CN210153207U - Inner cylinder body for hydraulic breaking hammer - Google Patents

Abstract

The utility model discloses an inner cylinder body for hydraulic breaking hammer, including the inner casing, be provided with the piston by liquid drive reciprocating motion in the inner casing, be provided with the guiding device that the liquid of being convenient for flows on the inner casing. The utility model discloses a processing of cylinder body is simplified in this kind of technique not only makes, and processing cost reduces and can fine assurance piston in the coaxiality of well cylinder body motion, has also made things convenient for the user simultaneously, and the user can oneself change the solution when breaking down, has reduced the technical degree of difficulty of changing, has realized manufacturer and user's win-win.

Description

Inner cylinder body for hydraulic breaking hammer

Technical Field

The utility model relates to a breaker, specifically speaking relate to an inner cylinder body for hydraulic pressure quartering hammer that uses in aspects such as mining, metallurgy, railway, highway, municipal garden, building, boats and ships, belong to engineering machine tool technical field.

Background

The hydraulic breaking hammer takes pressure oil output by hydraulic pumps of an excavator and a loader as power, and controls a piston arranged in an inner hole of a middle cylinder body to move back through a flow distribution valve arranged on the middle cylinder body of the breaking hammer. The hydraulic breaking hammer comprises an upper cylinder body, a middle cylinder body and a lower cylinder body, wherein the middle cylinder body is the most important cylinder body. The middle cylinder body is an installation carrier of important parts, and the quality of the middle cylinder body directly influences the performance of the breaking hammer.

There are two types of prior art cylinder bodies. One is that the middle cylinder body is an integral body, and once the cylinder body is damaged by pulling in use, two results can be generated, and firstly, the integral middle cylinder body is scrapped, so that the waste is serious; secondly, the centering cylinder body is polished and the piston is matched again, which is very troublesome. The second is to install a sleeve in the inner bore of the middle cylinder body, and to replace the sleeve when the bore cooperating with the piston fails. This arrangement has the advantage of not scrapping the whole middle cylinder. But also has disadvantages that the replacement is troublesome and the coaxiality after the replacement is not well ensured. According to repeated research and tests on the cylinder body in the prior art, a novel structure is developed, and the defects in the prior art can be well overcome. The technology not only simplifies the processing of the middle cylinder body, but also can solve the problem of repairing the damaged middle cylinder body and ensure the coaxiality of the damaged middle cylinder body.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is to overcome the above-mentioned not enough of prior art, provide an inner cylinder body for hydraulic pressure quartering hammer.

In order to solve the above problem, the utility model adopts the following technical scheme: an inner cylinder body for a hydraulic breaking hammer comprises an inner cylinder, wherein a piston driven by liquid to reciprocate is arranged in the inner cylinder, and a flow guide device convenient for the liquid to flow is arranged on the inner cylinder.

The following is the utility model discloses to the further optimization of above-mentioned scheme: the flow guide device comprises a piston stroke flow distribution unit for driving the piston to do stroke motion.

Further optimization: the inner cylinder is provided with a slide valve, and the inner cylinder is provided with a slide valve return flow distribution unit for driving the slide valve to do return movement.

Further optimization: the piston stroke flow distribution unit comprises a first annular groove, an inner cylinder second annular groove, an inner cylinder third annular groove and an inner cylinder fourth annular groove.

Further optimization: and three inner cylinder holes which are convenient for liquid to enter the inner cavity of the inner cylinder are formed in the third annular groove of the inner cylinder.

Further optimization: and the first annular groove is provided with four inner cylinder holes for facilitating the liquid to flow out of the inner cavity of the inner cylinder.

Further optimization: the return flow distribution unit of the slide valve comprises an inner cylinder second inner annular groove and an inner cylinder third inner annular groove, wherein the inner cylinder second inner annular groove and the inner cylinder third inner annular groove are formed in one end of the inner cylinder.

Further optimization: and the second inner annular groove of the inner cylinder is provided with an inner cylinder hole which is convenient for liquid to flow into the inner cavity of the inner cylinder.

