CN218093715U - Double-cavity linear driving cylinder - Google Patents

Abstract

The utility model relates to a double-cavity linear driving cylinder, which is characterized in that an auxiliary piston and an auxiliary piston rod are arranged in a main cylinder body; a driving cavity is arranged between the auxiliary piston and the main piston; the driving cavity is communicated with the driving fluid station through the main pressure fluid inlet; the auxiliary piston rod penetrates through the rear cylinder cover, and the keeping part of the auxiliary piston rod is positioned outside the rear cylinder cover; a second cylinder body is arranged outside the rear cylinder cover, and the part of the auxiliary piston rod, which is positioned outside the rear cylinder cover, is completely positioned in the second cylinder body; the tail end of the second cylinder body is sealed through a third cylinder cover; a fast propulsion chamber is formed in the second cylinder body and communicated with a driving fluid station through a driving fluid inlet; the diameter of the inner cavity of the second cylinder body is smaller than or equal to that of the inner cavity of the main cylinder body. The utility model discloses an add and impel sharp actuating cylinder fast, improve the functioning speed when idle or low merit stroke to reduced the fluid quantity, thereby improve equipment operating efficiency, reduced the consumption of drive fluid station.

Description

Double-cavity linear driving cylinder

Technical Field

The utility model relates to a carry out sharp driven pneumatic cylinder or cylinder has 2 independent drive cavities, belongs to the mechanical drive component field.

Background

In the field of mechanical equipment, hydraulic or pneumatic cylinders are often used to perform linear drives, which may be collectively referred to as linear drive cylinders. The main components of the linear driving cylinder comprise a cylinder body, a piston and a piston rod; a cylindrical piston is arranged in a cylindrical cylinder body, a piston rod is arranged on one side of the piston, the piston rod penetrates through a cylinder cover at the end part of the cylinder body, and the piston rod is exposed out of the cylinder body and serves as a linear driving element; hydraulic oil or air is injected into the cylinder body on one side of the piston to drive the piston to linearly move along the cylinder body, so that the piston rod is driven to linearly move.

Since the cylinder and the piston are both cylindrical and have fixed areas, the sectional area of the piston and the cylinder cavity is increased to obtain a larger driving force under the same driving pressure (the same driving oil pressure or driving air pressure), so that a larger amount of driving fluid (oil or air) is required.

In a gantry shear (refer to a gantry shear with the Chinese patent publication No. CN206509581U, a double-edge shearing gantry shear with the Chinese patent publication No. CN214264056U, and the like), a hydraulic packer (refer to a horizontal hydraulic full-automatic packer with the Chinese patent publication No. CN1765617A, a hydraulic packer with a mandril with the Chinese patent publication No. CN216659013U, and the like), even a press, and the like, a linear driving cylinder is adopted as a device of the linear driving element, in the pressurizing working process of the linear driving cylinder, the front very long stroke is a reactive or low-power stroke, and the last stroke is a stroke requiring large pressure.

Although the working stroke of large pressure is short, the mechanical equipment is limited by the structure of the existing linear driving cylinder, and only a large-power linear driving cylinder with a full-length large-size piston can be adopted; although most of the stroke of the linear drive cylinder does not generate a large driving pressure, which is required by the operating space of the equipment or the operating characteristics of the product, a large amount of driving fluid has to be injected to move the piston rod to the final working area.

When the working efficiency of the equipment is required to be improved, the flow rate of the driving fluid needs to be increased, the injection speed needs to be increased, the production fluid speed of a driving fluid station (a hydraulic station or an air pressure pump) needs to be increased, and the cost of the equipment is increased.

The problem which puzzles mechanical equipment research personnel who use linear driving cylinder product for a long time is along with market's demand increase to equipment operating efficiency promotion to and the demand increase to equipment energy consumption reduction, it is necessary to improve the structure of sharp cylinder body to both reduce the energy consumption, improve drive speed again, improve the operating efficiency of the equipment that linear driving cylinder belongs to.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a two-chamber straight line actuating cylinder improves straight line actuating cylinder at idle or the functioning speed of low-power stroke, reduces the fluid quantity to improve equipment operating efficiency reduces the consumption of drive fluid station.

In order to achieve the purpose of the utility model, the utility model provides a double-cavity linear driving cylinder, which comprises a main cylinder body, a front cylinder cover, a rear cylinder cover, a main piston rod and a return fluid inlet;

the section size of the main piston is matched with the inner section of the cylinder body, and the main piston divides the inner cavity of the main cylinder body into two parts; a return cavity is formed between the main piston and the front cylinder cover and is communicated with the return fluid inlet;

the main piston rod is connected to the main piston and is partially positioned in the return cavity; the main piston rod penetrates through the front cylinder cover, and the retaining part is positioned outside the front cylinder cover; the part of the main piston rod, which is positioned outside the front cylinder cover, is a working part;

an auxiliary piston and an auxiliary piston rod are also arranged in the main cylinder body;

the section size of the auxiliary piston is matched with that of the inner cavity of the main cylinder body, the auxiliary piston is arranged in parallel with the main piston, and a driving cavity is formed between the auxiliary piston and the main piston; the drive chamber is communicated with the drive fluid station through a main pressure fluid inlet;

