CN117570126A - Special-shaped clutch for flywheel engagement of screw press - Google Patents

Abstract

The present application relates to the field of screw press clutches, and in particular to a profile clutch for screw press flywheel engagement, comprising; the clutch outer cover is arranged above the large flywheel and the main screw rod, the side edge of the clutch outer cover is fixedly connected to the top side surface of the large flywheel, and a clutch inner cavity is formed among the inner wall of the clutch outer cover, the top side surface of the large flywheel and the top end surface of the main screw rod; the pressure inner container is arranged in the clutch inner cavity and is in clearance fit with the clutch outer cover, the pressure inner container is hollowed into a shell shape, and the edge of the pressure inner container is connected with the clutch inner cavity through bolts; the driving piece is used for driving the pressure liner to apply force downwards; the friction body is arranged between the bottom side of the pressure inner container and the wheel surface of the large flywheel, and applies downward force along with the pressure inner container so as to tightly prop against the large flywheel and the pressure inner container; correspondingly, the top side of the large flywheel is provided with a groove for accommodating the friction body. The screw press has the advantages that the stable operation of the screw press is ensured, and meanwhile, the large flywheel and the main screw rod have good joint performance.

Description

Special-shaped clutch for flywheel engagement of screw press

Technical Field

The present application relates to the field of screw press clutches, and in particular to a profile clutch for screw press flywheel engagement.

Background

The screw press is an industrial device for metal processing, a precise transmission assembly is finely developed on a simpler screw-nut structure frame, a nut matched with the main screw is driven to vertically move by rotating a main screw arranged vertically in a frame, a forging block is arranged on the nut, and a metal block on a bottom die of the screw press is pressed down and forged along with the rotation of the nut.

Because the fineness and the adaptability of the asynchronous servo motor are stronger, the existing screw press basically selects the asynchronous servo motor as a driving piece main body, and the flywheel arranged on the main screw is driven to rotate by the asynchronous servo motor driving gear transmission group or the belt transmission group, so that the main screw is driven to rotate.

As is well known, the conventional screw press has a disadvantage that the screw drive mode causes the ascending and descending of the forging block to depend on the forward rotation and the reverse rotation of the main screw rod, and huge energy is accumulated in the descending process of the forging block, so that the instantaneous power required for the main screw rod to reverse to a high-speed rotation state in a short time after forging is large, the electric shock generated by the asynchronous servo motor in the reverse rotation process impacts a power grid, the safety range of electric power is easily broken through, and the phenomena of tripping and wire burning are caused. However, the forging of the metal block requires multiple forging strokes, and it is impossible to cause a workshop power failure for each forging stroke, and therefore, improvement of the screw press is required.

There is an improvement mode in the market that single flywheel driving of a screw press is changed into double flywheel driving, namely, a small flywheel is arranged as a reversing driving piece of a main screw, and because inertia and momentum of the small flywheel are small, electric shock impulse generated in the moment of reversing of asynchronous servo motor driving cannot threaten a workshop power grid, a traditional large flywheel is used as a cooperative rotating piece on the basis, and rotation in the same direction is always kept, and the small flywheel acts on the main screw only when the main screw descends, and acts together with the small flywheel to assist a forging block at the bottom end of the main screw to accumulate energy.

The double flywheel driving structure needs a clutch, the large flywheel is combined with the main screw rod when the main screw rod rotates to drive the forging block to descend, and the large flywheel is separated from the main screw rod when the main screw rod rotates reversely to drive the forging block to ascend, so that the large flywheel always keeps the same rotating speed without reversing.

Aiming at the related technology, a novel clutch is designed for the double flywheel driving structure of the screw press, so that the screw press can be ensured to stably operate, and meanwhile, the large flywheel and the main screw rod have better joint performance.

Disclosure of Invention

In order to ensure that the screw press stably operates and simultaneously ensure that the large flywheel and the main screw rod have better joint performance, the application provides a special-shaped clutch for the joint of the screw press flywheel.