Further optimization: and the third inner annular groove of the inner cylinder is provided with a second inner cylinder hole which is convenient for the liquid in the inner cavity of the inner cylinder to flow out.

Further optimization: and the inner cylinder is provided with an inner cylinder axial groove used for communicating the first inner cylinder annular groove with the second inner cylinder annular groove.

The working principle is as follows: when high-pressure oil (liquid) enters the annular groove of the oil seal fixer through the oil inlet of the middle cylinder, a part of the high-pressure oil enters the first annular groove of the inner cylinder through the hole of the oil seal fixer, the high-pressure oil enters the second annular groove of the inner cylinder through the first annular groove of the inner cylinder, the first end surface of the slide valve pushes the slide valve to move leftwards under the action of the high-pressure oil, the first annular groove of the slide valve moves leftwards to be communicated with the third annular groove of the inner cylinder, the high-pressure oil enters the third annular groove of the inner cylinder and enters the first cavity through the three holes of the inner cylinder, the high-pressure oil pushes the first end surface of the piston to enable the piston to impact rightwards, and the stroke motion of the piston is formed under the combined action of the acting force of the high-pressure oil and the force of the nitrogen in;

one part of high-pressure oil entering from an oil inlet hole of the middle cylinder forms the stroke motion of the piston through a hole of the oil seal fixer, the other part of the high-pressure oil enters a first radial hole and a second radial hole of the middle cylinder through an annular groove of the oil seal fixer, enters a fourth cavity formed by the return oil distribution sleeve and the middle cylinder through the first axial hole of the middle cylinder, the second axial hole of the middle cylinder, the third radial hole of the middle cylinder and the fourth radial hole of the middle cylinder, and enters the second cavity through a hole of the return oil distribution sleeve;

the area of the second end surface of the piston on the piston is larger than that of the third end surface of the piston, in the piston stroke, the area of the first end surface of the piston plus the area of the third end surface of the piston is larger than that of the second end surface of the piston, and in addition, the action of nitrogen on the piston is great, the acting force in the piston stroke is also great, the pressure formed by the area of the second end surface of the piston being larger than that of the third end surface of the piston is negligible, and the phenomenon is the same as that in the prior art;

in the piston stroke movement, when the first end surface of the piston is positioned in the first inner annular groove of the inner cylinder, high-pressure oil for pushing the piston stroke enters the first inner annular groove of the inner cylinder, enters a fifth cavity formed by the inner cylinder and the slide valve through four holes of the inner cylinder in the first inner annular groove of the inner cylinder, enters a third cavity through a hole of the slide valve, is discharged through an oil return hole of the middle cylinder, the pressure in the first cavity is reduced, and the piston starts to return under the action of high-pressure oil in the second cavity;

when the piston moves rightwards to the second end face of the piston and is positioned in the second inner annular groove of the inner cylinder, high-pressure oil in a second cavity formed by the piston and the return oil distribution sleeve enters the annular groove in the middle of the piston through the first hole of the inner cylinder and the third inner annular groove of the inner cylinder and enters the sixth cavity through the second inner annular groove of the inner cylinder and the second hole of the inner cylinder to push the slide valve to move rightwards, when the slide valve moves rightwards to the inner hole of the slide valve to cut off the third annular groove of the inner cylinder and the second annular groove of the inner cylinder, the high-pressure oil in the first cavity is not discharged any more, the rightwards return motion of the piston is gradually decelerated to prepare for starting the leftwards stroke motion of the piston, and the reciprocating same-direction motion of the piston and the slide valve enables the pressure of the high-pressure oil in the.

The utility model discloses a processing of cylinder body is simplified in this kind of technique not only makes, and processing cost reduces and can fine assurance piston in the coaxiality of well cylinder body motion, has also made things convenient for the user simultaneously, and the user can oneself change the solution when breaking down, has reduced the technical degree of difficulty of changing, has realized manufacturer and user's win-win.

The present invention will be further explained with reference to the drawings and examples.

