CN214946480U - Automatic brake force compensator - Google Patents

Abstract

The application discloses tight power automatic compensator of floodgate belongs to petrochemical equipment technical field. When the lead screw of double-gate valve moves downwards, the T-shaped mandrel in the automatic brake force compensator compresses the spring, and under the action of the elastic force of the spring, the spring pushes the sleeve to move downwards so that the sleeve pushes the valve rod to move downwards through the valve rod joint to close the gate of the double-gate valve, so that the elastic force of the spring is converted into brake force, and the condition that the valve plate gate is not closed in place or the brake force is insufficient is avoided.

Description

Automatic brake force compensator

Technical Field

The application relates to the technical field of petrochemical equipment, in particular to a brake force automatic compensator.

Background

The electric high-temperature double-gate valve is widely applied in the field of petrochemical industry, and particularly in large petrochemical devices such as ethylene, propylene, butadiene and the like, the quality of the gate performance directly influences the stable operation of the device.

At present, there are three structural forms of a large-caliber electric high-temperature double-gate plate gate valve used in China, for example, a structural schematic diagram of a double-gate plate gate valve provided by the related art shown in fig. 1, and a structural schematic diagram of a double-gate plate gate valve of A, B and C structures are provided in fig. 1, where the a structure is a parallel double-gate plate gate valve with open sealing, the B structure is a parallel double-gate plate gate valve, and the C structure is a double-wedge double-gate plate gate valve.

To the double-gate board gate valve of A structure in fig. 1, when high temperature double-gate board gate valve was in the open mode, the lumen lasted logical steam, because the temperature of steam is higher, leads to the valve body to be heated and is in the expanding state, and then increases the height of valve body, and the valve rod is most to be exposed outside the lumen, and the temperature is close outdoor temperature, is in the shrink state, and the valve rod shortens. When the valve plate is used for closing the valve, the valve rod moves downwards due to expansion of the valve body and contraction of the valve rod, so that the valve plate is not pressed to the bottom, the valve plate is not in place or the brake force is insufficient, and the short-term leakage phenomenon is easily caused by the valve plate brake not in place or the brake force being insufficient.

For the double-gate-plate gate valve with the structure of B, C in fig. 1, when the valve is in a closed state, steam (or other gas) is introduced into the middle cavity, if the valve plate gate is closed in place, the valve rod is heated and expanded, the valve body is contracted due to the introduction of the sealing gas, and the gate tightening force is gradually increased due to the contraction of the valve body and the expansion of the valve rod, so that the phenomenon that the gate plate gate cannot be opened occurs. Meanwhile, damage to parts may occur, which affects the service performance of the gate valve.

Therefore, in the related art, a tool for assisting in closing or opening the valve plate gate is urgently needed for the large-caliber electric high-temperature double-gate valve, so as to avoid the situations that the valve plate gate is not in place or the gate tightening force is insufficient, and the damage and the valve opening clamping phenomenon caused by the overlarge gate tightening force of parts due to thermal expansion and cold contraction.

Disclosure of Invention

The embodiment of the application provides a tight power automatic compensator of floodgate can avoid appearing the valve plate floodgate and close not in place or the tight not enough condition of power of floodgate. The technical scheme is as follows:

in one aspect, an automatic braking force compensator is provided, the automatic braking force compensator comprising a first solid body, a spring and a second solid body, the first solid body comprising a T-shaped mandrel, the second solid body comprising a sleeve and a valve stem connector, the sleeve comprising a stepped receiving cavity;

the top end of the T-shaped mandrel is fixedly connected with the bottom end of a lead screw of the double-gate plate gate valve;

the T-shaped core shaft is sleeved in the stepped accommodating cavity, and the stepped accommodating cavity is used for providing a sliding channel for the T-shaped core shaft;

a spring is arranged between the head of the T-shaped mandrel and the upper surface of the step of the stepped accommodating cavity;

the top end of the valve rod connector is fixedly connected with the lower surface of the step;

an accommodating cavity is formed among the top end of the valve rod connector, the bottom end of the T-shaped mandrel and the inner surface of the step, the bottom end of the T-shaped mandrel extends into the accommodating cavity, and the accommodating cavity is used for providing a sliding channel for the bottom end of the T-shaped mandrel;

the bottom end of the valve rod joint is fixedly connected with the top end of a valve rod of the double-gate valve.