The application provides a special-shaped clutch for screw press flywheel joint adopts following technical scheme:

a profiled clutch for engagement of a screw press flywheel, comprising;

the clutch outer cover is arranged above the large flywheel and the main screw rod, the side edge of the clutch outer cover is fixedly connected to the top side surface of the large flywheel, and a clutch inner cavity is formed among the inner wall of the clutch outer cover, the top side surface of the large flywheel and the top end surface of the main screw rod;

the pressure inner container is arranged in the clutch inner cavity and is in clearance fit with the clutch outer cover, the pressure inner container is hollowed into a shell shape, and the edge of the pressure inner container is connected with the clutch inner cavity through bolts;

the driving piece is arranged at the top end of the clutch outer cover and is used for driving the pressure liner to apply force downwards;

the friction body is arranged between the bottom side of the pressure inner container and the wheel surface of the large flywheel, and applies downward force along with the pressure inner container so as to tightly prop against the large flywheel and the pressure inner container; correspondingly, the top side of the large flywheel is provided with a groove for accommodating the friction body.

By adopting the technical scheme, the clutch outer cover is used as the outer shell of the clutch, the clutch outer cover synchronously rotates along with the flywheel when the motor drives the large flywheel to rotate, and under the condition that the driving piece does not operate, namely in a state that the large flywheel is separated from the main screw rod, the clutch outer cover and the pressure inner container keep synchronously rotating, the pressure inner container can slide vertically along the axial direction of the bolt in a bolt connection mode, but only slide vertically, the pressure inner container is not rigidly connected with the friction body, the friction body is pressed to the surface of the flywheel only by the gravity of the pressure inner container, and the friction force between the friction body and the large flywheel is not brought by the gravity of the pressure inner container, so that the main screw rod cannot synchronously rotate along with the large flywheel, and the pressure inner container keep a separated state; when the main screw rotates to drive the forging block to descend, the clutch is required to connect the large flywheel with the main screw, the driving piece operates and drives the pressure liner to apply force downwards, so that the pressure liner supports the friction body against the wheel surface of the large flywheel, the friction force between the friction body and the wheel surface of the large flywheel is instantaneously increased by sudden pressure increase, the driving force of the large flywheel is connected to the rotation of the main screw, then the driving piece keeps in an operating state, the friction body continuously supports against the large flywheel, the rotation torque of the large flywheel is superposed with the rotation torque of the small flywheel, and huge energy is accumulated in the downward movement process of the forging block; based on the above operation process, in this embodiment, the pressure liner is hollowed into a shell shape, which not only saves the material cost of the pressure liner, but also reduces the gravity of the pressure liner, and when the main screw is separated from the large flywheel, the friction force between the friction body and the large flywheel wheel surface and the friction force between the friction body and the bottom side of the pressure liner can be kept in a smaller range, so as to minimize friction loss; in addition, in the scheme, the clearance fit between the pressure inner container and the clutch outer cover gives the pressure inner container a certain anti-vibration performance, and if the pressure inner container and the clutch outer cover are precisely matched, when the forging block violently impacts the metal block or the main screw rod rotates at a high speed, the accessory high-frequency vibration of the forging block can damage the precise matching surface.

Optionally, the friction body includes:

the friction disc body is horizontally arranged and fixedly connected to the top end of the main screw, a plurality of perforations are circumferentially formed in the upper part of the friction disc body at equal intervals, and the friction disc body vertically penetrates through the perforations;

the friction block is inserted into the through hole of the friction disc body, and two ends of the friction block protrude out of two sides of the friction disc body to be abutted against the top side of the large flywheel and the bottom side of the pressure liner.

