CN113718884A - Valveless reversing type idle-driving-prevention hydraulic breaking hammer - Google Patents
Valveless reversing type idle-driving-prevention hydraulic breaking hammer Download PDFInfo
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- CN113718884A CN113718884A CN202111012875.XA CN202111012875A CN113718884A CN 113718884 A CN113718884 A CN 113718884A CN 202111012875 A CN202111012875 A CN 202111012875A CN 113718884 A CN113718884 A CN 113718884A
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F5/00—Dredgers or soil-shifting machines for special purposes
- E02F5/30—Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil
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Abstract
The invention discloses a valveless reversing type idle-driving-preventing hydraulic breaking hammer, which comprises an integrated outer cylinder, wherein an installation cavity is formed in the outer cylinder, a piston is arranged in the installation cavity, an oil delivery hole is formed in the outer cylinder, the oil delivery hole is communicated with the installation cavity and is used for reversing the moving direction of the piston, an inner sleeve and an outer sleeve are sequentially arranged in the installation cavity of the outer cylinder, the position, close to the front end position of the piston, of the installation cavity is internally provided with a guide sleeve, a drill rod is arranged in the guide sleeve, the installation end of the drill rod is arranged in the outer sleeve, and buffer components for buffering the impact force on the drill rod are arranged at the positions on two sides of the installation end of the drill rod. The processing complexity is avoided, the requirement on the internal working environment is not high, and the use effect is further improved.
Description
Technical Field
The invention belongs to the technical field of hydraulic breaking hammers, and particularly relates to a valveless reversing type idle-driving-preventing hydraulic breaking hammer.
Background
The hydraulic breaking hammer is called as the breaking hammer or the breaker for short, the power source of the hydraulic breaking hammer is the pressure provided by an excavator, a loader or a pump station, and the hydraulic breaking hammer can effectively break stones and rocks in engineering construction and improve the working efficiency.
As patent numbers: 201920146008.7, discloses a kind of hydraulic breaking hammer, which includes a middle cylinder, a piston is equipped in the middle cylinder, and an oil storage device for supplying lubricating oil to the piston is arranged on the middle cylinder.
The existing hydraulic breaking hammer can be used for rock drilling, but the existing hydraulic breaking hammer still has many defects, the existing hydraulic breaking hammer adopts reversing of an external reversing valve and a built-in reversing valve, the two reversing modes adopt the principle that the directions of an oil inlet and an oil outlet are changed through the alternate movement of a valve core and the valve, so that the reversing purpose is achieved, but the reversing mode has higher requirements on the processing of parts and has higher requirements on the cleanliness of internal working media; secondly, the traditional bolt type is adopted in the existing drill rod connection mode, and the structure can not well transfer energy, is short in service life and has certain danger.
Disclosure of Invention
The invention aims to solve the main technical problem of providing a valveless reversing type idle-driving-preventing hydraulic breaking hammer, which can ensure the smooth working of the breaking hammer, avoid the processing complexity and has low requirement on the internal working environment; by adopting the novel drill rod and the connection mode, the energy can be ensured to be better transmitted, the buffer mechanism can prolong the service life of the drill rod, and the danger coefficient is reduced.
In order to solve the technical problems, the invention provides the following technical scheme:
the utility model provides a valveless switching-over formula air defense is beated hydraulic breaking hammer, including the outer jar of integral type, the installation cavity has been seted up in the outer jar, install the piston in the installation cavity, the oil transmission hole has been seted up on the outer jar, oil transmission hole and installation cavity intercommunication are used for reversing to the moving direction of piston, endotheca and overcoat are installed near piston front position department in the installation cavity of outer jar in proper order, install in the overcoat and lead just cover, lead and install the drill rod in just the cover, the installation end of drill rod is installed in the overcoat, the both sides position department of drill rod installation end is provided with the buffering subassembly that is used for carrying out the buffering to the impact force on the drill rod.
The following is a further optimization of the above technical solution of the present invention:
the outer surface of the piston is matched with the inner surface of the mounting cavity, a piston rear cavity, a piston front cavity and a nitrogen chamber are arranged between the outer surface of the piston and the inner surface of the mounting cavity, and a piston ring for packaging the nitrogen chamber is hermetically mounted on the piston.
Further optimization: the diameter of the outer surface of the second limiting section on the piston is matched with the diameter of the inner surface of the piston rear cavity in the mounting cavity.
Further optimization: the cross section annular area of the middle section of the upper piston of the piston is smaller than that of the rear end of the upper piston of the piston.
Further optimization: the oil delivery hole comprises an oil inlet and an oil outlet which are arranged on the outer cylinder, the oil inlet is communicated with the rear cavity of the piston, and the oil outlet is arranged on the outer cylinder and close to the inner sleeve.