In a possible implementation manner, the head of the T-shaped mandrel is provided with a first groove which is opened upwards, and the bottom end of the lead screw is embedded into the first groove.

In one possible implementation, the first entity further comprises an anti-rotation key and a first gland;

a second groove with an outward opening is formed in the side face of the lead screw, the part, close to the lead screw, of the anti-rotation key is embedded into the second groove, and the part, far away from the lead screw, of the anti-rotation key is fixedly connected with the part, close to the lead screw, of the first gland;

the bottom end of the first gland is fixedly connected with the head of the T-shaped mandrel.

In one possible implementation, the second entity further comprises a second capping;

the second gland is positioned above the sleeve and the head of the T-shaped mandrel, and the top end of the sleeve is flush with the head of the T-shaped mandrel;

the bottom end of the second gland is fixedly connected with the top end of the sleeve.

In one possible implementation, the second entity further comprises a first bearing;

the first bearing is sleeved on the periphery of the head of the T-shaped mandrel and is positioned in the sleeve.

In a possible implementation manner, the valve rod connector is a cross-shaped valve rod connector, and a third groove with a downward opening is formed in the bottom end of the T-shaped mandrel;

the top of cross valve rod joint stretches into in the third recess, the third recess is used for doing the top of cross valve rod joint provides sliding channel.

In a possible implementation manner, a fourth groove with a downward opening is formed in the bottom end of the sleeve, and a shoulder portion of the cross-shaped valve rod connector is embedded into the fourth groove.

In one possible implementation, the second entity further comprises a third capping;

the third gland is used for pressing the shoulder part of the cross-shaped valve rod connector into the fourth groove;

the top end of the third gland is fixedly connected with the bottom end of the sleeve.

In one possible implementation, the second entity further comprises a second bearing;

the second bearing is sleeved on the periphery of the lower end of the T-shaped mandrel and is positioned in the inner surface of the step.

In a possible implementation manner, the automatic braking force compensator is sleeved in a bracket of the double-gate valve.

The technical scheme provided by the embodiment of the application has the following beneficial effects:

when the lead screw of double-gate valve moves downwards, the T-shaped mandrel in the automatic brake force compensator compresses the spring, and under the action of the elastic force of the spring, the spring pushes the sleeve to move downwards so that the sleeve pushes the valve rod to move downwards through the valve rod joint to close the gate of the double-gate valve, so that the elastic force of the spring is converted into brake force, and the condition that the valve plate gate is not closed in place or the brake force is insufficient is avoided.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.

Fig. 1 is a schematic structural view of a double-gate valve provided in the related art;

fig. 2 is a schematic structural diagram of an automatic braking force compensator according to an embodiment of the present disclosure;

FIG. 3 is a schematic structural diagram of a dual-gate valve with an automatic brake force compensator according to an embodiment of the present disclosure;

fig. 4 is a schematic structural diagram of an automatic compensator for a braking force when a double-gate valve is in a valve-closing state according to an embodiment of the present application.

Detailed Description

To make the objects, technical solutions and advantages of the present application more clear, embodiments of the present application will be described in further detail below with reference to the accompanying drawings.

Fig. 2 is a schematic structural diagram of an automatic braking force compensator provided by an embodiment of the present application, and referring to fig. 2, the automatic braking force compensator includes a first solid body 1, a second solid body 2 and a spring 3, the first solid body 1 includes a T-shaped mandrel 11, the second solid body 2 includes a sleeve 21 and a valve stem connector 22, and the sleeve 21 includes a stepped receiving cavity.

In a possible implementation, the first entity 1 further comprises an anti-rotation key 12 and a first cover 13.

In a possible implementation, the second entity 2 also comprises a second gland 23. In a possible implementation, the second entity 2 further comprises a second bolt. In a possible implementation, the second body 2 also comprises a first bearing 24. In a possible implementation, the second entity 2 also comprises a third gland 25. In a possible implementation, the second entity 2 also comprises a second bearing 26.

For further explanation, the connection manner between the components of the automatic braking force compensator and the operation principle of the components are described below.