By adopting the technical scheme, the friction disc body is used as a main bearing structural member of the friction body and is arranged in a disc shape, the disc surfaces at two ends are circular, so that shearing torque can be evenly dispersed, friction forces at two sides of the pressure liner and the large flywheel can be well borne, a plurality of friction blocks are inserted in the friction disc body at equal intervals in the circumferential direction, the height of each friction block is higher than the thickness of the friction disc body, so that two ends of each friction block protrude out of the friction disc body, the friction disc body is used as a huge torque transmission framework between the pressure liner and the large flywheel, and strong structural strength is required, so that excessive friction loss cannot be received, the friction disc body is erected through the friction blocks, the two end surfaces of the friction disc body are not contacted with the bottom side surface of the pressure liner and the top side surface of the large flywheel, and when the pressure liner is driven by a driving piece to abut against the large flywheel, the friction blocks can be used only; in summary, the above solution makes a balanced design between the friction surface and the support structure surface; in addition, under the condition that the installation stability of the friction block and the structural strength of the friction disc body are not affected, the friction surface of the friction block in the scheme is arranged close to the edge of the friction disc body as much as possible, so that a torque arm is increased, and a better rotation driving effect is obtained.

Optionally, the driving member includes;

the communication valve is arranged at the top side of the clutch outer cover and is communicated with a high-pressure air source;

the air hose is arranged between the clutch outer cover and the communication valve, and is used for communicating the clutch inner cavity with the communication valve and leading the air conveyed by the high-pressure air source into the clutch inner cavity;

and the sealing piece is arranged in the clutch inner cavity and is used for reducing gas leakage.

By adopting the technical scheme, the torque shearing damage between the pressure liner and the driving piece can be avoided by adopting a mode of driving the pressure liner to move downwards by air pressure, the high-pressure air source is adopted to convey the air towards the communication valve, then the air is conveyed into the inner cavity of the clutch through the air hose, the air is diffused in the inner cavity of the clutch and blocked by the sealing piece, the air is limited in a small-volume space, and the input quantity of the high-pressure air source and the conveying energy consumption during the conveying of the air are reduced; in addition, the scheme adopts the mode of driving the pneumatic piece to externally apply the clearance fit between the pressure inner container and the clutch outer cover, and a gas isolation layer is formed between the pressure inner container and the inner wall of the clutch outer cover during operation, so that the mutual vibration influence of the pressure inner container and the clutch outer cover is avoided when the main screw rotates or the forging block collides.

Optionally, the air hose is provided with many, and the tie point of many air hoses and separation and reunion enclosing cover is equidistant along same circumference distribution.

Through adopting above-mentioned technical scheme, combine the structure of separation and reunion enclosing cover and clutch inner chamber in the above-mentioned scheme, with the tie point average distribution of air hose and separation and reunion enclosing cover, make the gas density in the clutch inner chamber average, because the non-rigid support of pneumatic drive's mode, the uneven pressure density will lead to the pressure inner bag to possess the slope trend, high-speed rotation and the high frequency vibrations that accompany large-scale flywheel take place violently vibrations when supporting the large-scale flywheel tread through the friction block, lead to screw press moving stability not enough, lead to the deformation of shell form pressure inner bag to take place more easily under the long-time, take place the focus skew, lead to follow-up stability to continue to worsen.

Optionally, further comprising;

the guide post is vertically arranged at the center part of the bottom side wall of the clutch outer cover, the bottom end of the side wall of the guide post is obliquely arranged, and correspondingly, the pressure liner is provided with a groove matched with the guide post.

By adopting the technical scheme, the limiting effect is applied to the pressure liner in the state of compressing the friction block, the vibration of the pressure liner is limited within a certain range, and meanwhile, the structural damage of the vibration to the joint of the weak part of the edge of the pressure liner and the bolt is weakened; according to the scheme, the guide column is arranged in a cylindrical shape, the part, close to the bottom end, of the side wall is inclined towards the central axis, so that the guide column is integrally arranged in an inverted cone shape, correspondingly, the pressure liner is provided with the groove which is matched with the inverted cone shape and is used for clamping the guide column, the contact area of the side wall of the guide column can be increased through the inclined structure of the side wall of the guide column, a more stable contact surface is provided when the pressure liner vibrates, and the stability of the operation process of the screw press is further improved; based on this structure, it is suggested that the fit of the guide post and the corresponding groove of the pressure liner is clearance fit, giving the pressure liner sufficient vibration space.

Optionally, further comprising;

the pressure piece is arranged above the clutch outer cover and connected with the communication valve, and is used for driving the communication valve to move vertically;

the communication valve penetrates through the clutch outer cover and is connected with the guide column, and the guide column moves downwards along with the operation of the driving piece.