a first rod cavity is formed between the auxiliary piston and the rear cylinder cover along the main cylinder body; the first rod cavity is communicated with the outside;

the auxiliary piston rod is connected to the auxiliary piston, and the part of the auxiliary piston rod is positioned in the first rod cavity;

the auxiliary piston rod penetrates through the rear cylinder cover, and the keeping part of the auxiliary piston rod is positioned outside the rear cylinder cover;

a second cylinder body is arranged outside the rear cylinder cover, and the part of the auxiliary piston rod, which is positioned outside the rear cylinder cover, is completely positioned in the second cylinder body; the tail end of the second cylinder body is sealed by a third cylinder cover;

a rapid propelling cavity is formed in the second cylinder body, a driving fluid inlet is formed in the second cylinder body or the third cylinder cover, and the rapid propelling cavity is communicated with the driving fluid inlet;

the rapid propulsion chamber is communicated with a driving fluid station through the driving fluid inlet;

the second cylinder body, the auxiliary piston rod in the second cylinder body and the quick propelling cavity jointly form a quick propelling linear driving cylinder;

the diameter of the inner cavity of the second cylinder body is smaller than or equal to that of the inner cavity of the main cylinder body.

As a further improvement of the utility model, the second cylinder body and the auxiliary piston rod therein form a plunger cylinder;

the quick propelling cavity is located in the whole second cylinder body.

As a further improvement of the utility model, the end part of the auxiliary piston rod, which is positioned at the second cylinder body, is provided with a quick-push piston;

the section size of the quick-push piston is matched with the section size of the inner cavity of the second cylinder body;

a quick pushing cavity is formed between the quick pushing piston and the third cylinder cover along the second cylinder body;

a second rod cavity is formed between the quick-push piston and the rear cylinder cover along the second cylinder body; the second rod cavity is communicated with the outside.

As a further improvement of the present invention, the main pressure fluid inlet is formed by disposing a first main pressure fluid channel in the auxiliary piston rod, and the first main pressure fluid channel penetrates through the auxiliary piston and is communicated with the driving cavity;

a main pressure fluid injection pipe is arranged in the second cylinder body, and a fluid channel is arranged in the main pressure fluid injection pipe;

the first primary pressure fluid passageway communicates with a drive fluid station through the primary pressure fluid injection tube.

Further, the main pressure fluid injection pipe is a hard pipeline;

one end of the main pressure fluid injection pipe is fixed on the third cylinder cover, and a fluid inlet port is formed in the third cylinder cover;

the other end of the main pressure fluid injection pipe is inserted into the first main pressure fluid channel; a sliding seal is disposed between the outer wall of the primary pressure fluid injection tube and the inner wall of the first primary pressure fluid passageway.

Further, the main pressure fluid injection pipe is a hose;

one end of the main pressure fluid injection pipe is fixed on the third cylinder cover or the wall surface of the second cylinder body;

the other end of the main pressure fluid injection pipe is connected with the first main pressure fluid channel of the auxiliary piston rod.

As a further improvement of the present invention, the main pressure fluid inlet is formed by arranging a second main pressure fluid channel in the main piston rod;

the second main pressure fluid channel penetrates through the main piston and is communicated with the driving cavity;

the inlet of the second main pressure fluid passage is located on the portion of the main piston rod outside the front cylinder head.

Further, the inlet of the second main pressure fluid passage is located on the rod body surface in front of the protruding end of the main piston rod.

As a further improvement of the utility model, a third main pressure fluid interface is arranged on the cylinder body; when the drive cavity moves to the third main pressure fluid interface, drive fluid may be injected into the drive cavity through the third main pressure fluid interface.

As a further improvement of the utility model, a support is arranged between the auxiliary piston and the main piston;

the driving cavity is always arranged between the auxiliary piston and the main piston;

when the volume of the driving cavity is minimum, the support is abutted between the auxiliary piston and the main piston;

when the volume of the driving cavity is minimum, the area of the contact surface between the driving cavity and the main piston reserved between the auxiliary piston and the main piston is larger than or equal to the effective fluid pushing area of the rapid propelling cavity.

The double-cavity linear driving cylinder of the utility model is additionally provided with the auxiliary piston and the auxiliary piston rod in the main cylinder body; the auxiliary piston rod penetrates through a rear cylinder cover at the tail end of the main cylinder body; a second cylinder body is additionally arranged outside the rear cylinder cover, and the part of the auxiliary piston rod, which is positioned outside the rear cylinder cover, is completely positioned in the second cylinder body; the tail end of the second cylinder body is sealed through a third cylinder cover; the second cylinder body and the auxiliary piston rod form a rapid propelling linear driving cylinder, driving fluid is injected into the second cylinder body by reducing the driving area, so that the rapid movement of the auxiliary piston rod is realized, the auxiliary piston is driven, the main piston is pushed to rapidly move along the main cylinder body, and the rapid extension of the main piston rod is finally realized; when large driving pressure is needed, the quick propelling cavity in the second cylinder is sealed, then driving fluid is injected into the driving cavity between the auxiliary piston and the main piston through the main pressure fluid inlet, and large driving pressure can be generated due to the large size of the main piston.

