阅读说明：本技术 一种变阻尼的二级火工液压阻尼推力筒 (Variable-damping two-stage hydraulic damping thrust cylinder for firer ) 是由 邓飞 龙军 杨涛 戚鹏 毛义峰 于 2019-10-09 设计创作，主要内容包括：本发明属于火工作动装置领域,具体涉及一种变阻尼的二级火工液压阻尼推力筒,该推力筒包括壳体、一级活塞、液压油、芯级活塞、前封头、挡圈；壳体与一级活塞之间的容腔与一级活塞与芯级活塞之间的容腔装有液压油形成两个储油腔,两个储油腔通过一级活塞上径向设置的过油孔相通。本发明由于采用了径向布置过油孔的方案,利用芯级活塞的外锥面和前封头内锥面对过油孔的遮挡,实现了启动与到位的变阻尼功能,降低了启动及到位冲击,相比于原有针孔阻尼结构,该推力筒结构空间利用率高,有效行程大。(The invention belongs to the field of initiating explosive devices, and particularly relates to a variable-damping two-stage initiating explosive hydraulic damping thrust cylinder which comprises a shell, a primary piston, hydraulic oil, a core-stage piston, a front end enclosure and a check ring; the cavity between the shell and the first-stage piston and the cavity between the first-stage piston and the core-stage piston are filled with hydraulic oil to form two oil storage cavities, and the two oil storage cavities are communicated through oil holes radially arranged on the first-stage piston. The thrust cylinder structure has the advantages that the scheme of radially arranging the oil passing holes is adopted, the outer conical surface of the core-grade piston and the inner conical surface of the front end enclosure are used for shielding the oil passing holes, the variable damping function of starting and in-place is realized, the starting and in-place impact is reduced, and compared with the original pinhole damping structure, the thrust cylinder structure is high in space utilization rate and large in effective stroke.)

1. The utility model provides a become second grade firer hydraulic damping thrust section of thick bamboo of damping which characterized in that: the hydraulic oil pump comprises a shell (1), a primary piston (2), hydraulic oil (3), a core-grade piston (4), a front seal head (5) and a retainer ring (6); the shell (1), the primary piston (2) and the core-stage piston (4) are sequentially nested and then move mutually along the axial direction; an oil storage cavity I is formed by a cavity between the shell (1) and a piston rod of the primary piston (2), an oil storage cavity II is formed by a cavity between the primary piston (2) and the core-stage piston (4), and hydraulic oil (3) is filled in the oil storage cavity I and the oil storage cavity II and is communicated with each other through an oil passing hole (22) radially arranged on the primary piston (2); preceding head (5) are installed at I right-hand member portion in oil storage chamber, and retaining ring (6) are installed at one-level piston (2) right-hand member portion, and the internal surface of the hole of preceding head (5) is the conical surface, and the aperture of hole reduces from left to right gradually, and the frustum surface of core level piston (4) left end is the conical surface, and the external diameter of frustum increases from left to right gradually.

2. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 1, wherein: the sectional area of the oil storage cavity I is equal to that of the oil storage cavity II.

3. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 1, wherein: the primary piston (2) comprises a piston disc (21) and a piston rod (23), an oil passing hole (22) is radially arranged at a position, close to the piston disc (21), on the piston rod (23), and the length-diameter ratio of the oil passing hole is not more than 2/1.

4. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 3, wherein: the outer side of the front seal head (5) is in clearance fit with a piston rod (23) of the primary piston (2).

5. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 4, wherein: the axial length of the conical surface of the inner hole of the front seal head (5) is equal to the distance between the center of the oil passing hole (22) on the primary piston (2) and the right end face of the piston disc (21).

6. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 5, wherein: an O-shaped sealing ring (9) is arranged between the front seal head (5) and the shell (1); an O-shaped sealing ring (8) is arranged between the front seal head (5) and the primary piston (2).

7. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 1, wherein: the core-stage piston (4) comprises a frustum (41) and a piston disc (42), the frustum is connected with the piston disc, and the height of the frustum (41) is equal to the distance between the center of the oil passing hole (22) in the first-stage piston and the right end face of the piston disc (21).

8. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 1, wherein: the shell (1), the first-stage piston (2) and the core-stage piston (4) are in clearance fit.

9. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 8, wherein: the distance of the first-stage piston (2) moving in the shell (1) is less than the distance of the core-stage piston (4) moving in the first-stage piston (2).

10. The variable damping two-stage fire hydraulic damping thrust cylinder according to claim 9, wherein: an O-shaped sealing ring (11) is arranged between the shell (1) and the primary piston (2), and an O-shaped sealing ring (10) is arranged between the core-level piston (4) and the primary piston (2).

11. The variable damping two-stage fire hydraulic damping thrust cylinder as claimed in any one of claims 1 to 10, wherein: the gas generator (7) is arranged on the side of the shell (1) or in the axial direction of the shell (1).

Technical Field

The invention relates to a secondary initiating explosive hydraulic damping thrust cylinder with starting and in-place variable damping, which is suitable for the fields of missile weapons, aerospace and the like which require stable motion process and small starting and in-place impact, such as missile wing unfolding, satellite solar sailboard unfolding and the like.

Background

The firer actuating device can release considerable energy in a very short time by means of gunpowder combustion, and converts the energy into mechanical energy to output work so as to complete a preset program action. Compared with the traditional electric drive, the fire actuator cylinder device has small volume and light weight and is more suitable for the working condition of one-time actuation. With the development of aerospace technology, the application of the method to carrier rockets, artificial satellites and missile weapon systems is more extensive.

The traditional fire actuator cylinder mainly outputs thrust without considering damping. However, under the working conditions of missile wing expansion, satellite load driving or solar sailboard expansion and the like, stable driving is required, the starting and in-place impact is small, and the traditional undamped actuating cylinder cannot meet the requirement. The hydraulic damping utilizes the liquid damping effect to provide resistance to movement, and the hydraulic damping technology is combined with the fire actuator cylinder to solve the problems by consuming the movement energy of an object to play a certain protection role.

At present, the hydraulic damping actuating cylinder for the fire works is applied to the field of aerospace, and the damping structure of the hydraulic damping actuating cylinder is divided into variable damping and constant damping. Because of some working conditions such as missile wing expansion, in order to avoid the structural damage caused by too large in-place impact of the missile wing, the required expansion time is short but the in-place speed is low, so a variable damping structure is often adopted.

The common variable damping hydraulic damping actuating cylinder for the fire works adopts a pinhole variable damping structure: the oil passing holes are axially arranged, two sides of each oil passing hole are respectively provided with a sealing piston, and one piston is provided with a blocking needle. When the gas-oil cylinder works, the gas pushes the piston to move, and hydraulic oil is pressed to the other side of the oil passing hole to realize damping action; after the piston moves to a certain position, the blocking needle enters the oil passing hole, and the cross-sectional area of oil passing is reduced to realize variable damping. The pinhole damping structure needs to be provided with an oil storage cavity in the axial direction, so that the pinhole damping structure occupies an axial space, the effective stroke occupation ratio (effective stroke/actuator cylinder body length) of the actuating device is small, the pinhole damping structure is not suitable for a working condition with a large stroke requirement, only in-place variable damping is realized, and the pinhole damping structure is not suitable for a working condition with a strict starting impact requirement.

Traditional non-firer multistage hydraulic damping driving device relies on external oil pump to impress hydraulic oil inside multistage piston in order to realize the function, is widely used in ground equipment or civilian field. However, this method requires an external oil storage chamber and a pressurizing device, and is bulky and heavy, and is not suitable for the aerospace field with high requirements on volume and weight. At present, in the field of domestic initiating explosive devices, the initiating explosive device damping actuating cylinder is generally of a single-stage structure and has a small stroke.

The damping force is related to the moving speed of the piston, and the piston starts to accelerate from a standstill when the actuating cylinder is started, so that the damping in the initial state is small. The gas thrust is high due to violent combustion of gunpowder, but the damping is low at the moment, so that the initial impact is high. In the field of spaceflight, particularly in the displacement driving of a satellite with a precision equipment load, the whole motion is required to have small impact, namely the impact is small when the satellite is started and put in place, and the conventional existing firer damping structure only with the position variable damping is not suitable for the working conditions.