Drawings

Fig. 1 is a schematic view of an assembly structure in an embodiment of the present invention;

FIG. 2 is a schematic view of the structure in the direction B-B in FIG. 1;

FIG. 3 is a schematic view of the structure in the direction A-A in FIG. 1;

FIG. 4 is a schematic view of the structure of FIG. 1 in the direction C-C;

FIG. 5 is a schematic view of the structure of FIG. 1 in the direction D-D;

FIG. 6 is a schematic view of the structure of FIG. 1 in the direction F-F;

FIG. 7 is a schematic view of the structure in the direction G-G in FIG. 1;

FIG. 8 is a schematic view of the structure in the direction E-E of FIG. 1;

FIG. 9 is a schematic view of the structure in the direction H-H in FIG. 1;

fig. 10 is a schematic structural view of an oil seal holder according to an embodiment of the present invention;

fig. 11 is a schematic structural view of a return oil distribution sleeve in an embodiment of the present invention;

fig. 12 is a schematic structural view of an inner cylinder in an embodiment of the present invention;

fig. 13 is a schematic structural view of a position limiting body according to an embodiment of the present invention;

fig. 14 is a schematic view of a slide valve according to an embodiment of the present invention;

fig. 15 is a schematic structural view of a piston according to an embodiment of the present invention;

fig. 16 is a schematic structural diagram of the present invention in an embodiment.

In the figure: 1-middle cylinder; 2-return oil distribution sleeve; 3-a limiting body; 4-inner cylinder; 5-a slide valve; 6-oil seal fixer; 7-a piston; 8, mounting the cylinder body; 9-a first annular groove; 10-a second annular groove; 11-a flange; 12-a boss; 13-a bump; k1-hole of return oil distribution sleeve; k2-one hole in the inner cylinder; k3-inner cylinder two holes; k4-three holes in inner cylinder; k5-four holes of inner cylinder; k6-a hole in the radial direction of the middle cylinder; k7-two radial holes of middle cylinder; k8-a hole in the middle cylinder axial direction; k9-two axial holes of the middle cylinder; k10-three radial holes in the middle cylinder; k11-radial four holes of middle cylinder; k12-middle cylinder oil inlet; k13-middle cylinder oil return hole; k14-bore of oil seal holder; k15-bore of slide valve; c1-inner cylinder axial groove; c2-oil seal holder ring groove; c3 — inner cylinder first annular groove; c4 — spool valve first annular groove; c41 — spool valve second annular groove; c5 — inner cylinder second annular groove; c6 — inner cylinder third ring groove; c7-inner cylinder first inner annular groove; c8-the fourth annular groove of the inner cylinder; c9-inner cylinder second inner annular groove; c10-inner cylinder third inner annular groove; c11 — piston middle ring groove; q1 — first cavity; q2 — second cavity; q3-third cavity; q4-fourth cavity; q5-fifth cavity; q6-sixth cavity; d1 — piston first end face; d2 — piston second end face; d3 — piston third end face; d4-return oil distribution sleeve end face; d5-the first end face of the spacing body; d6-a second end face of the spacing body; d7-inner cylinder first end face; d8-second end surface of inner cylinder; d9-oil seal fixer end; d10 — spool valve first end face; d11 — piston first end face; d12 — piston second end face; d13 — spool valve second end face; w1-piston outer circular surface; w2-inner cylinder outer circle surface; w3-stopper bore.

Detailed Description

In the embodiment, as shown in fig. 1 to 16, an inner cylinder body for a hydraulic breaking hammer comprises an inner cylinder 4 with a cylindrical structure, a piston 7 driven by liquid (lubricating oil) to reciprocate is arranged in the inner cylinder 4, and a flow guide device for facilitating the flow of the liquid is arranged on the inner cylinder 4.

The inner cylinder 4 is coaxially arranged in the middle cylinder 1 with a cavity inside, and one end of the middle cylinder 1 is provided with a gas driving mechanism for assisting the hydraulic circulating system to drive the piston 7 to move.

