the leakproofness of withstand voltage under-deck in the deep sea environment, is full of insulating oil in the withstand voltage under-deck moreover and makes the dynamic seal portion reach self-lubricating effect.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the application and together with the description serve to explain the application and not to limit the application. In the drawings:

FIG. 1 is a schematic cross-sectional view of a mechanical timed release device for use at full sea depth to which the present application relates;

FIG. 2 is a schematic perspective view of a mechanical timed release device for use at full sea depth in accordance with the present application;

FIG. 3 is a schematic cross-sectional view of a release mechanism in a mechanical timed release for full-sea applications to which the present application relates;

FIG. 4 is a schematic view of a first state of operation of the unhooking mechanism of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 5 is a schematic view of a second state of operation of the unhooking mechanism of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 6 is a schematic view of a third operating condition of the release mechanism of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 7 is a simplified schematic illustration of the installation of a mechanical timed release for full-sea applications to which the present application relates;

FIG. 8 is a schematic view of the construction of the flange of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 9 is a schematic view of the hook structure of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 10 is a schematic illustration of the construction of the eccentric shaft of the mechanical timed release for full-sea applications to which the present application relates;

FIG. 11 is a schematic view of a transition shaft of the mechanical timed release apparatus for full-sea applications to which the present application relates;

FIG. 12 is a schematic illustration of the construction of a first end cap in the mechanical timed release for full-sea applications to which the present application relates;

FIG. 13 is a schematic structural view of a necked flange in a mechanical timed release for full sea depth applications to which the present application relates;

FIG. 14 is a schematic perspective view of another angle of a mechanical timed release device for use at full sea depth to which the present application relates;

in the figure, 100, a pressure-resistant cabin; 110. a cabin body; 111. a signal transmission hole; 112. a watertight connector; 120. A first end cap; 121. a second mounting hole; 130. an elastic compensation diaphragm; 140. a second end cap; 141. a water pressure balancing hole; 150. a necked-in flange; 160. a fixed mount;

200. an eccentric shaft; 201. an eccentric section; 202. a basal shaft section;

300. a pin shaft; 301. a hexagon socket head cap screw;

400. hooking; 401. a first pin shaft hole;

501. a first mounting hole; 502. a distance rod hole; 503. a second pin shaft hole; 504. a notch; 510. a first flange plate; 520. a second flange plate; 530. a distance rod;

610. a rope; 620. balancing weight;

700. a reduction motor;

800. a transition shaft; 801. a first bearing; 802. a second bearing; 803. a shaft shoulder;

910. a seal ring; 920. sealing the groove.

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 in combination with the accompanying drawings.

It should be noted that in the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those described herein. Accordingly, the scope of the present invention is not limited by the specific embodiments disclosed below.

As shown in fig. 1 to fig. 3, the mechanical timing releasing device for full-sea deep application provided by the present application includes a decoupling mechanism, a power mechanism and a pressure-resistant cabin 100, wherein the power mechanism is hermetically disposed in the pressure-resistant cabin 100, and the decoupling mechanism includes:

the eccentric shaft 200 comprises an eccentric section 201 and two base shaft sections 202 positioned at two ends of the eccentric section 201, the axes of the two base shaft sections 202 are overlapped, the axis of the eccentric section 201 deviates from the axes of the two base shaft sections 202, and a power mechanism is in transmission connection with one base shaft section 202 and is used for driving the eccentric shaft 200 to make rotary motion around the axial direction of the base shaft section 202;

the pin shaft 300 is directly or indirectly fixed on the pressure-resistant cabin 100;

the hook 400 is provided with a first pin shaft hole 401, the pin shaft 300 penetrates through the first pin shaft hole 401, a certain part of the hook 400 deviating from the first pin shaft hole 401 can be lapped on the top of the eccentric section 201 of the eccentric shaft 200, and the eccentric shaft 200 rotates around the axis of the base shaft section 202 to enable the hook 400 and the eccentric section 201 to be in a lap joint state;

and the plate-shaped flange plate is provided with a first mounting hole 501, the end part of the eccentric shaft 200 is rotatably supported in the first mounting hole 501 on the flange plate, and the flange plate is directly or indirectly fixed on the pressure-resistant cabin 100. Further, the number of the flanges is two, which are denoted as a first flange 510 and a second flange 520, and the two base shaft sections 202 are respectively rotatably supported in the first mounting holes 501 of the first flange 510 and the second flange 520.