The utility model discloses a two-chamber linear drive jar, through the overall structure's to the linear drive jar improvement, through addding the rapid propulsion linear drive jar, improves the functioning speed when idle or low power stroke to reduced the fluid quantity, thereby improve equipment operating efficiency, reduced the consumption of drive fluid station.

Drawings

FIG. 1 is a schematic view of the overall structure of a first embodiment of the dual-chamber linear driving cylinder of the present invention;

FIG. 2 is a schematic view of the overall structure of a second embodiment of the dual-chamber linear driving cylinder of the present invention;

fig. 3 is a schematic structural view of a main pressure fluid inlet arrangement mode 1 of the present invention;

fig. 4 is a schematic structural view of the main pressure fluid inlet arrangement modes 2 and 3 of the present invention;

fig. 5 is a labeled diagram of internal cross-sectional parameters of a first embodiment of the present invention;

fig. 6 is a labeled diagram of internal cross-sectional parameters of a second embodiment of the present invention;

fig. 7 (a), 7 (b) and 7 (c) are schematic diagrams of the operation process of the first embodiment of the present invention;

fig. 8 (a), 8 (b) and 8 (c) are schematic diagrams of the operation process of the second embodiment of the present invention;

fig. 9 is a schematic view of the arrangement of the reserved driving cavity of the present invention;

reference numerals are as follows: a main cylinder body 101, a front cylinder cover 102 and a rear cylinder cover 103; a second cylinder 104, a third cylinder cover 105;

a return cavity 1, a driving cavity 2 and a reserved driving cavity 21; a first rod chamber 3; a fast propulsion chamber 4 and a second rod chamber 5;

a primary pressure fluid inlet 6, a first primary pressure fluid channel 61, a primary pressure fluid injection tube 62, a second primary pressure fluid channel 63, a third primary pressure fluid interface 64;

a main piston 7, a main piston rod 8; an auxiliary piston 9, an auxiliary piston rod 10; a quick push piston 11; a second interface 12;

a drive fluid inlet 13; a first port 14, a return fluid inlet 15.

Detailed Description

The following describes the embodiments of the present invention in further detail with reference to the accompanying drawings.

As shown in fig. 1 and fig. 2, the two-chamber linear driving cylinder is a schematic diagram of the overall structure of the dual-chamber linear driving cylinder of the present invention, and has two embodiments; compared with a common piston type linear driving cylinder, the piston type linear driving cylinder also comprises a main cylinder body 101, a front cylinder cover 102, a rear cylinder cover 103, a main piston 7, a main piston rod 8, a first interface 14 and a return fluid inlet 15; the cross-sectional dimension of the main piston 7 matches the inner cross-section of the main cylinder 101, and the main piston 7 divides the inner cavity of the main cylinder 101 into two parts, namely a return chamber 1, which communicates with the return fluid inlet 15, and a drive chamber 2.

The improvement of the utility model is that an auxiliary piston 9 is arranged in the original driving cavity 2, and an auxiliary piston rod 10 is connected on the auxiliary piston 9; the auxiliary piston rod 10 penetrates through the rear cylinder cover 103; a first rod cavity 3 is formed between the auxiliary piston 9 and the rear cylinder cover 103 along the main cylinder body 101, the auxiliary piston rod 10 is arranged in the first rod cavity 3, and the first rod cavity 3 is communicated with the first interface 14.

The driving cavity 2 is arranged between the main piston 7 and the auxiliary piston 9, and the driving cavity 2 is communicated with a driving fluid station through a main pressure fluid inlet 6.

A second cylinder body 104 is arranged outside the rear cylinder cover 103, and the part of the auxiliary piston rod 10, which is positioned outside the rear cylinder cover 103, is completely positioned in the second cylinder body 104; the end of the second cylinder block 104 is closed by a third cylinder head 105;

a fast propulsion chamber 4 is formed in the second cylinder 104, a driving fluid inlet 13 is arranged on the second cylinder 104 or the third cylinder cover 105, and the fast propulsion chamber 4 is communicated with the driving fluid inlet 13.

Fig. 1 is a schematic structural diagram of a first embodiment of the dual-cavity linear driving cylinder of the present invention, in which the auxiliary piston rod 10 forms a plunger cylinder structure in the second cylinder body 104.

Fig. 2 is a schematic structural diagram of a second embodiment of the dual-cavity linear driving cylinder of the present invention, wherein the secondary piston rod 10 forms a piston-cylinder structure in the second cylinder 104; therefore, a quick-push piston 11 is arranged at the tail end of the auxiliary piston rod 10; the fast-pushing cavity 4 is arranged between the fast-pushing piston 11 and the third cylinder cover 105; a second rod cavity 5 is formed between the quick-push piston 11 and the rear cylinder cover 103 along the second cylinder body 104; the second cylinder 104 is provided with a second port 12, and the second port 12 is communicated with the second rod chamber 5.

As shown in fig. 1, 2, and 3, the primary pressure fluid inlet 6 is provided in a manner 1 such that a first primary pressure fluid passage 61 is provided in the secondary piston rod 10, penetrates the secondary piston 9, and communicates with the drive chamber 2; a main pressure fluid injection pipe 62 is arranged in the second cylinder 104, and a fluid passage is arranged in the main pressure fluid injection pipe 62; one end of the main pressure fluid injection pipe 62 is inserted into the first main pressure fluid passage 61 and is always held in the first main pressure fluid passage 61, and the other end of the main pressure fluid injection pipe 62 is fixed to the third cylinder head 105, and a main pressure fluid injection port provided in the third cylinder head 105 is used to inject a fluid into the main pressure fluid injection pipe 62 and into the drive chamber 2 through the first main pressure fluid passage 61.