Disclosure of Invention

The technical problem solved by the invention is as follows: aiming at the problems that the effective stroke ratio (stroke/actuator cylinder body) of the existing hydraulic damping actuator cylinder is small, in-place buffering is only carried out, and the requirement of large-stroke low-impact driving cannot be met, the secondary hydraulic damping actuator cylinder with high space utilization rate and large stroke is provided, and the variable damping impact reduction function is carried out on starting and in-place.

The technical scheme for solving the technical problems is as follows:

a variable damping two-stage hydraulic damping thrust cylinder for priming system is disclosed: the hydraulic oil hydraulic pump comprises a shell, a primary piston, hydraulic oil, a core-grade piston, a front end enclosure and a retainer ring; a cavity between the shell and a piston rod of the primary piston is filled with hydraulic oil to form an oil storage cavity I, a cavity between the primary piston and the core-stage piston is filled with hydraulic oil to form an oil storage cavity II, and the two oil storage cavities are communicated through oil holes radially arranged on the primary piston; the front end enclosure is installed at I right-hand member portion in oil storage chamber, the retaining ring is installed at one-level piston right-hand member portion, front end enclosure hole left end and core level piston left end frustum processing have certain tapering, the internal surface of the hole of front end enclosure is the conical surface, the aperture of hole reduces from left to right gradually, the frustum surface of core level piston left end is the conical surface, the external diameter of frustum increases from left to right gradually.

There is certain relation between the casing internal diameter, the internal diameter of one-level piston and the tip external diameter three, promptly: the sectional area of an annular oil storage cavity I formed between the shell and a piston rod of the primary piston is equal to that of an oil storage cavity II.

The distance that the primary piston can move in the housing is less than the distance that the core piston can move in the primary piston. The shell, the primary piston and the core-grade piston are in clearance fit, and can move mutually along the axial direction after being nested in sequence, an O-shaped sealing ring is arranged between the shell and the primary piston, and the O-shaped sealing ring is arranged between the core-grade piston and the primary piston, so that dynamic sealing is realized in the moving process.

The primary piston comprises a piston disc and a piston rod, an oil passing hole is radially arranged at a position close to the piston disc, the length-diameter ratio of the oil passing hole is not more than 2/1, and the influence of liquid viscosity on the flow speed of liquid can be reduced while the structural strength and the processing manufacturability are ensured.

Grooves are uniformly formed in the inner side and the outer side of the front end enclosure and used for installing O-shaped sealing rings, the O-shaped sealing rings are arranged between the front end enclosure and the primary piston, and the O-shaped sealing rings are arranged between the front end enclosure and the shell; the O-shaped sealing ring on the outer side of the front seal head is tightly pressed with the shell to realize static sealing, the O-shaped sealing ring on the inner side of the front seal head is matched with a piston rod of the primary piston to realize dynamic sealing, and meanwhile, the front seal head realizes the limiting of the primary piston; the retainer ring is arranged at the right end part of the first-stage piston to limit the core-stage piston.

The outer side of the front end socket is in clearance fit with a piston rod of the first-stage piston, dynamic sealing is achieved by means of an O-shaped sealing ring during guiding, a conical surface is machined on the inner side, close to the oil storage cavity I, of the front end socket, the large opening faces the oil storage cavity I, the axial length of the conical surface is equal to the distance between the center of the oil passing hole in the first-stage piston and the right end face of the piston disc, the oil passing hole is shielded by the conical surface after entering the conical surface, and the liquid flow speed is gradually reduced so as.

The core-stage piston comprises a frustum and a piston disc, the frustum is machined on one side, close to the oil storage cavity II, of the tail of the core-stage piston, the frustum is connected with the piston disc, and the height of the frustum is equal to the distance between the center of the oil passing hole in the first-stage piston and the right end face of the piston disc. When the actuating cylinder is started, the cone table shields the oil passing hole, so that the flow velocity of liquid is gradually increased to reduce impact during starting.

The two oil storage cavities are filled with hydraulic oil (without bubbles), and the total volume of the hydraulic oil is equal to the maximum value of a containing cavity formed by the shell and the first-stage piston and the minimum value of the containing cavity formed by the first-stage piston and the core-stage piston.