According to the technical scheme, the stability of the high-pressure air delivered by the air pressure piece is considered, in the scheme, after the high-pressure air source is input into the clutch inner cavity, the pressure piece drives the communication valve, so that the guide post is driven to move downwards, the guide post is propped against the pressure inner cavity, the vibration of the pressure inner cavity is reduced, and the stability of the screw press in the rotation process of the main screw is improved; in the above scheme, only the pressure piece is used as a stabilizing component, after the high-pressure air source is in air transmission with the air hose through the communication valve and the air pressure is forced to be under the pressure liner by air pressure, the pressure liner is abutted against by the guide post, and the stability of the pressure liner is improved.

Optionally, the seal comprises;

the sealing ring is sleeved on the side edge of the pressure inner container and abuts against the corresponding part of the inner wall of the clutch outer cover.

By adopting the technical scheme, the sealing ring is used for limiting the gas flowing space, the corresponding part of the pressure liner is provided with a groove which is matched with the sealing ring, and the groove height is smaller than the diameter of the section of the sealing ring, so that the sealing ring abuts against the clutch outer cover after the pressure liner is installed; in order to further improve the sealing effect, the side edge of the pressure inner container can be vertically arranged, and a groove for clamping the sealing ring is formed in the position where the side edge of the pressure inner container is vertically arranged.

Optionally, the center part of the top side of the pressure liner is columnar and is a positioning part, and the middle part structure of the clutch outer cover is adapted to the positioning part;

the seal further comprises;

the sealing ring is sleeved on the side wall of the positioning part of the pressure liner, and abuts against the inner wall of the pressure liner and the inner wall of the clutch outer cover.

By adopting the technical scheme, the cross-section structure of the pressure liner is similar to a triangle, partial structures are vertically arranged on the top side and the bottom side and are used for clamping the sealing piece, sealing pieces are arranged on the top side and the bottom side of the pressure liner, gas input from the gas hoses is limited on the inclined side wall part of the pressure liner, the direction of gas source input of the gas hoses is nearly vertical, and the plurality of gas hoses impact high-pressure gas flow on the pressure liner in a short time and are driven to move downwards by the sealing effect of the sealing pieces through denser gas pressure; in addition, the vertical arrangement of the top side and the bottom side of the pressure liner can play a role in guiding, so that the displacement freedom degree of the pressure liner pushed by the air pressure is further limited, and the horizontal offset of the pressure liner is directly avoided by cooperation of the bolt and the guide post; in addition, because sealing washer and sealing ring are soft material, consequently can also cushion the vibrations that transmit to pressure inner bag department when main screw rod rotates to a certain extent.

In summary, the present application includes at least the following beneficial technical effects:

1. the high-pressure air source is used for conveying air pressure through the communication valve and the air hose, and the high-density air pressure drives the pressure liner to move downwards in a driving mode, so that direct contact between the driving piece and the pressure liner can be avoided, and vibration of the pressure liner is prevented from being directly transmitted to the driving piece to interfere with stable operation of the driving piece;

2. in this application with the clutch blocks outstanding in friction disk body setting, avoid the higher friction disk body both ends face direct contact of structural requirement, cause the friction loss of friction disk body, and the clutch blocks are close to the edge setting of pressure disc ladder on guaranteeing structural strength's basis, the arm of force of extension frictional force increases the driving effect to the main screw rod.

Drawings

Fig. 1 is a schematic overall structure of an embodiment of the present application.

Fig. 2 is a semi-sectional view of an embodiment of the present application for highlighting the internal structure of the clutch.

Fig. 3 is a schematic structural view of a friction disc in an embodiment of the present application.

Fig. 4 is an enlarged view of a portion a of fig. 2.

Reference numerals illustrate: 1. a screw press; 11. a main screw; 12. a large flywheel; 2. a clutch outer cover; 21. a friction body; 211. a friction plate body; 212. a friction hole; 213. a friction block; 22. a communication valve; 221. an air hose; 23. a seal ring; 24. a seal ring; 25. a guide groove; 251. a guide post; 26. and a gas spring.