The flow guide device comprises an inner cylinder first annular groove C3, an inner cylinder second annular groove C5, an inner cylinder third annular groove C6 and an inner cylinder fourth annular groove C8 which are of annular structures and are sequentially arranged on the outer circumference of the inner cylinder 4 from one end to the other end of the inner cylinder 4;

the inner wall of the inner cylinder 4 is sequentially provided with a first inner annular groove C7, a second inner annular groove C9 and a third inner annular groove C10 of an annular structure from one end to the other end of the inner cylinder 4, and the inner cylinder 4 is coaxially assembled at a position close to one end on the piston 7.

A plurality of inner cylinder axial grooves C1 with arc-shaped longitudinal sections are arranged on the outer circumference of the inner cylinder 4 in an annular array mode, the inner cylinder axial grooves C1 are arranged along the axial direction of the inner cylinder 4 respectively, and the inner cylinder axial grooves C1 are located between the first inner cylinder annular groove C3 and the second inner cylinder annular groove C5.

A plurality of inner cylinder three holes K4 penetrating through the side wall of the inner cylinder 4 are formed in the position, close to the middle, of the inner cylinder third annular groove C6;

the plurality of inner cylinder three holes K4 are annularly arrayed on the inner cylinder third annular groove C6, and each inner cylinder three hole K4 is respectively arranged in the radial direction of the inner cylinder 4.

A plurality of inner cylinder four holes K5 penetrating through the side wall of the inner cylinder 4 are annularly arrayed at a position close to one end of the first inner annular groove C7 of the inner cylinder, and each inner cylinder four hole K5 is respectively arranged along the radial direction of the inner cylinder 4.

The outer circumference of the inner cylinder 4 is provided with a first annular groove 9 with an annular structure at the position corresponding to the inner cylinder four holes K5.

A plurality of inner cylinder two holes K3 penetrating through the side wall of the inner cylinder 4 are annularly arrayed at a position close to one end on the inner wall of the inner cylinder second inner annular groove C9, and each inner cylinder two hole K3 is respectively arranged along the radial direction of the inner cylinder 4.

And a second annular groove 10 with an annular structure is formed in the outer circumference of the inner cylinder 4 at a position corresponding to the second inner cylinder hole K3.

A plurality of inner cylinder one-hole K2 penetrating through the side wall of the inner cylinder 4 are annularly arrayed at a position close to one end on the inner wall of the inner cylinder third inner annular groove C10, and each inner cylinder one-hole K2 is respectively arranged along the radial direction of the inner cylinder 4.

The inner cylinder 4 is fixedly arranged in the middle cylinder 1 through a limiting device, the limiting device comprises an oil seal fixer 6 coaxially assembled at one end of the inner cylinder 4, and the other end of the inner cylinder 4 is limited in position by a limiting body 3.

The oil seal fixer 6 is of a two-section structure connected integrally, one section is a large-diameter section connected with the outer circumference of the piston 7 in a sliding way, and the end surface D9 of the oil seal fixer of the large-diameter section is contacted with the second end surface D8 of the inner cylinder 4;

the other section is a small-diameter section arranged between the outer circular surface W2 of the inner cylinder 4 and the inner wall of the middle cylinder 1, and the inner diameter of the small-diameter section is equal to the outer diameter of the inner cylinder 4;

the large-diameter section and the small-diameter section are both of annular structures, and the axes of the large-diameter section and the small-diameter section are on the same straight line.

The longitudinal section of the limiting body 3 is L-shaped, the limiting body 3 is fixedly installed between the middle cylinder 1 and the inner cylinder 4, a bulge 13 used for limiting the axial position of the limiting body 3 is arranged on the outer circumference of the inner cylinder 4 and close to the second annular groove 10, and the bulge 13 is of an annular structure.

And one end of the limiting body 3, which is far away from the oil seal fixer 6, is provided with a piston return oil distribution unit which axially limits the limiting body 3, and the piston return oil distribution unit is a return oil distribution sleeve 2.

A cavity is formed in the return oil distribution sleeve 2, and the return oil distribution sleeve 2 is coaxially assembled between the middle cylinder 1 and the piston 7.