Further optimization: the middle part of the inner sleeve is provided with a mounting hole and an oil outlet cavity, the diameter of the inner surface of the mounting hole is matched with the diameter of the outer surface of the striking end of the piston, and the diameter of the inner surface of the oil outlet cavity is matched with the diameter of the outer surface of the first limiting section of the piston.
Further optimization: an oil drainage groove is formed in the position, close to the oil outlet cavity, on the outer surface of the inner sleeve, an oil drainage hole is formed between the oil drainage groove and the oil outlet cavity, the oil outlet cavity is communicated with the oil drainage groove through the oil drainage hole, and the oil outlet is communicated with the oil drainage groove.
Further optimization: the buffering subassembly includes blotter and buffering hydraulic cylinder, and the blotter is installed between endotheca and overcoat, and buffering hydraulic cylinder installs and just overlaps and the overcoat between, is provided with the defeated oil pipe way that is used for carrying hydraulic oil for buffering hydraulic cylinder on the overcoat.
Further optimization: the buffering hydraulic cylinder comprises a hydraulic cylinder main body, a piston body is installed in the hydraulic cylinder main body, a piston rod is installed on the piston body, the other end of the piston rod extends to the outside of the hydraulic cylinder main body and is fixedly connected with a buffering cover, a buffering spring is arranged on the piston rod, and two ends of the buffering spring are respectively connected with the buffering cover and the hydraulic cylinder main body in a jacking mode.
Further optimization: defeated oil pipe way is including seting up overcoat oil inlet and the overcoat oil-out on the overcoat, and the buffering pneumatic cylinder oil inlet intercommunication of seting up in overcoat oil inlet and the pneumatic cylinder main part, and the buffering pneumatic cylinder oil-out intercommunication of seting up in overcoat oil-out and the pneumatic cylinder main part has into oil pipe, and overcoat oil inlet department intercommunication has an overflow valve, advances the low reaches position department series connection of oil pipe and has the check valve on the oil pipe.
By adopting the technical scheme, the hydraulic breaking hammer is ingenious in conception and reasonable in structure, the outer cylinder is of an integrated structure, the hydraulic breaking hammer is convenient to integrally install, the oil leakage phenomenon cannot occur, a reversing valve does not need to be additionally arranged, the piston can automatically reverse under the action of hydraulic oil, the hydraulic breaking hammer is of a valveless reversing type structure, the smooth working of the breaking hammer can be guaranteed, the processing complexity is avoided, the requirement on the internal working environment is not high, and the using effect is improved.
The drill rod is arranged in the outer sleeve through the guide sleeve, the mounting end of the drill rod is arranged in the drill rod mounting hole, the cushion pad and the buffer hydraulic cylinder can be used for limiting the axial position of the drill rod, and the drill rod is convenient to use.
When the drill rod is impacted by impact force, the impact force on the drill rod can act on the buffer pad and the buffer hydraulic cylinder, so that the impact force on the drill rod can be buffered through the buffer pad and the buffer hydraulic cylinder, the characteristic of preventing idle striking is realized, the impact force on the drill rod is reduced, the drill rod is protected, the damage of the drill rod is avoided, the service life of the drill rod can be prolonged, and the safety is improved.
The invention is further illustrated with reference to the following figures and examples.
Drawings
FIG. 1 is a schematic view of the overall structure of embodiment 1 of the present invention;
FIG. 2 is a schematic structural view of an outer cylinder in embodiment 1 of the present invention;
FIG. 3 is a schematic structural view of a piston in embodiment 1 of the present invention;
FIG. 4 is a schematic structural view of an inner sleeve in embodiment 1 of the present invention;
FIG. 5 is a schematic view showing the structure of an outer jacket in example 1 of the present invention;
fig. 6 is a schematic structural view of a cushion cylinder in embodiment 1 of the present invention;
FIG. 7 is an enlarged view of a portion of FIG. 6 at A;
FIG. 8 is a schematic view of the cushion cylinder in embodiment 1 of the present invention;
FIG. 9 is a schematic view of the return stroke of the piston in embodiment 1 of the present invention;
FIG. 10 is a schematic view showing the overall structure of embodiment 2 of the present invention;
in the figure: 1-outer cylinder; 101-nitrogen chamber; 102-piston rear chamber; 103-piston front cavity; 104-an oil inlet; 105-an oil outlet; 106-drill rod installation cavity; 2-a piston ring; 3-a piston; 301-piston rear end; 302-a second limiting section; 303-piston middle section; 304-a first spacing segment; 305-a striking end; 306-a drainage groove; 4-lowering the cylinder; 5-inner sleeve; 501-oil outlet cavity; 502-mounting holes; 503-oil drainage groove; 504-oil drainage holes; 6-a buffer pad; 7-coating; 701-an outer sleeve oil inlet; 702-a jacket oil outlet; 703-an installation section; 704-a body segment; 705-drill rod mounting holes; 706-a pilot sleeve mounting cavity; 8-a buffer hydraulic cylinder; 801-buffer hydraulic cylinder oil inlet; 802-buffer hydraulic cylinder oil outlet; 803-a buffer cover; 804-a buffer spring; 805-a piston rod; 806-a hydraulic cylinder body; 9-a guide sleeve; 10-a drill rod; 11-an overflow valve; 12-a one-way valve; 13-oil inlet pipe.