First, the respective components in the first entity 1 are described below by (1.1) to (1.3).

(1.1) T-shaped mandrel 11

The top end of the T-shaped mandrel 11 is fixedly connected with the bottom end of a screw rod 4 of the double-gate valve.

The screw 4 is a screw 4 of an electric actuator of a double gate valve, and is a member for pushing a valve stem 5 to slide up and down, such as the screw 4 shown in the structure a-C in fig. 1. The double-gate valve can be a double-gate valve shown in any structure of the structures a-C in fig. 1, and the embodiment of the present application does not specifically limit the double-gate valve and the lead screw 4. In a possible implementation manner, the bottom end of the lead screw 4 is a base, and the diameter of the base is larger than that of the rod body of the lead screw 4.

The T-shaped mandrel 11 is composed of two parts, namely a head part and a shaft body, and the top end of the shaft body is connected with the lower surface of the head part. After the top end of the T-shaped mandrel 11 is fixedly connected to the bottom end of the lead screw 4 of the double-gate valve, if the lead screw 4 slides downward (i.e., slides in the valve-closing direction), the lead screw 4 can push the T-shaped mandrel 11 to slide downward, if the lead screw 4 slides upward (i.e., slides in the valve-opening direction), the lead screw 4 can pull the T-shaped mandrel 11 to slide upward, and when the T-shaped mandrel 11 slides upward, the lead screw 4 can also be pushed to slide upward.

In a possible implementation, the head of the T-shaped mandrel 11 is provided with a first groove that opens upwards, into which the bottom end of the lead screw 4 is embedded, so that the bottom end of the lead screw 4 is connected with the top end of the T-shape.

Specifically, the base of the lead screw 4 is embedded in the first groove, and the upper surface of the base is flush with the upper surface of the head of the T-shaped mandrel 11. So that when the lead screw 4 slides downward, the T-shaped spindle 11 can be pushed to slide downward.

In order to facilitate the screw rod 4 to be able to pull the T-shaped mandrel 11 to slide upwards when sliding upwards, the first entity 1 further comprises a rotation prevention key 12 and a first gland 13, and the screw rod 4 and the T-shaped mandrel 11 are fixedly connected together through the rotation prevention key 12 and the gland. The anti-rotation key 12 and the gland are described below by means of the following 1.2 and 1.3, respectively.

(1.2) anti-rotation Key 12

The anti-rotation key 12 is used to limit the rotation of the screw 4, and in a possible implementation, a second groove with an outward opening is provided on a side surface of the screw 4, and a portion of the anti-rotation key 12 close to the screw 4 is embedded in the second groove. Wherein, the second groove can be arranged on the outer side of the shaft above the base of the screw rod 4.

In a possible implementation manner, the lateral surfaces of the left side and the right side of the screw rod 4 are symmetrically provided with second grooves with outward openings, and the first entity 1 comprises 2 anti-rotation keys 12, namely a first anti-rotation key and a second anti-rotation key.

For the second groove on the left side of the screw rod 4, the right part of the first anti-rotation key is embedded into the second groove to limit the rotation of the screw rod 4, at this time, the right part of the first anti-rotation key is also the part of the first anti-rotation key close to the screw rod 4, and the left part of the first anti-rotation key is also the part of the first anti-rotation key far away from the screw rod 4.

For the second groove on the right side of the screw rod 4, the left part of the second anti-rotation key is embedded into the second groove to limit the rotation of the screw rod 4, at this time, the left part of the second anti-rotation key is also the part of the first anti-rotation key close to the screw rod 4, and the right part of the second anti-rotation key is also the part of the first anti-rotation key far away from the screw rod 4.

(1.3), first gland 13

The part of the anti-rotation key 12 far away from the screw rod 4 is fixedly connected with the part of the first gland 13 close to the screw rod 4, and the bottom end of the first gland 13 is fixedly connected with the head part of the T-shaped mandrel 11, so that the anti-rotation key 12 and the T-shaped mandrel 11 are connected into a whole by the first gland 13, and the anti-rotation key 12 is embedded in a second groove arranged in the screw rod 4, so that the screw rod 4, the anti-rotation key 12, the first gland 13 and the T-shaped mandrel 11 are connected into a whole.