And holes K1 of the return oil distribution sleeve penetrating through the side wall of the return oil distribution sleeve 2 are annularly arrayed at one end, close to the limiting body 3, of the outer circumference of the return oil distribution sleeve 2, and the holes K1 of each return oil distribution sleeve are respectively arranged along the radial direction of the return oil distribution sleeve 2.

The middle cylinder 1 is provided with a boss 12 with the inner diameter equal to the outer diameter of the small diameter section corresponding to the small diameter section of the oil seal fixer 6, the boss 12 is of an annular structure, and the oil seal fixer 6 can be axially limited by the design.

The one end fixedly connected with of well jar 1 is inside to be provided with the last cylinder body 8 of cavity, and the one end top of going up cylinder body 8 is tight and is kept away from the one end of inner casing 4 on oil blanket fixer 6, carries out the position through the combined action of well jar 1 and last cylinder body 8 and prescribes a limit to oil blanket fixer 6 like this.

The upper cylinder body 8, the oil seal fixer 6 and the piston 7 form a gas driving mechanism, a cavity surrounded by the upper cylinder body 8, the oil seal fixer 6 and the piston 7 is filled with compressed gas for driving the piston 7 to move, and the compressed gas is nitrogen.

The oil seal holder 6, the piston 7 and the inner cylinder 4 enclose a first cavity Q1, and the first cavity Q1 is used for containing liquid for driving the piston 7 to move.

The inner cylinder 4 is provided on its outer circumference with a shut-off device for controlling whether liquid enters the first cavity Q1, which is reciprocally moved on the inner cylinder 4.

The cut-off means includes a spool 5 of a cylindrical structure, the spool 5 being coaxially fitted on the outer circumference of the inner cylinder 4, and one end of the spool 5 being coaxially fitted between the stopper body 3 and the inner cylinder 4.

And a first annular groove C4 of the slide valve, which is used for communicating the second annular groove C5 of the inner cylinder and the third annular groove C6 of the inner cylinder, is formed in the position, close to one end, on the inner wall of the slide valve 5.

And one end of the inner wall of the slide valve 5, which is far away from the first annular groove C4 of the slide valve, is provided with a second annular groove C41 of the slide valve, which is used for communicating the fourth annular groove C8 of the inner cylinder with the first annular groove 9.

The first annular groove C4 and the second annular groove C41 are both annular structures and are arranged coaxially with the slide valve 5.

The spool valve 5 and the inner cylinder 4 enclose a fifth cavity Q5, and the fifth cavity Q5 is used for containing liquid output by the four holes K5 of the inner cylinder.

The inner wall of the second annular groove C41 of the slide valve is provided with a slide valve hole K15 which penetrates through the inner wall of the slide valve 5 at a position close to one end, so that the liquid in the fifth cavity Q5 is conveniently output.

One end of the slide valve 5 close to the limiting body 3 is provided with a bulge with an annular structure, and the bulge is used for limiting the movement of the slide valve 5 towards the direction close to the limiting body 3.

A second cavity Q2 is defined by the return oil distribution sleeve 2, the piston 7, the inner cylinder 4 and the limiting body 3, and a flange 11 with an annular structure is arranged on the piston 7 at a position in the second cavity Q2.

One end face of the flange 11 is a piston second end face D2, and the other end face is a piston third end face D3.

A fourth cavity Q4 is defined among the middle cylinder 1, the return oil distribution sleeve 2 and the limiting body 3, and a middle cylinder radial four-hole K11 and a middle cylinder radial three-hole K10 which are communicated with the fourth cavity Q4 are arranged at the position, corresponding to the fourth cavity Q4, on the middle cylinder 1.

The middle cylinder radial four-hole K11 and the middle cylinder radial three-hole K10 are respectively arranged along the radial direction of the middle cylinder 1, and the included angle between the middle cylinder radial four-hole K11 and the middle cylinder radial three-hole K10 is a right angle.

And a middle cylinder oil inlet hole K12 which penetrates through the side wall of the middle cylinder 1 is formed in the position, corresponding to the boss 12, on one side of the middle cylinder 1, and the middle cylinder oil inlet hole K12 is used for injecting liquid into the device.