The variable damping secondary hydraulic damping thrust cylinder for the firer further comprises a fuel gas generator, the mounting position of the fuel gas generator is not limited to the radial mounting mode in the figure 1, the fuel gas generator can be arranged on the side surface of the actuating cylinder, and can also be arranged in the axial direction of the actuating cylinder, and fuel gas can be discharged into a power cavity in the shell. When the gas turbine works, the gas pushes the primary piston to move to compress the hydraulic oil in the annular cavity, so that the hydraulic oil enters the primary piston to drive the core-stage piston to realize secondary damping action; when the primary piston is started and in place, the variable damping effect is realized by the change of the shielding degree of the conical surface on the oil passing hole, the oil passing area is changed from small to large when the primary piston is started, and the oil passing area is changed from large to small when the primary piston is in place, so that the starting and in-place impact is reduced.

The working principle of the variable damping secondary hydraulic damping thrust cylinder provided by the invention is as follows: when the damping device works, the gas generator generates gas to push the primary piston to move, the primary piston compresses hydraulic oil in the annular cavity when moving, and the hydraulic oil generates a damping effect through the oil passing hole at the left end of the primary piston so as to enter the primary piston to drive the core-stage piston to realize secondary damping action; when the actuating cylinder is started, the damping force is larger under the shielding effect of the conical surface of the core-level piston, the clearance between the conical surface of the core-level piston and the oil passing hole is larger and larger along with the movement of the primary piston, the shielding effect on the oil passing hole is weaker and weaker, the damping force is gradually reduced, the damping force is reduced from large to small during starting, and the thrust output is changed from small to large so as to realize the impact reduction during starting; due to the incompressible characteristic of liquid, hydraulic oil enters the inside of the first-stage piston and then acts on the core-stage piston to drive the core-stage piston to move, when the actuating cylinder works in place, the oil passing hole is shielded by the conical surface of the front end socket, and the damping force is gradually increased to realize in-place strong buffering.

The left end is referred to herein as the end proximate the gasifier and the right end is referred to as the end distal from the gasifier.

Compared with the prior art, the invention has the beneficial effects that:

(1) the invention provides a two-stage hydraulic damping actuating scheme with high space utilization rate and large effective stroke, which adopts the scheme that the space between a first-stage piston and a shell and the space between the first-stage piston and a core-stage piston are used for storing oil and radially arranging oil passing holes, so that the ratio of the motion stroke of each-stage piston is larger than that of the original pinhole damping structure, and the total stroke output by an actuating cylinder is qualitatively improved compared with the conventional hydraulic damping actuating structure by utilizing the two-stage piston actuation realized by the incompressible characteristic of liquid;

(2) the invention realizes the purpose that the damping is changed from big to small when the engine is started by utilizing the shielding of the outer conical surface of the core-grade piston to the oil passing hole; the shielding of the inner cone surface of the front end socket on the oil passing hole is utilized to realize that the in-place damping is changed from small to large, the starting and in-place impact is reduced, the two-time damping changing effect of starting and in-place greatly reduces the impact of the initiating explosive device on the load during working, and compared with the single damping effect of the existing initiating explosive device damping actuating cylinder, the invention is more suitable for the driving of precision equipment;

(3) the two-stage pistons of the invention move synchronously, the core-stage piston outputs force all the time, and compared with the traditional two-stage piston which has sudden change of thrust force caused by sudden change of gas action area when the first-stage piston moves in place, the invention outputs thrust force uniformly and stably in the whole working process.

Drawings

FIG. 1 is a schematic structure diagram of a two-stage hydraulic damping thrust cylinder provided by the invention;

FIG. 2 is a schematic structure diagram of the working in-place state of the two-stage hydraulic damping thrust cylinder provided by the invention;

FIG. 3 is a primary piston structure diagram of a secondary hydraulic damping thrust cylinder according to the present invention;

fig. 4 is a core-stage piston structure diagram of the two-stage fire hydraulic damping thrust cylinder provided by the invention.