In a possible implementation, the first entity 1 further comprises a first bolt 14; the first bolt 14 penetrates the first gland 13, and the lower end of the first bolt 14 is embedded into the upper surface of the head of the T-shaped mandrel 11. Specifically, a threaded hole penetrating through the first gland 13 is formed in the first gland 13, the threaded hole is matched with an external thread of the first bolt 14, a threaded hole with an upward opening is formed in the upper surface of the head of the T-shaped core shaft 11, the threaded hole is matched with the external thread of the first bolt 14, the first bolt 14 is screwed into the threaded hole formed in the first gland 13, the bottom of the first bolt 14 extends out of the threaded hole formed in the first gland 13, and the bottom of the first bolt 14 is screwed into the threaded hole formed in the upper surface of the head of the T-shaped core shaft 11, so that the first gland 13 is fixedly connected with the T-shaped core shaft 11 through the first bolt 14.

In a possible implementation, the first entity 1 comprises 2 first glands 13 and 2 first bolts 14. Wherein, a part of a first gland 13 close to the screw 4 is fixedly connected with the left part of a first anti-rotation key 12, so that the first gland 13 is integrally connected with the first anti-rotation key 12, and the first gland 13 is fixed at the left part of the head part of the T-shaped mandrel 11 through a first bolt 14; a portion of the other first pressing cover 13 adjacent to the screw 4 is fixedly connected to a right portion of the second anti-rotation key 12, so that the other first pressing cover 13 is integrally connected to the second anti-rotation key 12, and the other first pressing cover 13 is fixed to a right portion of the head of the T-shaped mandrel 11 by a first bolt 14.

When the screw rod 4 slides downwards, the T-shaped mandrel 11 is pushed to slide downwards through the bottom end of the screw rod 4, the anti-rotation key 12 and the first gland 13, and when the screw rod 4 slides upwards, the T-shaped mandrel 11 is pulled to slide upwards through the anti-rotation key 12 and the first gland 13.

The respective components in the second body 2 and the spring 3 are described below by (2.1) to (2.7) below.

(2.1) Sleeve 21

This sleeve 21 includes the cascaded chamber that holds, and this T shape dabber 11 cup joints in this cascaded chamber that holds, and this cascaded chamber that holds is used for providing sliding channel for this T shape dabber 11.

The sleeve 21 internally comprises a through hole, steps which are symmetrical left and right are arranged in the through hole, and the steps on any side are connected with the inner surface of the sleeve 21, so that the through hole becomes the stepped accommodating cavity.

A first accommodating cavity is formed between the upper surface of the step which is arranged in the through hole and is in bilateral symmetry to the uppermost edge of the through hole, and the first accommodating cavity is used for providing a sliding channel for the head part of the T-shaped core shaft 11. The diameter of the first accommodating cavity is larger than or equal to the diameter of the head of the T-shaped mandrel 11, so that the head of the T-shaped mandrel 11 can slide up and down in the first accommodating cavity.

The step of bilateral symmetry that sets up in this through-hole all has certain height and width to make and form a second between the step of bilateral symmetry and hold the chamber, this second holds the chamber and is used for providing sliding channel for the axle body of this T shape dabber 11, and the diameter that this second held the chamber can be more than or equal to the axle body diameter of this T shape dabber 11, so that the axle body of this T shape dabber 11 can hold the intracavity and slide from top to bottom at this second.

The diameter of the first accommodating cavity is larger than that of the second accommodating cavity, so that the first accommodating cavity and the second accommodating cavity form the stepped accommodating cavity.

It should be noted that the height of the stepped receiving cavity is greater than the height of the T-shaped mandrel 11, so that the T-shaped mandrel 11 can slide up and down in the stepped receiving cavity. Initially, the upper surface of the head of the T-shaped mandrel 11 is flush with the upper surface of the sleeve 21, the bottom end of the shaft body of the T-shaped mandrel 11 extends into the second accommodating cavity, but a target distance still exists between the bottom end of the shaft body and the bottom of the second accommodating cavity, and the target distance is a preset maximum sliding distance of the T-shaped mandrel 11, so that the subsequent shaft body of the T-shaped mandrel 11 slides up and down in the target distance in the second accommodating cavity. The target distance may be adjusted according to a specific implementation scenario, and the target distance is not specifically limited in the embodiment of the present application.