Of course, the primary pressure fluid injection pipe 62 may also be a flexible pipe (compressible or coiled), and an inlet of the first primary pressure fluid channel 61 on the secondary piston rod 10 is connected to the primary pressure fluid injection port on the third cylinder head 105, so as to inject fluid from the primary pressure fluid injection port on the third cylinder head 105, and finally enter the driving chamber 2 through the first primary pressure fluid channel 61.

As shown in fig. 4, the main pressure fluid inlet 6 may also be arranged in other ways:

the main pressure fluid inlet 6 is arranged in a manner 2 that a second main pressure fluid channel 63 is arranged in the main piston rod 8, penetrates through the main piston 7 and is communicated with the driving cavity 2; the inlet of the second main pressure fluid channel 63 is preferably located on the rod body of the main piston rod 8 outside the front cylinder head 102, not on the end face, since the end of the main piston rod 8 generally needs to be connected to the working part of the equipment.

The main pressure fluid inlet 6 is arranged in a mode 3 that a third main pressure fluid connector 64 is arranged on the main cylinder body 101; when the drive chamber 2 is moved to the third main pressure fluid port 64, drive fluid may be injected into the drive chamber 2 through the third main pressure fluid port 64.

As shown in fig. 5 and fig. 6, the parameters of the internal cross section of the dual-chamber linear driving cylinder of the present invention are labeled as follows:

(1) A = the cross-sectional area of the inner cavity of the main cylinder 101 = the cross-sectional area of the main piston 7 = the cross-sectional area of the auxiliary piston 9;

(2) B = cross-sectional area of the secondary piston rod 10; b < A;

(3) C = cross-sectional area of the main piston rod 8; c < A;

(4) D = cross-sectional area of main pressure fluid injection tube 62; d < B

(5) E = the cross-sectional area of the second cylinder 104 = the cross-sectional area of the quick-push piston 11; e is less than or equal to A; e > B > D;

(6) S1= cross-sectional area of the return chamber 1= a-C;

(7) S2= the cross-sectional area of the drive cavity 2= a;

(8) S3= effective fluid propelling area of fast propulsion chamber 4 = B-D (embodiment one, plunger cylinder, as shown in fig. 5);

or = E-D (embodiment two, piston cylinder, as shown in fig. 6).

When the double-cavity linear driving cylinder is used, the main cylinder body 101 is preferably fixed on a frame of target equipment, and then the end part of the main piston rod 8 is connected with the working part of the equipment;

the output flow rate of the drive fluid station is Q (m) ³ /s) and an output pressure of P (Pa).

In the following process, the effects of friction, resistance, and the like of each part are not considered for the moment;

the main pressure fluid inlet 6 is set in the setting mode 1, and the main pressure fluid injection pipe 62 is a hard pipe.

As shown in fig. 7 (a), 7 (b), and 7 (c), the first embodiment of the linear actuator of the present invention specifically operates as follows:

a, a rapid stretching process; as shown in fig. 7 (a);

the driving fluid inlet 13 is communicated with a driving fluid station and is used for injecting driving fluid;

the main pressure fluid inlet 6 is closed;

if liquid exists in the return cavity 1, the return fluid inlet 15 is communicated with an oil return pipeline;

if no liquid exists in the return cavity 1, the return fluid inlet 15 is kept in an open state, so that the return cavity 1 is communicated with the outside;

if liquid exists in the first rod cavity 3, the first connector 14 is communicated with an oil return pipeline;

if no liquid exists in the first rod chamber 3, the first interface 14 is kept in an open state, so that the first rod chamber 3 is communicated with the outside;

a driving fluid is injected into the second cylinder 104 to provide a driving force to the auxiliary piston rod 10;

at this time, the space of the driving cavity 2 is very small or even not available; the auxiliary piston rod 10 drives the auxiliary piston 9 to move directly or push the main piston 7 to move through residual fluid in the driving cavity 2, and finally drives the main piston rod 8 to extend out;

the moving distance of the main piston 7, the main piston rod 8, the auxiliary piston 9 and the auxiliary piston rod 10 is La;

phase a of the main piston rod 8:

operating speed Va = Q ÷ S3;

protracted elapsed time Ta = La ÷ Va = La × S3 ÷ Q;

pressure Fa = P × S3;

the driving fluid dosage Ma = La × S3.

b, a main pressing process; as shown in fig. 7 (b) and 7 (c);

when the output pressure needs to be increased after the main piston rod 8 extends out by the distance La,

the driving fluid inlet 13 is disconnected from the driving fluid station and kept closed, so that the fluid amount in the quick propelling cavity 4 is kept constant;

the main pressure fluid inlet 6 is opened and communicated with a driving fluid station, and driving fluid is injected into the driving cavity 2;

the return fluid inlet 15 and the first interface 14 are kept in the original state;

driving fluid is injected into the driving cavity 2 to directly provide driving force for the main piston 7, and the main piston 7 is driven to continue to move towards the working direction, namely the main piston rod 8 is driven to continue to extend until the main piston rod 8 extends to a specified position or completely extends out;

at this time, the driving fluid in the driving chamber 2 also applies pressure to the secondary piston 9;

when the fluid in the fast propulsion chamber 4 is hydraulic oil, that is, the second cylinder 104 is a hydraulic ram cylinder, the volume of the fluid in the fast propulsion chamber 4 is not substantially compressed, so that the size of the fast propulsion chamber 4 is not changed, and the secondary piston 9 can still be kept at the position of the extending distance La.