Reference numerals:

1. a housing; 2. a primary piston; 3. hydraulic oil; 4. a core stage piston; 5. a front end enclosure; 6. a retainer ring; 7. a gas generator; 8. an O-shaped sealing ring; 9. an O-shaped sealing ring; 10. an O-shaped sealing ring; 11. an O-shaped sealing ring; 21. a piston disc; 22. an oil passing hole; 23. a piston rod; 41. a frustum; 42. a piston disc.

Detailed Description

The present invention will be described in detail with reference to the accompanying drawings and specific embodiments, which are implemented on the premise of the technical solution of the present invention, and give detailed embodiments and specific operation procedures, but the protection scope of the present invention is not limited to the following embodiments.

When the actuating cylinder drives the load to move, the maximum impact occurs when the load starts to move and is in place. The damping force is related to the moving speed of the piston, and the piston starts to accelerate from a rest state when the actuating cylinder is started, so that the damping force is small in an initial state. The fuel gas thrust is high due to violent combustion of gunpowder, but the damping is low at the moment, and the load acceleration is high, so that the initial impact is high; when the load is in place, the load is suddenly stopped from a certain speed, so the impact is larger. In the field of aerospace, particularly displacement driving with precision equipment load on a satellite, the whole motion is required to have small impact, namely the impact is small when the satellite is started and put in place.

Based on the above inventive concept, the invention discloses a variable damping two-stage hydraulic damping thrust cylinder, as shown in fig. 1, the thrust cylinder comprises: the fuel gas generator comprises a shell 1, a primary piston 2, hydraulic oil 3, a core-grade piston 4, a front seal head 5, a check ring 6, a fuel gas generator 7 and O-shaped seal rings 8-11, wherein a cavity between the shell 1 and a piston rod of the primary piston 2 is filled with the hydraulic oil 3 to form an oil storage cavity I, a cavity between the primary piston 2 and the core-grade piston 4 is filled with the hydraulic oil 3 to form an oil storage cavity II, and the two oil storage cavities are communicated through oil through holes 22 which are radially arranged on the primary piston 2; preceding head 5 install at I right-hand member portion in oil storage chamber, retaining ring 6 is installed at 2 right-hand member portions of one-level piston, the processing of 5 hole left ends of preceding head and 4 left end frustums of core level piston has certain tapering, the internal surface of the hole of preceding head 5 is the conical surface, the aperture of hole reduces from left to right gradually, the frustum surface of 4 left ends of core level piston is the conical surface, the external diameter of frustum increases from left to right gradually. The two oil storage cavities are filled with hydraulic oil, and the total volume of the hydraulic oil 3 is equal to the maximum value of the cavity formed by the shell 1 and the first-stage piston 2 and the minimum value of the cavity formed by the first-stage piston 2 and the core-stage piston 4.

The shell 1, the primary piston 2 and the core-stage piston 4 are in clearance fit and can move axially after being nested in sequence, an O-shaped sealing ring 11 is arranged between the shell 1 and the primary piston 2, an O-shaped sealing ring 10 is arranged between the core-stage piston 4 and the primary piston 2, and dynamic sealing is realized in the moving process.

As shown in FIG. 3, the primary piston 2 comprises a piston disc 21, oil passing holes 22 and a piston rod 23, the oil passing holes 22 are radially arranged at positions close to the piston disc 21, and the length-diameter ratio of the oil passing holes is not more than 2/1, so that the influence of liquid viscosity on the flow speed of liquid can be reduced while the structural strength and the processing manufacturability are ensured.

Grooves for installing O-shaped rings 8 and 9 are uniformly formed in the inner side and the outer side of the front seal head 5, an O-shaped sealing ring 8 is arranged between the front seal head 5 and the primary piston 2, and an O-shaped sealing ring 9 is arranged between the front seal head 5 and the shell 1; an O-shaped ring 9 on the outer side of the front seal head is tightly pressed with the shell 1 to realize static sealing, an O-shaped ring 8 on the inner side of the front seal head is matched with a piston rod of the primary piston 2 to realize dynamic sealing, and meanwhile, the front seal head 5 realizes the limit of the primary piston 1; the retainer ring 6 is arranged at the end part of the first-stage piston 2 to limit the core-stage piston 4.