Detailed Description
Example 1: as shown in fig. 1-9, a valveless reversing type idle-stroke-prevention hydraulic breaking hammer comprises an outer cylinder 1, wherein a mounting cavity is formed in the outer cylinder 1, a piston 3 is installed in the mounting cavity, an oil delivery hole is formed in the outer cylinder 1, the oil delivery hole is communicated with the mounting cavity and used for reversing the moving direction of the piston 3, an inner sleeve 5 and an outer sleeve 7 are sequentially installed at the position, close to the front end of the piston 3, in the mounting cavity of the outer cylinder 1, a drill rod 10 is installed in the outer sleeve 7, and buffering assemblies used for buffering impact force on the drill rod 10 are arranged at the positions on two sides of the mounting end of the drill rod 10.
The installation cavity in the outer cylinder 1 is a counter bore shape, and the installation cavity specifically comprises a nitrogen chamber 101, a piston rear cavity 102, a piston front cavity 103 and a drill rod installation cavity 106 which are sequentially arranged.
The nitrogen chamber 101, the piston rear cavity 102, the piston front cavity 103 and the drill rod installation cavity 106 are communicated with each other in sequence, and one end of the drill rod installation cavity 106 close to the drill rod 10 penetrates through the end face of the outer cylinder 1 and forms an opening.
The diameters of the inner surfaces of the nitrogen chamber 101, the piston rear cavity 102, the piston front cavity 103 and the drill rod installation cavity 106 gradually increase.
The inner surface diameter of the nitrogen gas chamber 101 is smaller than the inner surface diameter of the piston rear chamber 102.
The diameter of the inner surface of the piston rear chamber 102 is smaller than that of the piston front chamber 103.
The diameter of the inner surface of the piston front cavity 103 is smaller than that of the drill rod installation cavity 106.
The cross section of the piston 3 is in a stepped shaft shape, and the piston 3 specifically comprises a piston rear end 301, a second limiting section 302, a piston middle section 303, a first limiting section 304 and a striking end 305 which are coaxially and integrally connected in sequence.
The outer surface diameter of the piston rear end 301 is smaller than that of the second stopper section 302, and the outer surface diameter of the piston rear end 301 is smaller than that of the inner surface of the nitrogen gas chamber 101.
The diameter of the outer surface of the second stopper section 302 matches the diameter of the inner surface of the rear piston cavity 102.
The diameter of the outer surface of the middle piston section 303 is smaller than the diameter of the outer surface of the second limiting section 302 and the diameter of the outer surface of the rear piston end 301.
The outer surface diameter of the first position-limiting section 304 is larger than that of the piston middle section 303 and smaller than that of the second position-limiting section 302.
The outer surface diameter of the striking end 305 is smaller than the outer surface diameter of the first restraint section 304.
The piston 3 is mounted in a mounting cavity of the outer cylinder 1, and the piston 3 is movable in the axial direction of the mounting cavity for striking the end of the drill rod 10.
After the piston 3 is installed in the installation cavity of the outer cylinder 1, the outer surface of the piston 3 is matched with the inner surface of the installation cavity.
By the design, the diameter of the outer surface of the second limiting section 302 is matched with the diameter of the inner surface of the piston rear cavity 102, and when the piston 3 moves to the side far away from the drill rod 10 in the installation cavity, the second limiting section 302 of the piston 3 is matched with the inner surface of the piston rear cavity 102 to disconnect the communication between the piston rear cavity 102 and the piston front cavity 103.
When the piston 3 moves towards one side close to the drill rod 10 in the installation cavity, the second limiting section 302 of the piston 3 can move into the piston front cavity 103, the diameter of the inner surface of the piston front cavity 103 is larger than that of the inner surface of the piston rear cavity 102, further, the diameter of the inner surface of the piston front cavity 103 is larger than that of the outer surface of the second limiting section 302, then, the piston rear cavity 102 is communicated with the piston front cavity 103, and high-pressure oil in the piston rear cavity 102 can flow into the piston front cavity 103.