Detailed Description

The present application is described in further detail below in conjunction with figures 1-4.

The embodiment of the application discloses a special-shaped clutch for flywheel engagement of a screw press. Referring to fig. 1 and 2, a special clutch for engagement of a flywheel of a screw press comprises a clutch outer cover 2 arranged on the top side of a main screw 11 and a large flywheel 12 of the screw press 1, wherein the longitudinal section of the clutch outer cover 2 is triangular, the inside of the clutch outer cover is evacuated to be in a shell shape, and the whole clutch outer cover is in a gong shape; the side edge of the clutch outer cover 2 is fixed on the large flywheel 12 through bolts and synchronously rotates along with the large flywheel 12; the clutch inner cavity is formed by the bottom side surface of the clutch outer cover 2, the top end surface of the main screw 11 and the top end surface of the large flywheel 12, and the main clutch structure of the clutch is arranged in the clutch inner cavity. In this embodiment, the clutch outer cover 2 serves as an integral housing of the clutch, and serves to protect the internal clutch structure.

Referring to fig. 2, the top end surface of the main screw 11 and the top end surface of the large flywheel 12 are both horizontally arranged, a pressure liner 3 is arranged in the clutch inner cavity, the top side of the pressure liner 3 is obliquely arranged parallel to the clutch outer cover 2, the top side of the pressure liner 3 is in clearance fit with the clutch outer cover 2, the bottom side of the pressure liner 3 is horizontally arranged, and the bottom edge of the pressure liner is in bolt connection with the clutch outer cover 2 and the large flywheel 12 through a vertically arranged bolt, so that the pressure liner 3 can vertically displace, but is limited in a clearance with the clutch outer cover 2; in this embodiment, the pressure liner 3 is one of the main clutch structures, a friction body 21 is disposed between the bottom side of the pressure liner 3 and the top side of the large flywheel 12, the friction body 21 is connected with the main screw 11, vertical downward pressure is applied to the pressure liner 3 to compress the friction body 21, and the friction force between the friction body 21 and the large flywheel 12 drives and engages the rotation of the large flywheel 12 onto the main screw 11, so that the main screw 11 and the large flywheel 12 rotate synchronously, and engagement is achieved.

Referring to fig. 2 and 3, the friction body 21 is composed of a friction plate body 211 and a plurality of friction blocks 213 disposed inside the friction plate body 211, the friction plate body 211 is horizontally disposed, inserted into the top end portion of the main screw 11, and fixed to the main screw 11 by bolts; the part of the friction disk body 211, which is close to the edge, is vertically provided with a plurality of cylindrical perforations, the plurality of perforations are distributed at equal intervals along the circumferential direction of the edge of the friction disk body 211, each perforation is internally and vertically inserted with a friction block 213 with an adaptive perforation aperture, and the thickness of the friction block 213 is higher than that of the friction disk, so that when the friction block 213 is inserted into the friction disk body 211, two ends of the friction block 213 protrude out of the friction disk.

When the clutch is in an engaged state, the pressure liner 3 downwards presses the friction block 213, so that the pressure liner 3 and the large flywheel 12 drive the friction block 213 to synchronously rotate through huge friction force, and the friction block 213 pulls the main screw 11 to synchronously rotate with the large flywheel 12 through the friction disc 211; when the clutch is in a separation state, the pressure inner container 3 does not apply force any more, the clutch outer cover 2 synchronously rotates along with the large flywheel 12, the pressure inner container 3 keeps rotating at a low speed in the clutch inner cavity under the friction drive of the clutch outer cover 2, and the friction disc 211 and the main screw 11 are synchronously rotated under the drive of the small flywheel, namely, the friction disc 211, the pressure inner container 3 and the large flywheel 12 keep independent and respectively rotate relatively.