Preceding head 5 outsides and one-level piston 2's piston rod 23 are clearance fit, rely on O shape sealing washer 8 to realize the movive seal in the direction, preceding head 5 is close to the inboard processing of oil storage chamber I and has certain tapering, and the macrostoma is towards oil storage chamber I, and the conical surface is about 2 times in the oilhole aperture with the maximum clearance of one-level piston 2 piston rod 23, and the axial length of conical surface equals the distance of crossing oilhole 22 center and piston disc 21 right-hand member face on one- level piston 2, and 1 is generally got to the inclination: 5-1: 3.

as shown in fig. 4, the core-stage piston 4 includes a frustum 41 and a piston disc 42, the frustum 41 is processed on one side of the tail portion of the core-stage piston 4 close to the oil storage chamber ii, the frustum 41 is connected with the piston disc 42 without steps, the height of the frustum is equal to the distance between the center of the oil passing hole 22 on the first-stage piston 2 and the right end face of the piston disc 21, and the inclination of the frustum is the same as that of the inner conical surface of the front end enclosure 5. When the actuating cylinder is started, the damping force is larger under the shielding effect of the conical surface of the core-level piston 4, the clearance between the conical surface of the core-level piston 4 and the oil passing hole is larger and larger along with the movement of the primary piston 2, the shielding effect on the oil passing hole is weaker and weaker, and the damping force is gradually reduced so as to realize impact reduction during starting; when the actuating cylinder works in place, the oil passing hole is shielded by the conical surface of the front seal head 5, and the damping force is gradually increased to realize in-place strong buffering.

The sectional area of an annular oil storage cavity I formed between the shell 1 and the piston rod of the primary piston 2 is equal to the sectional area of the inner cavity of the primary piston 2, the movable distance of the primary piston 2 in the shell 1 is slightly smaller than that of the core piston 4 in the primary piston 2, and the distance is about smaller than 2%. The constraint conditions can ensure that the end faces of the rear-stage piston 2 and the front end enclosure 5 are attached when the actuator cylinder works in place while realizing the maximum stroke ratio so as to bear the gas thrust after the actuator cylinder works in place, and avoid the hidden danger of leakage caused by the fact that the gas thrust continuously presses hydraulic oil after the actuator cylinder works in place.

Because the hydraulic transmission system plays a role similar to a movable pulley while realizing damping, the two-stage pistons are expanded in an equal ratio in the motion process, and the speed ratio of the first-stage piston to the core-stage piston is 1: 2, under the condition of certain gas pressure, the output thrust is always the same, and the magnitude of the output thrust is equal to 0.5 time of the thrust of the gas acting on the primary piston.

The variable damping secondary hydraulic damping thrust cylinder is driven by high-temperature and high-pressure gas generated by burning gunpowder in the gas generator 7 to realize functions, the mounting position of the gas generator is not limited to the radial mounting mode in the figure 1, and the variable damping secondary hydraulic damping thrust cylinder can also be arranged in the axial direction of the actuating cylinder and can discharge the gas into a power cavity in the shell 1.

When the damping device works, the fuel gas generator 7 generates fuel gas to push the primary piston 2 to move, and the hydraulic oil 3 in the annular cavity is compressed when the primary piston 2 moves, so that the hydraulic oil passes through the oil passing hole at the root part of the primary piston to generate a damping effect; due to the shielding effect of the conical surface of the core-stage piston 4, the damping force is reduced from large to small during starting, and the thrust output is reduced from small to large so as to reduce the impact. Due to the incompressible characteristic of liquid, hydraulic oil 3 enters the inside of the first-stage piston and then acts on the core-stage piston 4 to drive the core-stage piston to move, as shown in fig. 2, when the first-stage piston moves in place quickly, the oil passing hole enters the front end enclosure 5 and is shielded by the front end enclosure, the damping force is gradually increased to achieve in-place strong buffering, and the flow rate of the hydraulic oil is reduced to achieve variable damping.

The left end is herein the end close to the gas generator 7 and the right end is the end remote from the gas generator 7.

Those skilled in the art will appreciate that those matters not described in detail in the present specification are well known in the art.