(2.2) second gland 23

In order to avoid the T-shaped mandrel 11 from slipping out of the sleeve 21 when sliding upwards, the second body 2 also comprises a second gland 23; the second gland 23 is located above the sleeve 21 and the head of the T-shaped mandrel 11, and the top end of the sleeve 21 is flush with the head of the T-shaped mandrel 11; the bottom end of the second gland 23 is fixedly connected with the top end of the sleeve 21.

Specifically, the lower surface of the second pressing cover 23 is fixedly connected with the upper surface of the sleeve 21, and the second pressing cover 23 covers the upper surface of the head of the T-shaped mandrel 11 to limit the T-shaped mandrel 11 from sliding out of the sleeve 21.

In a possible implementation, the second entity 2 further comprises a second bolt 27; the second bolt 27 penetrates the second pressing cover 23, and the lower end of the second bolt 27 is embedded into the upper surface of the sleeve 21. Specifically, a threaded hole penetrating through the second gland 23 is formed in the second gland 23, the threaded hole is matched with an external thread of the second bolt 27, a threaded hole with an upward opening is formed in the upper surface of the sleeve 21, the threaded hole is matched with the external thread of the second bolt 27, the second bolt 27 is screwed into the threaded hole formed in the second gland 23, the bottom of the second bolt 27 extends out of the threaded hole formed in the second gland 23, and the bottom of the second bolt 27 is screwed into the threaded hole formed in the upper surface of the sleeve 21, so that the second gland 23 is fixedly connected with the sleeve 21 through the second bolt 27.

In a possible implementation, the second entity 2 comprises 2 second glands 23 and 2 second bolts 27. Wherein a second pressing cover 23 is fixed to a left portion of the upper surface of the sleeve 21 by a second bolt 27; another second pressing cover 23 is fixed to a symmetrical right portion of the upper surface of the sleeve 21 by another second bolt 27.

(2.3) first bearing 24

In order to reduce the friction when the T-shaped mandrel 11 slides, the second body 2 further comprises a first bearing 24; the first bearing 24 is sleeved on the periphery of the head of the T-shaped mandrel 11 and is located in the sleeve 21. The first bearing 24 is used to provide a sliding channel for the head of the T-shaped mandrel 11.

The diameter of the through hole of the first bearing 24 is the diameter of the head of the T-shaped mandrel 11, so that the head of the T-shaped mandrel 11 is conveniently sleeved in the through hole of the first bearing 24.

The height of the first bearing 24 is the sum of the height of the head of the T-shaped mandrel 11 and the target distance, so that the head of the T-shaped mandrel 11 can slide up and down in the target distance in the first bearing 24, and the friction force of the head of the T-shaped mandrel 11 during sliding can be reduced.

(2.4) spring 3

A spring 3 is arranged between the head of the T-shaped mandrel 11 and the upper surface of the step of the stepped accommodating cavity. So that the T-shaped core shaft 11 can compress the spring 3 to slide downward during the downward sliding process, so that the elastic force of the spring 3 is increased on the step of the stepped receiving cavity, so that the elastic force of the spring 3 acts as a downward braking force to improve the braking force when the valve is closed.

In a possible realization, the automatic braking force compensator comprises 2 springs 3, the 2 springs 3 being respectively symmetrically arranged between the head of the T-shaped mandrel 11 and the upper surface of the step of the stepped housing cavity. For example, a spring 3 is provided between the lower surface of the head right portion of the T-shaped stem 11 and the upper surface of the right step of the stepped accommodation chamber; another spring 3 is provided between the lower surface of the left side portion of the head of the T-shaped stem 11 and the upper surface of the left side step of the stepped receiving chamber.

In a possible implementation manner, the spring 3 is a disc spring, but may be a spring with other shapes, and the shape of the spring 3 is not particularly limited in the embodiment of the present application.

(2.5) second bearing 26

In order to further reduce the friction force when the T-shaped mandrel 11 slides, the second body 2 further comprises a second bearing 26; the second bearing 26 is sleeved on the periphery of the lower end of the T-shaped mandrel 11 and is positioned in the inner surface of the step of the stepped accommodating cavity.