As shown in fig. 4, in the above structure, one end of the hook 400 is pivotally connected to the pin 300, and the other end thereof overlaps the eccentric section 201. The power mechanism is generally a speed reducing motor 700, the motor is provided with a brake module, the motor is powered off to brake, the eccentric shaft 200 cannot rotate, so that after the counterweight 620 is hung on the hook 400 through the rope 610, the hook 400 is tightly pressed on the eccentric section 201 under the gravity action of the counterweight 620 to prevent unhooking, and the detection device can perform detection work in potential water. As shown in fig. 5 and 6, when the released counterweight 620 floats upwards after the detection operation is completed, the motor is controlled to operate at a preset timing through a preset program, the eccentric shaft 200 is driven to perform a rotary motion around the axial direction of the base shaft section 202, the eccentric shaft 200 enables the eccentric section 201 to be far away from the hook 400 in the rotating process, the hook 400 loses the support of the eccentric section 201 and then rotates downwards, so that the rope 610 is separated from the hook 400, and the counterweight 620 is released.

As shown in FIG. 10, the eccentric shaft 200 and the base shaft section 202 are each generally cylindrical in configuration and are of similar thickness, integrally formed, and bow-like shape.

Further, at least a part of the surface of the eccentric section 201 is lower than the surface of the base shaft section 202 at both ends to form an inner concave portion for overlapping the hook 400, and the stability of the overlapping state of the hook 400 and the eccentric shaft 200 can be further improved when the surface of the inner concave portion is arranged to be a plane.

To ensure that the hook 400 is free from the support of the eccentric section 201, the linear distance between the center of the hole of the pin 300 and the farthest point on the hook 400 should be smaller than the farthest linear distance between the center of the hole of the pin 300 and the eccentric section 201.

Generally, the axis of the pin shaft 300 is disposed parallel to the axis of the base shaft section 202 of the eccentric shaft 200 in view of ease of manufacturing and installation.

The first flange 510 and the second flange 520 may be provided with a certain number of through holes, which not only ensures mechanical properties, but also reduces weight.

Further, referring again to fig. 1, a distance rod 530 is provided between the first flange 510 and the second flange 520 to prevent the first flange 510 and the second flange 520 from approaching in the axial direction of the eccentric shaft 200. The hook 400 is located between the first flange 510 and the second flange 520, and a large gap is left between the first flange 510 and the second flange 520 to facilitate the hook 400 to rotate around the pin shaft 300.

Further, two ends of the distance rod 530 are respectively fixed on the first flange 510 and the second flange 520; specifically, distance rod holes 502 are formed in the first flange plate 510 and the second flange plate 520, the distance rod holes 502 are stepped holes, threaded holes are formed in the ends of the distance rods 530, and after the ends of the distance rods 530 extend into the distance rod holes 502, the hexagon socket head cap screws 301 are screwed into the threaded holes in the ends of the distance rods 530, so that the hexagon socket head cap screws 301 are clamped on the step surfaces of the distance rod holes 502, and the distance rods 530 can be connected with the flange plates.

Further, the number of the distance rods 530 is at least one, and three in the illustration of the present application.

Further, referring to fig. 8, a second pin hole 503 is provided on the flange, and the pin 300 passes through the second pin hole 503 on the flange. Similarly, the second pin shaft hole 503 is a stepped hole, a threaded hole is formed in the end portion of the pin shaft 300, and after the end portion of the pin shaft 300 extends into the second pin shaft hole 503, the hexagon socket head cap screw 301 is screwed into the threaded hole in the end portion of the pin shaft 300, so that the hexagon socket head cap screw 301 is clamped on the stepped surface of the second pin shaft hole 503, and the pin shaft 300 and the flange plate can be connected.

Further, the first mounting hole 501 and the second pin hole 503 are disposed near the bottom of the flange, and the bottom of the flange is provided with a notch 504, and the notch 504 is at least partially located between the first mounting hole 501 and the second pin hole 503. The gap 504 exposes the hook 400 out of the flange, which facilitates hanging the rope 610 of the hanging weight 620 on the hook 400 and then connecting the hook 400 on the eccentric section 201.