When the fluid in the fast propulsion chamber 4 is compressed air, the volume of the fluid in the fast propulsion chamber 4 is compressed, so that the pressure in the fast propulsion chamber 4 is increased until the balance of the two sides of the secondary piston 9 is achieved, the size of the fast propulsion chamber 4 is reduced, and the extension distance of the secondary piston 9 is retracted and is smaller than La.

Here, the second cylinder 104 is exemplified by a hydraulic ram cylinder, without additionally estimating the compression of the fluid volume inside the fast propulsion chamber 4:

the moving distance of the main piston 7 and the main piston rod 8 is Lb;

b-phase of the main piston rod 8:

operating speed Vb = Q ÷ S2;

protracted elapsed time Tb = Lb ÷ Vb = Lb × S2 ÷ Q;

pressure Fb = P × S2;

the driving fluid usage Mb = Lb × S2.

The utility model discloses a under two-chamber linear drive jar embodiment mode state, stretching out of whole piston rod is consuming time:

T＝Ta+Tb＝(La×S3+Lb×S2)÷Q；

the driving fluid usage M = Ma + Mb = La × S3+ Lb × S2.

If the existing linear driving cylinder is adopted: the extending speed V' = Q ÷ S2 of the piston rod;

running the entire piston rod extension takes time:

T`＝(La+Lb)÷V`＝(La×S2+Lb×S2)÷Q；

the driving fluid amount M' = La × S2+ Lb × S2.

In the first state of the double-cavity linear driving cylinder of the utility model, compared with the prior linear driving cylinder,

saving the time spent on reaching Δ T = T' -T = ((La × S2+ Lb × S2) - (La × S3+ Lb × S2)) ÷ Q = La × (S2-S3) ÷ Q = La × (a- (B-D))/;

the injection-saving driving fluid dosage Δ M = M' -M = (La × S2+ Lb × S2) - (La × S3+ Lb × S2) = La × (S2-S3) = La × (a- (B-D));

namely, when the moving distance La in the stage a (idle or low power stroke) is longer, and the effective fluid pushing area S3 of the fast propelling cavity 4 is smaller (the cross-sectional area B of the auxiliary piston rod 10 is smaller, or the cross-sectional area D of the main pressure fluid injection pipe 62 is larger), the more time is consumed for extension and the more the amount of the injected driving fluid is saved (the less the amount of the driving fluid is used), the more the synergy of the linear driving cylinder is obvious; but correspondingly, the driving pressure Fa at the stage a is also reduced.

As shown in fig. 8 (a), 8 (b), and 8 (c), the second embodiment of the linear actuator of the present invention has the following specific operation steps:

a, a rapid stretching process; as shown in fig. 8 (a);

the driving fluid inlet 13 is communicated with a driving fluid station and is used for injecting driving fluid;

the main pressure fluid inlet 6 is closed;

if liquid exists in the return cavity 1, the return fluid inlet 15 is communicated with an oil return pipeline;

if no liquid exists in the return cavity 1, the return fluid inlet 15 is kept in an open state, so that the return cavity 1 is communicated with the outside;

if the first rod cavity 3 contains liquid, the first interface 14 is communicated with an oil return pipeline;

if no liquid exists in the first rod chamber 3, the first interface 14 is kept in an open state, so that the first rod chamber 3 is communicated with the outside;

if liquid exists in the second rod cavity 5, the second connector 12 is communicated with an oil return pipeline;

if no liquid exists in the second rod cavity 5, the second interface 12 is kept in an open state, so that the first rod cavity 3 is communicated with the outside;

the first rod cavity 3 is communicated with the second rod cavity 5 or is divided to keep mutually independent;

a driving fluid is injected into the fast propelling cavity 4 of the second cylinder 104 to provide a driving force for the fast propelling piston 11, so as to drive the auxiliary piston rod 10 to move;

at this time, the space of the driving cavity 2 is very small or even not available; the auxiliary piston rod 10 drives the auxiliary piston 9 to move directly or push the main piston 7 to move through residual fluid in the driving cavity 2, and finally drives the main piston rod 8 to extend out;

the moving distance of the main piston 7, the main piston rod 8, the auxiliary piston 9, the auxiliary piston rod 10 and the fast push piston 11 is La;

phase a of the main piston rod 8:

operating speed Va = Q ÷ S3;

protracted elapsed time Ta = La ÷ Va = La × S3 ÷ Q;

pressure Fa = P × S3;

the driving fluid dosage Ma = La × S3.