The second bearing 26 is sleeved in the second accommodating cavity of the stepped accommodating cavity. The diameter of the through hole of the second bearing 26 is the diameter of the shaft body of the T-shaped mandrel 11, so that the shaft body of the T-shaped mandrel 11 is sleeved in the through hole of the second bearing 26, and the lower end of the shaft body of the T-shaped mandrel 11 can slide up and down in the second bearing 26.

The height of the second bearing 26 is greater than or equal to the target distance, so that the bottom of the shaft body of the T-shaped mandrel 11 can slide up and down in the second bearing 26 within the target distance, and the friction force of the bottom of the shaft body of the T-shaped mandrel 11 during sliding can also be reduced.

(2.6) valve-stem joint 22

The top end of the valve rod connector 22 is fixedly connected with the lower surface of the step of the stepped accommodating cavity; an accommodating cavity is formed among the top end of the valve rod connector 22, the bottom end of the T-shaped mandrel 11 and the inner surface of the step, the bottom end of the T-shaped mandrel 11 extends into the accommodating cavity, and the accommodating cavity is used for providing a sliding channel for the bottom end of the T-shaped mandrel 11. This receiving chamber is also the first receiving chamber mentioned above.

In a possible implementation manner, the valve rod connector 22 is a cross-shaped valve rod connector, and a third groove with a downward opening is formed at the bottom end of the T-shaped mandrel 11; the top of the cross-shaped valve rod connector extends into the third groove, and the third groove is used for providing a sliding channel for the top of the cross-shaped valve rod connector.

The diameter of the third groove is equal to the diameter of the top of the cross-shaped valve rod connector, and when the T-shaped spindle 11 slides downwards, the top of the cross-shaped valve rod connector slides upwards in the third groove; when the T-shaped spindle 11 slides upwards, the top of the cross-shaped valve stem connector slides downwards in the third groove.

In a possible embodiment, the bottom end of the sleeve 21 is provided with a fourth recess which is open downwards and in which the shoulder of the cross-shaped valve stem connector engages. The bottom of the fourth groove may be a lower surface of the step of the stepped receiving cavity.

When the T-shaped mandrel 11 slides downwards, the head of the T-shaped mandrel 11 compresses the spring 3, the elastic force of the spring 3 acts on the step of the stepped accommodating cavity, so that the spring 3 pushes the sleeve 21 to slide downwards, and the sleeve 21 pushes the cross-shaped valve rod joint to slide downwards due to the fact that the cross-shaped valve rod joint is embedded into the fourth groove.

(2.7) third gland 25

The second entity 2 also comprises a third gland 25, and the third gland 25 is used for pressing the shoulder part of the cross-shaped valve rod joint into the fourth groove; the top end of the third gland 25 is fixedly connected with the bottom end of the sleeve 21, so that the sleeve 21 and the cross-shaped valve rod connector are fixedly connected into a whole by the third gland 25, and the cross-shaped valve rod connector is prevented from falling off from the sleeve 21 in the sliding process.

In a possible implementation, the second entity 2 further comprises a third bolt 28; the third bolt 28 penetrates the second pressing cover 23, and the lower end of the third bolt 28 is embedded into the lower surface of the sleeve 21. Specifically, a threaded hole penetrating through the third gland 25 is formed in the third gland 25, the threaded hole is matched with an external thread of the third bolt 28, a threaded hole with a downward opening is formed in the lower surface of the sleeve 21, the threaded hole is matched with the external thread of the third bolt 28, the third bolt 28 is screwed into the threaded hole formed in the third gland 25, the bottom of the third bolt 28 extends out of the threaded hole formed in the third gland 25, and the bottom of the third bolt 28 is screwed into the threaded hole formed in the lower surface of the sleeve 21, so that the third gland 25 is fixedly connected with the sleeve 21 through the third bolt 28.

In a possible implementation, the second entity 2 comprises 2 third glands 25 and 2 second bolts. Wherein a third gland 25 is fixed to a left portion of the upper surface of the sleeve 21 by a third bolt 28; another third gland 25 is fixed to a symmetrical right portion of the lower surface of the sleeve 21 by another third bolt 28.