Typically, the flange is semi-circular, and the first mounting hole 501 and the second pin hole 503 are disposed near the straight edges of the semi-circle.

Further, referring to fig. 9, the hook 400 is an arc-shaped structure with a smooth surface to facilitate the rope 610 to be separated from the hook 400, and the hook 400 is generally shaped like an S.

Further, the pressure-resistant chamber 100 includes a chamber body 110 having two ports, the chamber body 110 is cylindrical, one port of the chamber body 110 is sealed and sealed by a first end cap 120, the other port is sealed and sealed by an elastic compensation membrane 130, and the chamber body 110 is filled with insulating oil, usually silicone oil, which has the characteristics of stable chemical properties and good electrical insulation. The pin 300 may be fixed to the first end cap 120.

Further, a second end cap 140 is disposed outside the elastic compensation diaphragm 130, the second end cap 140 compresses and seals the elastic compensation diaphragm 130 and the port of the cabin 110, the second end cap 140 also plays a role of protecting the elastic compensation diaphragm 130, and the second end cap 140 is provided with a water pressure balance hole 141 for communicating with fluid outside the cabin 110. After the release device enters the measurement environment along with the detection equipment, seawater acts on the elastic compensation diaphragm 130 through the water pressure balance hole 141 on the second end cover 140.

Furthermore, the elastic compensation diaphragm 130 protrudes to the outer side of the cabin body 110, the elastic compensation diaphragm 130 is made of a corrosion-resistant non-metallic material, and is usually made of nitrile rubber, the shore a hardness is not more than 60, the tensile length is less than 20mm, and the elongation at break is not less than 300%.

Referring to fig. 1 again, the cabin 110 is further provided with a signal transmission hole 111 for leading out a signal line for signal transmission, the signal line is connected with a watertight connector 112 when being led out, and the watertight connector 112 has an ultra-strong sealing effect and can be applied in the whole sea depth range.

The signal transmission hole 111 is used for filling silicon oil into the pressure resistant cabin 100 under normal pressure to exhaust gas in the pressure resistant cabin 100, and after the oil filling is completed, the signal wire is hermetically led out through the watertight connector 112.

When the pressures on the two sides of the elastic compensation diaphragm 130 are unbalanced, the internal and external pressure difference of the cabin 110 is reduced by the self deformation of the elastic compensation diaphragm 130, the pressure bearing capacity of the cabin 110 is improved, and the water seepage of the cabin 110 is prevented. For example, when the external seawater pressure is greater than the pressure of the silicone oil in the cabin 110, the elastic compensation diaphragm 130 will move toward the inside of the cabin 110, so that the volume compression pressure of the silicone oil is increased, the pressure difference between the inside and the outside of the cabin 110 is reduced, and the pressure-resistant cabin is filled with the insulating oil to make the self-lubricating effect of the dynamic seal part.

Referring again to fig. 1, further, one of the base shaft segments 202 of the eccentric shaft 200 is drivingly connected to the output shaft of the power mechanism through a transition shaft 800. Referring to fig. 12, the first end cap 120 is provided with a second mounting hole 121, and the first end cap 120 and the cabin 110 are hermetically connected through a neck flange 150. The neck flange 150 comprises a diameter pipe and a disc body arranged on the periphery of the diameter pipe, the transition shaft 800 is rotatably supported in the second mounting hole 121 and the diameter pipe through a first bearing 801 and a second bearing 802, and an inner shoulder for positioning the speed reduction motor is further arranged in the diameter pipe of the neck flange 150. Referring to fig. 13 and 14, the neck flange 150, the cabin body 110, and the first end cap 120 are connected by bolts, the neck flange 150, the cabin body 110, and the first end cap 120 are all provided with connecting holes, the neck flange 150 and the first end cap 120 are provided with through holes, and the cabin body 110 is provided with blind threaded holes.