b, main pressure process; as shown in fig. 8 (b) and 8 (c);

when the output pressure needs to be increased after the main piston rod 8 extends out by the distance La,

the driving fluid inlet 13 is disconnected from the driving fluid station and kept closed, so that the amount of fluid in the quick propelling cavity 4 is kept unchanged;

the main pressure fluid inlet 6 is opened and communicated with a driving fluid station, and driving fluid is injected into the driving cavity 2;

the return fluid inlet 15, the first interface 14 and the second interface 12 are kept in the original state;

driving fluid is injected into the driving cavity 2 to directly provide driving force for the main piston 7, and the main piston 7 is driven to continue to move towards the working direction, namely the main piston rod 8 is driven to continue to extend until the main piston rod 8 extends to a specified position or completely extends out;

at this time, the driving fluid in the driving chamber 2 also applies pressure to the secondary piston 9;

when the fluid in the fast propulsion chamber 4 is hydraulic oil, that is, the second cylinder 104 is a hydraulic piston cylinder, the volume of the fluid in the fast propulsion chamber 4 is not substantially compressed, so that the size of the fast propulsion chamber 4 is not changed, and the auxiliary piston 9, the auxiliary piston rod 10, and the fast propulsion piston 11 can still remain at the extending distance position of La.

When the fluid in the fast propulsion chamber 4 is compressed air, the volume of the fluid in the fast propulsion chamber 4 is compressed, so that the pressure in the fast propulsion chamber 4 is increased until the balance of the two sides of the auxiliary piston 9 is achieved, the size of the fast propulsion chamber 4 is reduced, and the extending distances of the auxiliary piston 9, the auxiliary piston rod 10 and the fast propulsion piston 11 are retracted and smaller than La.

Here, the second cylinder 104 is exemplified by a hydraulic piston cylinder, without additionally evaluating the compression of the fluid volume inside the fast propulsion chamber 4:

the moving distance of the main piston 7 and the main piston rod 8 is Lb;

b-stage of the main piston rod 8:

operating speed Vb = Q ÷ S2;

protracted elapsed time Tb = Lb ÷ Vb = Lb × S2 ÷ Q;

pressure Fb = P × S2;

the driving fluid usage Mb = Lb × S2.

The utility model discloses a under two-chamber linear drive jar embodiment two states, stretching out of whole piston rod is consuming time:

T＝Ta+Tb＝(La×S3+Lb×S2)÷Q；

the driving fluid usage M = Ma + Mb = La × S3+ Lb × S2.

In the second state of the double-cavity linear driving cylinder of the utility model, compared with the prior linear driving cylinder,

saving the time spent reaching Δ T = T' -T = ((La × S2+ Lb × S2) - (La × S3+ Lb × S2))/. Q = La × (S2-S3)/. Q = La × (a- (E-D))/. Q;

the injection-saving driving fluid dosage Δ M = M' -M = (La × S2+ Lb × S2) - (La × S3+ Lb × S2) = La × (S2-S3) = La × (a- (E-D));

namely, when the moving distance La in the stage a (idle or low power stroke) is longer, and the effective fluid pushing area S3 of the fast propelling cavity 4 is smaller (the cross-sectional area E of the fast propelling piston 11 is smaller, or the cross-sectional area D of the main pressure fluid injection pipe 62 is larger), the more the stretching time is saved, the more the amount of the injected driving fluid is saved (the less the amount of the driving fluid is used), the more the synergy of the linear driving cylinder is obvious; but correspondingly, the driving pressure Fa at the stage a is also reduced.

When the linear driving cylinder of the utility model is used, the efficiency is further improved; when the working pressure requirement of the stage a of the target equipment is extremely low, even only idle stroke is required, the first driving fluid station with large output flow and low output pressure can be adopted for driving, and rapid extension is emphasized; when the phase b is entered, the second driving fluid station with high output pressure is switched to drive, and high-pressure operation is emphasized. By arranging 2 driving fluid stations with different output performances, the working efficiency can be further improved, and the comprehensive energy consumption of the driving fluid stations and even the comprehensive purchase cost of the driving fluid stations are expected to be reduced.

The utility model discloses a during the linear drive jar used, when the a stage passes through the b stage, if vice piston 9 with between the main piston 7 drive chamber 2 undersize, do not have at all even, often can influence the production of subsequent main pressure process's pressure Fb, so begin at the a stage, or the in-process, required operating pressure is less hour (working resistance is less promptly), can set up piston separation process, makes the main pressure fluid entry 6 communicates with each other with the drive fluid station is short for a short time, pours into the drive fluid into, forms drive chamber 2. Or, a support (which may be a raised ring surface, a raised cylinder, or even a raised grain; which may be formed by removing material on the end surface of the piston in a milling manner; or by installing a raised object on the end surface of the piston) is provided between the secondary piston 9 and the primary piston 7, so that the two are separated at least by a certain distance, and the driving cavity 2 always exists.

As shown in fig. 9, a recess is formed in the middle of the end of the secondary piston 9 to form a reserved driving cavity 21, a supporting body is formed on the periphery of the reserved driving cavity 21, and when the primary pressure fluid inlet 6 is opened, the supporting body on the periphery of the reserved driving cavity 21 can be abutted against the primary piston 7, so as to directly push the primary piston 7; the main pressure fluid inlet 6 is preferably in the form of a first main pressure fluid channel 61, and the area S4 of the contact surface of the reserved driving chamber 21 and the main piston 7 is greater than or equal to the effective fluid pushing area S3 of the fast propulsion chamber 3.