In a possible implementation, the bottom end of the stem union 22 is fixedly connected to the top end of the stem 5 of the double gate valve.

In a possible implementation, the bottom end of the stem union 22 is provided with a fifth groove that opens downward, and the top end of the stem 5 is sleeved in the fifth groove.

In a possible implementation manner, the inner surface of the fifth groove is provided with an internal thread, the side surface of the top end of the valve rod 5 is provided with an external thread matched with the internal thread, and the top end of the valve rod 5 is screwed in the fifth groove, so that the valve rod 5 and the valve rod connector 22 are connected into a whole.

The automatic brake force compensator is sleeved in the bracket 6 of the double-gate valve. For example, fig. 3 is a schematic structural diagram of a dual-gate valve with an automatic brake force compensator installed therein according to an embodiment of the present application. In a possible realization, a guide groove is provided in the support 6, in which the automatic braking force compensator is mounted such that it can slide up and down.

During the closing process of the valve, the lead screw 4 slides downwards, the lead screw 4 pushes the T-shaped mandrel 11 to slide downwards, and thus the head of the T-shaped mandrel 11 downwards extrudes the spring 3; when the spring 3 is squeezed, the spring 3 pushes the sleeve 21 to slide downwards, the sleeve 21 pushes the valve rod connector 22 to slide downwards, the valve rod connector 22 pushes the valve rod 5 to slide downwards, and the valve rod 5 pushes the valve plate gate in the valve body of the double-gate valve to slide downwards, so that the valve is closed; after the valve closing action is finished, in order to avoid the situation that the valve plate brake is not closed in place or the brake force is insufficient, the screw rod 4 continues to slide downwards, so that the elastic force of the spring 3 is further increased, and the sleeve 21 further pushes the valve rod 5 to move downwards through the valve rod connector 22; when the valve plate gate is in place, the lead screw 4 continues to slide downwards to further compress the spring 3, and since the valve plate gate is in place, the sleeve 21 does not slide downwards under the action of the spring 3, and a gap is formed between the head of the T-shaped bearing and the second gland 23, for example, a structural schematic diagram of an automatic compensator for the braking force when the double-gate-plate gate valve is in a valve closing state is provided in the embodiment of the present application shown in fig. 4.

For the double-gate valve of B and C structure of installation tight power automatic compensator of floodgate, after the flashboard gate was closed, and the lumen of valve body lets in gas such as steam, the valve body temperature drops, the valve body shrink, although the temperature of lumen drops to some extent, but for exposing in the air, the temperature of valve rod 5 still can rise in the valve body, valve rod 5 inflation, thereby make valve rod 5 stretch out the length increase of valve body, at this moment, other parts compression spring 3 in the second entity 2 are driven to valve rod 5, so that spring 3 absorbs the displacement of giving away, thereby make tight power of floodgate change in reasonable within range, in order to prevent the too big damage and the card of opening the valve that cause of tight power of floodgate.

In the process of opening the valve, the screw rod 4 drives other components in the first entity 1 to slide upwards, at the moment, the pressure applied to the spring 3 is reduced, the spring 3 extends, after the head of the T-shaped bearing contacts the second gland 23, the T-shaped bearing drives the second entity 2 to move upwards together, the valve rod 5 in the second entity 2 is connected with the joint to drive the valve rod 5 to move upwards, and therefore the valve rod 5 drives the valve plate gate in the valve body to move upwards, and the valve opening action is achieved.

When the lead screw of double-gate valve is when the downward movement, T shape dabber compression spring among the tight power automatic compensator of floodgate that this application embodiment provided, under the effect of spring force, the spring promotes the sleeve and moves down to the sleeve passes through valve rod joint promotion valve rod and moves down, with the valve plate floodgate of closing double-gate valve, thereby makes the elasticity of spring convert the tight power of floodgate, in order to avoid appearing the valve plate floodgate and close not in place or the not enough condition of tight power of floodgate. And, when the brake tight power is too big, the valve rod moves the compression spring upwards to the spring absorbs the complimentary displacement, thereby makes the brake tight power change in reasonable scope, prevents the damage and the valve opening card that the brake tight power arouses and hinders. And, because the transmission efficiency of the screw assembly is not easy to calculate accurately, the actual braking force calculated based on the transmission efficiency of the screw assembly is also inaccurate, the compression amount of the spring can be measured, and the actual braking force calculated based on the compression amount of the spring is relatively accurate, so that the actual braking force is convenient to control.