The boss 12 is provided with a middle cylinder radial first hole K6 and a middle cylinder radial second hole K7 at positions corresponding to the middle cylinder radial four holes K11 and the middle cylinder radial three holes K10.

The middle cylinder radial first hole K6 and the middle cylinder radial second hole K7 are respectively arranged along the radial direction of the middle cylinder 1.

The middle cylinder radial one-hole K6 and the middle cylinder radial three-hole K10 are communicated through a middle cylinder axial one-hole K8, and the middle cylinder radial two-hole K7 and the middle cylinder radial four-hole K11 are communicated through a middle cylinder axial two-hole K9.

The middle cylinder axial one-hole K8 and the middle cylinder axial two-hole K9 are respectively arranged along the axial direction of the middle cylinder 1.

And the positions of the oil seal fixer 6 corresponding to the first radial hole K6, the second radial hole K7 and the oil inlet K12 of the middle cylinder are respectively provided with a hole K14 of the oil seal fixer.

The holes K14 of the three oil seal retainers are respectively communicated with the radial first hole K6 of the middle cylinder, the radial second hole K7 of the middle cylinder and the oil inlet hole K12 of the middle cylinder, and the hole K14 of each oil seal retainer is arranged along the radial direction of the oil seal retainer 6.

And the oil seal fixer 6 is provided with an annular ring C2 of the oil seal fixer in an annular structure at a position corresponding to the hole K14 of the oil seal fixer, and the annular ring C2 of the oil seal fixer is used for communicating the holes K14 of the three oil seal fixers.

And a third cavity Q3 is defined by the middle cylinder 1, the slide valve 5, the inner cylinder 4, the oil seal fixer 6 and the limiting body 3, and a middle cylinder oil return hole K13 is formed in the position, close to the middle cylinder oil inlet hole K12, of one side of the middle cylinder 1.

The middle cylinder oil return hole K13 is arranged along the radial direction of the middle cylinder 1 and is used for outputting liquid in the third cavity Q3.

The slide valve 5, the inner cylinder 4 and the limiting body 3 enclose a sixth cavity Q6, and the sixth cavity Q6 is used for containing the liquid output by the two holes K3 of the inner cylinder and enabling the liquid to drive the slide valve 5 to move.

One end surface of the piston 7 for controlling the connection and disconnection of the first inner annular groove C7 of the inner cylinder and the first cavity Q1 is a first piston end surface D1, and one end of the piston 7 close to the upper cylinder body 8 is a first piston end surface D11.

And one end surface of the piston 7 for controlling the on-off of the second inner annular groove C9 and the third inner annular groove C10 of the inner cylinder is a second end surface D12 of the piston.

The outer circular surface of the piston 7 contacting with the inner wall of the inner cylinder 4 is a piston outer circular surface W1, and the piston outer circular surface W1 is located between the piston first end surface D1 and the piston second end surface D12.

And a piston middle annular groove C11 used for communicating the inner cylinder second inner annular groove C9 with the inner cylinder third inner annular groove C10 is formed in the position, close to the piston second end face D12, of the piston 7, and the piston middle annular groove C11 is of an annular structure.

A limiting body inner hole W3 is formed in the limiting body 3, and the limiting body inner hole W3 is connected with the slide valve 5 in a sliding mode.

An end face, which is contacted with the limiting body 3, on the return oil distribution sleeve 2 is a return oil distribution sleeve end face D4, and an end face, which is contacted with the return oil distribution sleeve end face D4, on the limiting body 3 is a limiting body first end face D5.

One end face of the limiting body 3, which is in contact with one side of the protrusion 13, is a second end face D6 of the limiting body, and one end face of the protrusion 13, which is in contact with the second end face D6 of the limiting body, is a first end face D7 of the inner cylinder.

The end surface of the slide valve 5 close to the oil seal fixer 6 is a slide valve first end surface D10, and the end surface of the slide valve 5 close to the bulge 13 is a slide valve second end surface D13.