Referring to fig. 2, a disk groove adapted to the friction disk 211 is formed on the top side surface of the large flywheel 12; based on the above-mentioned operation principle of the pressure liner 3, in this embodiment, the pressure liner 3 is hollowed out, so that the pressure liner 3 is entirely shell-shaped, so as to reduce the gravity of the pressure liner 3, and avoid the increase of friction loss of the friction disk 211 and the pressure liner 3 due to the influence of the friction blocks 213 when the clutch is not engaged; further, the bottom side of the pressure liner 3 is not closed, so that friction loss caused by direct contact with the top end of the main screw 11 is avoided, and the side edge of the bottom side of the pressure liner 3 corresponds to the friction block 213 and covers the upper side of the friction block 213.

Referring to fig. 2 and 4, the pressure liner 3 is pressed downward by pneumatic driving, and accordingly, the pneumatic driving member in this embodiment includes a communication valve 22 disposed at a central portion of the clutch outer cover 2, the communication valve 22 is integrally square, each side edge is connected with one air hose 221, one end of each air hose 221, far away from the communication valve 22, is connected to the clutch outer cover 2 and penetrates through the clutch outer cover 2 to be communicated with the clutch inner cavity, connection points of the air hoses 221 and the clutch outer cover 2 in this embodiment are distributed on the same circumference, and two ends of each air hose 221 are on the same vertical plane, so that gas input points of the clutch inner cavity are distributed uniformly, and gas density distribution in the clutch inner cavity is uniform.

In this embodiment, the communication valve 22 is connected to a high-pressure air source, which is not shown for convenience of illustration and is not described in detail. The high-pressure air source injects air into the gap part between the pressure inner container 3 and the clutch outer cover 2 in the inner cavity of the clutch through the air hose 221, a high-pressure air belt is formed between the pressure inner container 3 and the clutch outer cover 2, the pressure inner container 3 is pushed to move downwards to abut against the friction block 213, the high-pressure air source keeps the stable high pressure in the inner cavity of the clutch in an air pressure stable state, the pressure inner container 3 continuously presses the friction block 213, and the continuous connection between the main screw 11 and the large flywheel 12 is realized.

Referring to fig. 2 and 4, based on the pneumatic driving manner, in this embodiment, sealing elements are disposed at the top end and the bottom end of the inner cavity of the clutch, and the sealing elements can greatly reduce the divergence of gas along the top side and the bottom side of the pressure inner container 3, and reduce the volume of the flowing area of the gas by improving the sealing performance, and reduce the conveying amount and conveying energy consumption of the high-pressure gas source during gas input.

Referring to fig. 4, the sealing member includes a sealing ring 23 disposed at the bottom edge of the pressure liner 3, the edge of the pressure liner 3 is provided with an annular groove for clamping the sealing ring 23 with respect to the sealing ring 23, and the groove height of the annular groove is smaller than the cross-sectional diameter of the sealing ring 23, so that the sealing ring 23 is extruded and deformed in the gap between the clutch outer cover 2 and the pressure liner 3, and a better sealing effect is achieved; the sealing piece further comprises a sealing ring 24 sleeved on the edge of the top side of the pressure liner 3, the thickness of the sealing ring 24 is smaller than the preset gap width between the clutch outer cover 2 and the pressure liner 3, and the sealing ring 24 and the sealing ring 23 are enabled to be extruded and deformed in the same way, so that the sealing effect is improved.

Referring to fig. 2 and 4, in order to improve the fixing performance of the sealing ring 23 and the sealing ring 24, at the same time, after the high-pressure gas is input, the displacement directionality of the pressure liner 3 along with the gas extrusion is provided with positioning parts at the parts of the pressure liner 3 near the top side and the bottom side, the part of the pressure liner 3 at the positioning part is in a vertically arranged disk shape, the sealing ring 24 is sleeved on the positioning part at the top end of the pressure liner 3, the sealing ring 23 is sleeved on the positioning part at the bottom side of the pressure liner 3, and accordingly, an annular groove for clamping the sealing ring 23 is formed on the corresponding positioning part; the guide groove 25 is formed in the clutch outer cover 2 corresponding to the positioning part of the pressure inner container 3, the guide groove 25 is vertically formed in the positioning part of the pressure inner container 3 in a matched mode, when the pressure inner container 3 is pushed to move downwards by high air pressure, the guide groove 25 of the clutch outer cover 2 enables the positioning part of the pressure inner container 3 to move downwards to press the friction block 213 through structure limiting, and the phenomenon that the joint effect of the main screw 11 and the large flywheel 12 is unstable due to uneven pressing of the friction block 213 is avoided.