Further, based on the above embodiment, a recess may also be provided at the end of the master piston 7; the recess may not be located entirely in the middle of the piston, e.g. offset to one side; the depressions may also not be present completely in the form of circular depressions, such as rectangular, oval, or even irregular shapes; the recess may also be communicated with the inner wall of the main cylinder 101, so that the main pressure fluid inlet 6 is arranged in the arrangement mode 3, that is, the main cylinder 101 is provided with a third main pressure fluid port 64, and the driving fluid is injected into the reserved driving cavity 21 through the third main pressure fluid port 64.

That is, when the linear driving cylinder of the present invention is applied to the field requiring continuous increasing of output pressure such as a hydraulic packing machine (a horizontal hydraulic full-automatic packing machine with chinese patent publication No. CN 1765617A), the linear driving cylinder of the present invention operates first in the fast stretching process at stage a, and the auxiliary piston 9 pushes the main piston 7 to move forward through the supporting body on the periphery of the reserved driving cavity 21; when the stage a is transited to the stage b, the driving fluid is directly injected into the reserved driving cavity 21 through the first main pressure fluid channel 61, at this time, because S4 is larger than or equal to S3, the driving pressure Fa which is larger than the driving pressure Fa in the rapid extension process of the stage a is also generated in an instant, the main piston 7 can be directly pushed, once the driving cavity 2 is formed, the output driving pressure is also increased to Fb, and the main pressure process of the stage b is entered.

In the above process, the main pressure fluid inlet 6 preferably adopts the form of the first main pressure fluid channel 61, which can ensure that the driving fluid can smoothly enter the reserved driving cavity 21 and can maximize the area of the driving cavity 2 at the side of the main piston 7.

The utility model discloses a linear drive cylinder, when La distance at every turn is fixed, then drive chamber 2 is in initial position on the main cylinder body 101 is also fixed, then main pressure fluid entry 6 can adopt the mode that sets up of third main pressure fluid interface 64, predetermines on the main cylinder body 101 (this moment, main piston 7 with vice piston 9 need keep sufficient interval, forms drive chamber 2 makes things convenient for when drive fluid injects through third main pressure fluid interface 64, directly can produce Fb's pressure, avoids because of effective area is not enough, and the resistance is too big, causes unable timely parturition main piston 7 with vice piston 9 forms drive chamber 2), its advantage third main pressure fluid interface 64 can be fixed along with main cylinder body 101 together.

Alternatively, when the distance La is not fixed, the driving fluid may be injected into the driving chamber 2 from the sub-piston 9 by using the first main pressure fluid passage 61 and the main pressure fluid injection pipe 62, and the corresponding oil delivery pipe may be fixed to the third cylinder head 105. However, since the high-pressure fluid medium is injected into the main-pressure fluid inlet 6, there is a high demand for sealing between the first main-pressure fluid passage 61 and the main-pressure fluid injection pipe 62.

Alternatively, when the distance La is not fixed, the second main pressure fluid passage 63 may be used to inject the driving fluid from the main piston 7 into the driving chamber 2 to perform the b-stage operation, but the corresponding oil delivery passage needs to be moved in accordance with the movement of the main piston rod 8.

The linear driving cylinder of the utility model completes the pressurization work, and is in the stage c and the resetting process when the main piston rod 8 needs to be retracted;

the return fluid inlet 15 is communicated with the driving fluid station and injects driving fluid into the return cavity 1;

the driving fluid inlet 13 and the main pressure fluid inlet 6 are communicated with an oil return pipeline simultaneously or sequentially, or are opened to discharge fluid media in the driving cavity 2 and the rapid propulsion cavity 4;

the first interface 14 or the second interface 12 is kept in an open state or is connected with a fluid infusion device;

the c-stage moving distance of the main piston rod 8 is La + Lb:

operating speed Vc = Q ÷ S1= Q ÷ (a-C);

retraction time Tc = (La + Lb) ÷ Vc = (La + Lb) × (a-C) ÷ Q;

the driving fluid usage Mc = (La + Lb) × S1= (La + Lb) × (a-C).

The utility model discloses a c stage of linear drive cylinder, it is unanimous with current linear drive cylinder performance.

In the use process of the linear driving cylinder, the auxiliary piston rod 10 does not participate in the outward pressure application.

When the linear driving cylinder of the utility model is used, the process of the outward extension of the main piston rod 8 to generate pressure (thrust) is mainly utilized, namely, the fast extension process at the stage a and the main pressure process at the stage b; however, when the linear driving cylinder works, the sequence of the stage a and the stage b is not required to be strictly limited, and the action sequence of the stage a and the stage b can be reasonably allocated according to the use requirement and the application requirement of specific working equipment; the a stage and the b stage can be alternatively combined in a certain mode, and even the reset process of the c stage can be added in time.

While the preferred embodiments of the present invention have been described, it will be understood by those skilled in the art that the invention is not limited to the disclosed embodiments, but is intended to cover various modifications and alternatives falling within the spirit and scope of the invention as defined by the appended claims.