The outer circumference of the piston 7 is provided with a plurality of oil storage grooves with annular structures at positions close to the middle part, and the oil storage grooves are respectively positioned between the piston middle annular groove C11 and the flange 11 and between the piston middle annular groove C11 and the piston first end surface D1.

And the first annular groove 9, the inner cylinder second annular groove C5, the inner cylinder third annular groove C6, the inner cylinder fourth annular groove C8, the inner cylinder four-hole K5, the inner cylinder first annular groove C3, the inner cylinder axial groove C1 and the inner cylinder first inner annular groove C7 form a piston stroke flow distribution unit.

And the inner cylinder second inner annular groove C9, the inner cylinder third inner annular groove C10, the inner cylinder first hole K2 and the inner cylinder second hole K3 form a slide valve return flow distribution unit.

The working principle is as follows: when high-pressure oil (liquid) enters an annular groove C2 of an oil seal fixer through an oil inlet K12 of a middle cylinder, a part of the high-pressure oil enters a first annular groove C3 of an inner cylinder through a hole K14 of the oil seal fixer, the high-pressure oil enters a second annular groove C5 of the inner cylinder through a first annular groove C1 of the inner cylinder, a first end surface D10 of a slide valve pushes the slide valve 5 to move leftwards under the action of the high-pressure oil, the first annular groove C4 of the slide valve moves leftwards to be communicated with a third annular groove C6 of the inner cylinder, the high-pressure oil enters a third annular groove C6 of the inner cylinder and enters a first cavity Q1 through three holes K4 of the inner cylinder, the high-pressure oil pushes a first end surface D1 of a piston 7 to impact the piston 7 rightwards, and the stroke motion of the piston 7 is formed under the combined action of the action force of the high-pressure oil and the force of nitrogen acting on the first end surface D11 of;

one part of high-pressure oil entering from the oil inlet hole K12 of the middle cylinder forms the stroke motion of the piston 7 through a hole K14 of an oil seal fixer, the other part of the high-pressure oil enters a first radial hole K6 and a second radial hole K7 of the middle cylinder 1 through an annular groove C2 of the oil seal fixer, enters a fourth cavity Q4 formed by the return oil distribution sleeve 2 and the middle cylinder 1 through a first axial hole K8 of the middle cylinder, a second axial hole K9 of the middle cylinder, a third radial hole K10 of the middle cylinder and a fourth radial hole K11 of the middle cylinder, and enters a second cavity Q2 through a hole K1 of the return oil distribution sleeve 2;

the area of the second end surface D2 of the piston on the piston 7 is larger than the area of the third end surface D3 of the piston, in the stroke of the piston 7, the area of the first end surface D1 of the piston plus the area of the third end surface D3 of the piston is much larger than the area of the second end surface D2 of the piston, plus the action of nitrogen on the piston 7, the acting force in the stroke of the piston 7 is also very large, the pressure formed by the area of the second end surface D2 of the piston being larger than the area of the third end surface D3 of the piston is negligible, and the phenomenon is the same as that;

in the stroke motion of the piston 7, when the first end surface D1 of the piston is positioned in the first inner annular groove C7 of the inner cylinder, high-pressure oil which pushes the piston 7 to stroke enters the first inner annular groove C7 of the inner cylinder, enters a fifth cavity Q5 formed by the inner cylinder 4 and the slide valve 5 through four inner cylinder holes K5 in the first inner annular groove C7 of the inner cylinder, enters a third cavity Q3 through a hole K15 of the slide valve, and is discharged through an oil return hole K13 of the middle cylinder, at the moment, the pressure in the first cavity Q1 is reduced, and the piston 7 starts to return under the action of the high-pressure oil in the second cavity Q2;