The above description is only exemplary of the present application and should not be taken as limiting, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (10)

1. An automatic brake force compensator, characterized in that it comprises a first solid body (1), a second solid body (2) and a spring (3), said first solid body (1) comprising a T-shaped mandrel (11), said second solid body (2) comprising a sleeve (21) and a valve stem union (22), said sleeve (21) comprising a stepped housing cavity;

the top end of the T-shaped mandrel (11) is fixedly connected with the bottom end of a lead screw (4) of the double-gate-plate gate valve;

the T-shaped mandrel (11) is sleeved in the stepped accommodating cavity, and the stepped accommodating cavity is used for providing a sliding channel for the T-shaped mandrel (11);

a spring (3) is arranged between the head of the T-shaped mandrel (11) and the upper surface of the step of the stepped accommodating cavity;

the top end of the valve rod connector (22) is fixedly connected with the lower surface of the step;

a containing cavity is formed among the top end of the valve rod connector (22), the bottom end of the T-shaped mandrel (11) and the inner surface of the step, the bottom end of the T-shaped mandrel (11) extends into the containing cavity, and the containing cavity is used for providing a sliding channel for the bottom end of the T-shaped mandrel (11);

the bottom end of the valve rod joint (22) is fixedly connected with the top end of a valve rod (5) of the double-gate valve.

2. The automatic brake force compensator according to claim 1, wherein the head of the T-shaped mandrel (11) is provided with a first groove opening upwards, into which the bottom end of the lead screw (4) is embedded.

3. The automatic brake force compensator according to claim 1, characterized in that the first entity (1) further comprises an anti-rotation key (12) and a first gland (13);

a second groove with an outward opening is formed in the side face of the lead screw (4), the part, close to the lead screw (4), of the anti-rotation key (12) is embedded into the second groove, and the part, far away from the lead screw (4), of the anti-rotation key (12) is fixedly connected with the part, close to the lead screw (4), of the first gland (13);

the bottom end of the first gland (13) is fixedly connected with the head of the T-shaped mandrel (11).

4. Automatic brake force compensator according to any of claims 1-3, characterized by the second entity (2) further comprising a second gland (23);

the second gland (23) is positioned above the sleeve (21) and the head of the T-shaped mandrel (11), and the top end of the sleeve (21) is flush with the head of the T-shaped mandrel (11);

the bottom end of the second gland (23) is fixedly connected with the top end of the sleeve (21).

5. The automatic brake force compensator according to claim 4, characterized in that the second entity (2) further comprises a first bearing (24);

the first bearing (24) is sleeved on the periphery of the head of the T-shaped mandrel (11) and is positioned in the sleeve (21).

6. The automatic brake force compensator according to claim 4, wherein the valve rod connector (22) is a cross-shaped valve rod connector, and a third groove with a downward opening is formed at the bottom end of the T-shaped mandrel (11);

the top of cross valve rod joint stretches into in the third recess, the third recess is used for doing the top of cross valve rod joint provides sliding channel.

7. The automatic braking force compensator according to claim 6, wherein the bottom end of the sleeve (21) is provided with a fourth groove which is opened downwards, and the shoulder part of the cross-shaped valve rod connector is embedded in the fourth groove.

8. The automatic brake force compensator according to claim 7, characterized in that the second entity (2) further comprises a third gland (25);

the third gland (25) is used for pressing the shoulder part of the cross-shaped valve rod joint into the fourth groove;

the top end of the third gland (25) is fixedly connected with the bottom end of the sleeve (21).

9. The automatic brake force compensator according to claim 4, characterized in that the second body (2) further comprises a second bearing (26);

the second bearing (26) is sleeved on the periphery of the lower end of the T-shaped mandrel (11) and is positioned in the inner surface of the step.

10. The automatic brake force compensator according to claim 4, characterized in that it is sleeved inside the support (6) of the double-gate valve.

Images