Referring to fig. 2 and 4, considering that when the main screw 11 is not engaged with the large flywheel 12, the pressure inner container 3 is easy to deviate relative to the rotation of the clutch outer cover, and when the main screw 11 is engaged with the large flywheel 12, the rotation of the main screw 11 is accompanied by high-frequency vibration, and the vibration deviation of the pressure inner container 3 will occur due to the transmission of structural guidance to the pressure inner container 3, in this embodiment, a guide post 251 is vertically disposed on the bottom side surface of the clutch outer cover 2, the top end of the guide post 251 is fixedly connected with the communication valve 22, a guide slot 25 is disposed on the top end of the pressure inner container 3 corresponding to the guide post 251, the guide post 251 is inserted into the guide slot 25, and the bottom end extends to the inner bottom wall of the guide slot 25, in this embodiment, the portion of the guide post 251 extending into the clutch inner cavity is inclined towards the center, and accordingly, the inner wall of the guide slot 25 is adapted to the guide post 251 is disposed, thereby, when the pressure inner container 3 vibrates, the pressure inner container 3 is reset by means of the structure of the guide slot 25 and the guide post 251.

Referring back to fig. 2, in this embodiment of the present application, the driving element for driving the pressure liner 3 to move downward further includes a gas spring 26 disposed above the pressure liner 3, where the gas spring 26 is disposed vertically downward, and a piston rod of the gas spring 26 is fixedly connected with a top end of the communication valve 22, so as to drive the communication valve 22 to move downward after the gas spring 26 operates to extend out of the piston rod, and further drive a guide post 251 fixedly connected with a bottom end of the communication valve 22 to move downward to tightly abut against the top end of the pressure liner 3.

In this embodiment, after the high-pressure gas is injected into the clutch cavity from the high-pressure gas source to push the pressure liner 3 to move downward, the gas spring 26 operates to extend out of the piston rod to push the guide post 251 to move downward, so as to apply a vertical downward force to the pressure liner 3 to tightly press the pressure liner 3, and apply a stable rigid supporting force to the pressure liner 3. Thereby, the method is used for the treatment of the heart disease. The main driving force depends on the high pressure air source, and the air spring 26 only gives one hard supporting force, and the two work together.

Referring to fig. 2 and 4, the clutch outer cover 2 in this embodiment is vertically provided with a venting port for communicating the clutch inner cavity with the outside for discharging the high pressure gas. The vent is connected to a closure assembly, not shown, for ease of illustration of the communication valve 22.

The implementation principle of the special-shaped clutch for the engagement of the flywheel of the screw press is as follows: the clutch is characterized in that the combination and separation of the main screw 11 and the large flywheel 12 are completed by the friction block 213, the clutch outer cover 2, the pressure liner 3 and the large flywheel 12 are fixed by bolts and synchronously rotate, and the clutch outer cover 2, the pressure liner 3 and the large flywheel 12 independently rotate relative to the friction block 213 and the main screw 11.

When the clutch needs to be connected with the large flywheel 12 and the main screw 11, high-pressure gas is injected into the clutch inner cavity by the high-pressure gas source through the communication valve 22 and the gas hose 221, and the high-pressure gas is limited by the sealing element, the pressure liner 3 is pushed to move downwards to tightly abut against the friction block 213 by the excessive high-pressure gas, and the friction block 213 is combined with the pressure liner 3, so that the driving force of the large flywheel 12 is connected to the main screw 11.

Meanwhile, the air spring 26 operates to press the guide post 251 against the pressure liner 3 to provide a stable rigid supporting force so as to realize stable joint of the pressure liner 3 and the friction block 213.

When the clutch needs to separate the large flywheel 12 from the main screw 11, the air release port is opened, the high-pressure air source stops supplying air, under strong air pressure, the high-pressure air in the clutch is lost instantaneously, the pressure liner 3 loses the downward pressure support, and the pressure liner is restored to a state of independent rotation relative to the friction block 213.