when the piston 7 moves rightwards until the second end D12 of the piston is positioned in the second inner annular groove C9 of the inner cylinder, high-pressure oil in a second cavity Q2 formed by the piston 7 and the return oil distribution sleeve 2 enters the annular groove C11 in the middle of the piston through the first hole K2 of the inner cylinder and the third inner annular groove C10 of the inner cylinder, enters the sixth cavity Q6 through the second inner annular groove C9 of the inner cylinder and the second hole K3 of the inner cylinder, the slide valve 5 is pushed to move rightwards, when the slide valve 5 moves rightwards to cut off the third annular groove C6 of the inner cylinder and the second annular groove C5 of the inner cylinder, the high-pressure oil in the first cavity Q1 is not discharged any more, the return stroke movement of the piston 7 rightwards is gradually decelerated and is ready to start the stroke movement of the piston 7 leftwards, and the reciprocating equidirectional movement of the piston 7 and the slide valve 5 makes the high-pressure oil in the first cavity Q1 change to form the reciprocating return stroke movement.

The utility model breaks through the design thought of the traditional hydraulic breaking hammer, and the parallel arrangement structure of the piston and the distributing valve is innovative and is coaxially arranged; the equidirectional movement of the distributing valve and the piston is realized, and the phenomenon that the breaking hammer is not started when the stop position of the piston or the distributing valve is not proper is avoided; the utility model has simple integral structure, saves more than 30 percent of materials, is easy to process, reduces the cost and improves the processing efficiency by more than 40 percent; when the strain phenomenon occurs, only one small part is replaced without replacing the middle cylinder, so that the use cost of a user is reduced; the utility model discloses the research and development thinking that the popularization and application of technique will change the quartering hammer trade makes china's quartering hammer trade technological innovation step into a new step.

Having shown and described the basic principles and essential features of the invention and advantages thereof, it will be apparent to those skilled in the art that the invention is not limited to the details of the foregoing exemplary embodiments, but is capable of other specific forms without departing from the spirit or essential characteristics thereof, and it is therefore intended that the embodiments be considered as exemplary and not limiting in any way, since the scope of the invention is defined by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein and are therefore not to be embraced therein by any reference numerals in the claims.

Claims (6)

1. The utility model provides an inner cylinder body for hydraulic breaking hammer which characterized in that: comprises an inner cylinder (4), a piston (7) driven by liquid to reciprocate is arranged in the inner cylinder (4), and a flow guide device convenient for the liquid to flow is arranged on the inner cylinder (4);

the flow guide device comprises a piston stroke flow distribution unit for driving a piston (7) to do stroke motion;

the piston stroke flow distribution unit comprises a first annular groove (9), an inner cylinder second annular groove (C5), an inner cylinder third annular groove (C6) and an inner cylinder fourth annular groove (C8);

the third annular groove (C6) of the inner cylinder is provided with three inner cylinder holes (K4) which are convenient for liquid to enter the inner cavity of the inner cylinder (4);

four inner cylinder holes (K5) which are convenient for liquid to flow out from the inner cavity of the inner cylinder (4) are formed in the first annular groove (9).

2. The inner cylinder for a hydraulic demolition hammer as set forth in claim 1, wherein: the inner cylinder (4) is provided with a slide valve (5), and the inner cylinder (4) is provided with a slide valve return flow distribution unit for driving the slide valve (5) to do return movement.

3. The inner cylinder for a hydraulic demolition hammer as set forth in claim 2, wherein: the return flow distribution unit of the slide valve comprises an inner cylinder second inner annular groove (C9) and an inner cylinder third inner annular groove (C10) which are arranged at one end of the inner cylinder (4).

4. The inner cylinder for a hydraulic demolition hammer as set forth in claim 3, wherein: an inner cylinder hole (K2) which is convenient for liquid to flow into the inner cavity of the inner cylinder (4) is arranged on the second inner annular groove (C9) of the inner cylinder.

5. The inner cylinder for a hydraulic demolition hammer as set forth in claim 4, wherein: and a second inner cylinder hole (K3) which is convenient for the liquid in the inner cavity of the inner cylinder (4) to flow out is formed in the third inner annular groove (C10) of the inner cylinder.

6. The inner cylinder for a hydraulic demolition hammer as set forth in claim 5, wherein: and the inner cylinder (4) is provided with an inner cylinder axial groove (C1) for communicating the first inner cylinder annular groove (C3) with the second inner cylinder annular groove (C5).

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