The transition shaft 800 penetrates through the second mounting hole 121 and is fixedly connected with the base shaft section 202 of the eccentric shaft 200, and the other end of the transition shaft is fixedly connected with the output shaft of the speed reducing motor 700; sealing rings 910 are arranged on the contact surfaces of the transition shaft 800 and the second mounting hole 121, the neck flange 150 and the inner wall of the cabin body 110, and the contact surfaces of the neck flange 150 and the inner wall of the first end cap 120, a sealing ring 910 is also arranged on the edge of the inner surface of the elastic compensation diaphragm 130, a sealing groove 920 is arranged on the contact surface provided with the sealing ring 910, the sealing ring 910 is hermetically embedded in the sealing groove 920 to ensure the water tightness of the cabin body 110, and generally, an O-shaped sealing ring can be selected as the sealing ring 910.

Referring to fig. 11, a shaft shoulder 803 is generally disposed on the transition shaft 800, the transition shaft 800 on both sides of the shaft shoulder 803 is rotatably supported in the second mounting hole 121 and the bore pipe through the first bearing 801 and the second bearing 802, respectively, and both the second mounting hole 121 and the bore pipe inner hole are stepped holes to axially position the transition shaft 800. Generally, the transition shaft 800 is keyed or pinned to the base shaft segment 202.

Further, referring to fig. 1, 2 and 7, the mechanical timing releasing device for full-sea application further includes a fixing frame 160 for mounting the cabin 110 on the detection device, the fixing frame 160 is composed of two fixing plates, the two fixing plates are connected into an L shape, and one of the fixing plates has a through hole capable of being sleeved on the periphery of the first end cap 120.

In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present invention.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; the connection can be mechanical connection, electrical connection or communication; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

The above-mentioned specific embodiments can not be regarded as the restriction to the protection scope of the present invention, to the technical personnel in this technical field, it is right that any replacement improvement or transformation that the embodiment of the present invention made all fall within the protection scope 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

1. The utility model provides a machinery timing release at full sea depth application which characterized in that, includes unhook mechanism, power unit and withstand voltage cabin, power unit seal sets up in withstand voltage cabin, wherein, unhook mechanism includes:

the pin shaft is directly or indirectly fixed on the pressure-resistant cabin;

2. The mechanical timing release device for full-sea applications as claimed in claim 1, wherein the number of the flanges is two, the two base shaft sections are rotatably supported in the first mounting holes of the two flanges, respectively, and a distance rod is disposed between the two flanges to prevent the two flanges from approaching in the axial direction of the eccentric shaft.

3. The mechanical timing release device for full-sea-depth applications as claimed in claim 1 or 2, wherein the flange is provided with a second pin shaft hole, and the pin shaft penetrates through the second pin shaft hole on the flange.

4. The mechanical timed release device for full-sea applications according to claim 1, characterized in that at least part of the surface of the eccentric section is lower than the base shaft section surface at both ends, so as to form an internal recess for the hook to overlap.

5. The mechanical timing release device for use at full sea depths of claim 3, wherein the first mounting hole and the second pin hole are disposed proximate a bottom of the flange, the bottom of the flange being provided with a notch, the notch being at least partially located between the first mounting hole and the second pin hole.

6. The mechanical timed release device for full-sea applications according to claim 1, characterized in that the hook is an arc-like structure with smooth surface.

7. The mechanical timed release device for full-sea applications according to claim 1, wherein the pressure-resistant chamber comprises a chamber body with two ports, one of the ports of the chamber body is sealed and sealed by the first end cap, the other port is sealed and sealed by an elastic compensation diaphragm, and the chamber body can be filled with insulating oil.

8. The mechanical timing release device for full-sea deep application of claim 7, wherein a second end cap is disposed outside the elastic compensation diaphragm, the second end cap tightly seals the elastic compensation diaphragm with the port of the cabin, and a hydraulic pressure balance hole is formed on the second end cap.

9. Mechanical timed release device for full sea applications according to claim 7, characterised in that the elastic compensation diaphragm is convex towards the outside of the nacelle.

10. The mechanical timing release device for full-sea deep application of claim 7, wherein one of the basic shaft sections of the eccentric shaft is in transmission connection with the output shaft of the power mechanism through a transition shaft, the first end cover is provided with a second mounting hole, the first end cover is in sealing connection with the cabin body through a neck flange, the neck flange comprises a radial pipe and a disk body arranged on the periphery of the radial pipe, and the transition shaft is rotatably supported in the second mounting hole and the radial pipe through a first bearing and a second bearing.