Claims (10)

1. The double-cavity linear driving cylinder comprises a main cylinder body, a front cylinder cover, a rear cylinder cover, a main piston rod and a return fluid inlet;

the section size of the main piston is matched with the inner section of the cylinder body, and the main piston divides the inner cavity of the main cylinder body into two parts; a return cavity is formed between the main piston and the front cylinder cover and is communicated with the return fluid inlet;

the main piston rod is connected to the main piston and is partially positioned in the return cavity; the main piston rod penetrates through the front cylinder cover, and the keeping part is positioned outside the front cylinder cover; the part of the main piston rod, which is positioned outside the front cylinder cover, is a working part;

the device is characterized in that an auxiliary piston and an auxiliary piston rod are also arranged in the main cylinder body;

the section size of the auxiliary piston is matched with that of the inner cavity of the cylinder body, the auxiliary piston is arranged in parallel with the main piston, and a driving cavity is formed between the auxiliary piston and the main piston; the drive chamber is communicated with the drive fluid station through a main pressure fluid inlet;

a first rod cavity is formed between the auxiliary piston and the rear cylinder cover along the main cylinder body; the first rod cavity is communicated with the outside;

the auxiliary piston rod is connected to the auxiliary piston, and the part of the auxiliary piston rod is positioned in the first rod cavity;

the auxiliary piston rod penetrates through the rear cylinder cover, and the keeping part of the auxiliary piston rod is positioned outside the rear cylinder cover;

a second cylinder body is arranged outside the rear cylinder cover, and the part of the auxiliary piston rod, which is positioned outside the rear cylinder cover, is completely positioned in the second cylinder body; the tail end of the second cylinder body is sealed through a third cylinder cover;

a rapid propelling cavity is formed in the second cylinder body, a driving fluid inlet is formed in the second cylinder body or the third cylinder cover, and the rapid propelling cavity is communicated with the driving fluid inlet;

the rapid propulsion chamber is communicated with a driving fluid station through the driving fluid inlet;

the second cylinder body, the auxiliary piston rod in the second cylinder body and the quick propelling cavity form a quick propelling linear driving cylinder together;

the diameter of the inner cavity of the second cylinder body is smaller than or equal to that of the inner cavity of the main cylinder body.

2. The dual chamber linear drive cylinder of claim 1 wherein said second cylinder body and said secondary piston rod therein form a plunger cylinder;

the quick propelling cavity is located in the whole second cylinder body.

3. The dual chamber linear drive cylinder of claim 1 wherein said secondary piston rod is provided with a quick push piston at the end of said secondary cylinder;

the cross section size of the quick-push piston is matched with the cross section size of the inner cavity of the second cylinder body;

a quick pushing cavity is formed between the quick pushing piston and the third cylinder cover along the second cylinder body;

a second rod cavity is formed between the quick-push piston and the rear cylinder cover along the second cylinder body; the second rod cavity is communicated with the outside.

4. The dual chamber linear drive cylinder of claim 1 wherein said primary pressure fluid inlet is a first primary pressure fluid passageway disposed within said secondary piston rod, said first primary pressure fluid passageway extending through said secondary piston and communicating with said drive chamber;

a main pressure fluid injection pipe is arranged in the second cylinder body, and a fluid channel is arranged in the main pressure fluid injection pipe;

the first primary pressure fluid passageway is in communication with a drive fluid station through the primary pressure fluid injection tube.

5. The dual chamber linear drive cylinder of claim 4 wherein said main pressure fluid injection tube is a rigid pipe;

one end of the main pressure fluid injection pipe is fixed on the third cylinder cover, and a fluid inlet port is formed in the third cylinder cover;

the other end of the primary pressure fluid injection tube is inserted into the first primary pressure fluid channel; a sliding seal is disposed between the outer wall of the primary pressure fluid injection tube and the inner wall of the first primary pressure fluid passageway.

6. The dual chamber linear actuator cylinder of claim 4 wherein said main pressure fluid injection tube is a hose;

one end of the main pressure fluid injection pipe is fixed on the third cylinder cover or the wall surface of the second cylinder body;

the other end of the main pressure fluid injection pipe is connected with the first main pressure fluid channel of the auxiliary piston rod.

7. The dual chamber linear drive cylinder of claim 1 wherein said primary pressure fluid inlet is a second primary pressure fluid passageway disposed within said primary piston rod;

the second main pressure fluid channel penetrates through the main piston and is communicated with the driving cavity;

the inlet of the second main pressure fluid passage is located on the portion of the main piston rod outside the front cylinder head.

8. The dual chamber linear actuator cylinder of claim 7 wherein the inlet of said second main pressure fluid passageway is located on the face of the body forward of the extending end of said main piston rod.

9. The dual chamber linear actuator cylinder of claim 1 wherein a third main pressure fluid port is provided in said cylinder block; when the drive chamber moves to the third main pressure fluid interface, drive fluid may be injected into the drive chamber through the third main pressure fluid interface.

10. The dual chamber linear drive cylinder of claim 1 wherein a support is provided between said secondary piston and said primary piston;

the driving cavity is always arranged between the auxiliary piston and the main piston;

when the volume of the driving cavity is minimum, the support is abutted between the auxiliary piston and the main piston;

when the volume of the driving cavity is minimum, the area of the contact surface between the driving cavity and the main piston reserved between the auxiliary piston and the main piston is larger than or equal to the effective fluid pushing area of the rapid propelling cavity.

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