The foregoing are all preferred embodiments of the present application, and are not intended to limit the scope of the present application in any way, therefore: all equivalent changes in structure, shape and principle of this application should be covered in the protection scope of this application.

Claims (8)

1. A profiled clutch for engagement of a screw press flywheel, characterized by: comprises the following steps of;

the clutch outer cover (2) is arranged above the large flywheel (12) and the main screw (11), the side edge of the clutch outer cover is fixedly connected to the top side surface of the large flywheel (12), and a clutch inner cavity is formed among the inner wall of the clutch outer cover (2), the top side surface of the large flywheel (12) and the top end surface of the main screw (11);

the pressure inner container (3) is arranged in the clutch inner cavity and is in clearance fit with the clutch outer cover (2), the interior of the pressure inner container (3) is hollowed into a shell shape, and the edge of the pressure inner container (3) is connected with the clutch inner cavity through bolts;

the driving piece is arranged at the top end of the clutch outer cover (2) and is used for driving the pressure liner (3) to apply force downwards;

the friction body (21) is arranged between the bottom side of the pressure inner container (3) and the wheel surface of the large flywheel (12), and is downwards applied with the pressure inner container (3) to tightly prop against the large flywheel (12) and the pressure inner container (3); correspondingly, the top side of the large flywheel (12) is provided with a groove for accommodating the friction body (21).

2. A profiled clutch for engagement of a screw press flywheel as claimed in claim 1 wherein: the friction body (21) includes:

the friction disc body (211) is horizontally arranged and fixedly connected to the top end of the main screw (11), a plurality of perforations are circumferentially arranged on the friction disc body at equal intervals, and the friction disc body (211) vertically penetrates through the perforations;

the friction block (213) is inserted into the through hole of the friction disc body (211), and two ends of the friction block protrude out of two sides of the friction disc body (211) to be abutted against the top side of the large flywheel (12) and the bottom side of the pressure liner (3).

3. A profiled clutch for engagement of a screw press flywheel as claimed in claim 1 wherein: the driving member includes;

the communication valve (22) is arranged at the top side of the clutch outer cover (2) and is communicated with a high-pressure air source;

the air hose (221) is arranged between the clutch outer cover (2) and the communication valve (22), and is used for communicating the clutch inner cavity with the communication valve (22) and leading air conveyed by the high-pressure air source into the clutch inner cavity;

and the sealing piece is arranged in the clutch inner cavity and is used for reducing gas leakage.

4. A profiled clutch for engagement of a screw press flywheel as claimed in claim 3 wherein: the clutch outer cover is characterized in that a plurality of air hoses (221) are arranged, and connection points of the air hoses (221) and the clutch outer cover (2) are distributed at equal intervals along the same circumference.

5. A profiled clutch for engagement of a screw press flywheel as claimed in claim 3 wherein: also comprises;

the guide column (251) is vertically arranged at the center part of the bottom side wall of the clutch outer cover (2), the bottom end of the side wall of the guide column (251) is obliquely arranged, and correspondingly, the pressure liner (3) is provided with a groove which is matched with the guide column (251).

6. A profiled clutch for engagement of a screw press flywheel as claimed in claim 3 wherein: also comprises;

the pressure piece is arranged above the clutch outer cover (2) and is connected with the communication valve (22) and used for driving the communication valve (22) to move vertically;

the communication valve (22) penetrates through the clutch outer cover (2) to be connected with the guide column (251), and moves downwards along with the operation of the driving piece and the guide column (251).

7. A profiled clutch for engagement of a screw press flywheel as claimed in claim 3 wherein: the seal comprises;

the sealing ring (23) is sleeved on the side edge of the pressure liner (3) and abuts against the corresponding part of the inner wall of the clutch outer cover (2).

8. A profiled clutch for engagement of a screw press flywheel as claimed in claim 1 wherein: the seal further comprises;

and the sealing ring (24) is sleeved on the side wall of the positioning part of the pressure liner (3), and abuts against the inner walls of the pressure liner (3) and the clutch outer cover (2).