The nitrogen chamber 101 is a closed cavity, and the nitrogen chamber 101 is filled with nitrogen.
The piston ring 2 is hermetically installed at the rear end 301 of the piston 3, and the outer surface of the piston ring 2 is hermetically connected with the inner surface of the nitrogen chamber 101 and used for isolating the nitrogen chamber 101 from the rear piston cavity 102.
It can be seen that the piston ring 2 can be used to seal the connection between the piston rear end 301 of the piston ring 2 and the nitrogen gas chamber 101, thereby isolating the nitrogen gas chamber 101 from the piston rear cavity 102, and the piston ring 2 can also guide the movement of the piston 3.
When the piston 3 moves to the side close to the nitrogen gas chamber 101, the piston 3 can compress the nitrogen gas in the nitrogen gas chamber 101, and further the impact force when the piston 3 returns can be buffered by the nitrogen gas in the nitrogen gas chamber 101, which is convenient for use.
The oil delivery hole comprises an oil inlet 104 and an oil outlet 105 which are arranged on the outer cylinder 1, and the oil inlet 104 is communicated with the piston rear cavity 102.
The oil inlet 104 is communicated with an external hydraulic oil source, hydraulic oil in the external hydraulic oil source can enter the piston rear cavity 102 through the oil inlet 104, at the moment, the hydraulic oil can push the piston 3 to move towards one side close to the drill rod 10 to realize a stroke, and the piston 3 impacts the drill rod 10 under the thrust and inertia of the hydraulic oil.
The cross-sectional annular area of the piston middle section 303 of the piston 3 is smaller than the cross-sectional annular area of the piston rear end 301.
By the design, when high-pressure hydraulic oil is injected into the piston rear cavity 102, the piston 3 moves to one side close to the drill rod 10, the piston 3 performs stroke motion at the moment, the drill rod 10 can be impacted, after the piston rear cavity 102 is communicated with the piston front cavity 103, and as can be known from a formula F = PS, the hydraulic oil in the piston front cavity 103 pushes the piston 3 to move to one side far away from the drill rod 10, automatic reversing can be realized, and at the moment, the piston 3 performs return motion.
Therefore, the piston 3 can automatically perform reversing action without externally arranging a reversing valve, so that the valveless reversing type idle-stroke-prevention hydraulic breaking hammer has a simple integral structure and reduces parts.
The oil outlet 105 is arranged on the outer cylinder 1 at a position close to the inner sleeve 5, and the inner sleeve 5
The middle part of the inner sleeve 5 is provided with a mounting hole 502, and the diameter of the inner surface of the mounting hole 502 is matched with the diameter of the outer surface of the striking end 305 of the piston 3.
An oil outlet cavity 501 is formed in one end, close to the piston 3, of the inner sleeve 5, the oil outlet cavity 501 is coaxial with the mounting hole 502 and is communicated with the mounting hole 502, and the diameter of the inner surface of the oil outlet cavity 501 is matched with the diameter of the outer surface of the first limiting section 304 of the piston 3.
An oil drainage groove 503 is formed in the outer surface of the inner sleeve 5 at a position close to the oil outlet cavity 501, and the oil drainage groove 503 is annular.
An oil drainage hole 504 is formed between the oil drainage groove 503 and the oil outlet cavity 501, and the oil outlet cavity 501 is communicated with the oil drainage groove 503 through the oil drainage hole 504.
The inner sleeve 5 is embedded in the drill rod installation cavity 106 of the outer cylinder 1, and one end of the inner sleeve 5 is connected with the connection part of the drill rod installation cavity 106 and the piston front cavity 103 in a propping mode.
The inner sleeve 5 is in clearance fit with the inner surface of the drill rod installation cavity 106 of the outer cylinder 1.
In this embodiment, a seal ring may or may not be additionally provided between the outer surface of the inner sleeve 5 and the joint of the outer cylinder 1.
The striking end 305 of the piston 3 is installed in the installation hole 502 of the inner sleeve 5, and the installation hole 502 can guide the movement of the piston 3, thereby being convenient for use.
An oil outlet 105 on the outer cylinder 1 is communicated with an oil drainage groove 503, and an oil drainage loop is formed among the oil outlet cavity 501, an oil drainage hole 504, the oil drainage groove 503 and the oil outlet 105.
By the design, when the piston 3 is in a stroke stage, hydraulic oil enters the piston rear cavity 102 from the oil inlet 104 to push the piston 3 to move forwards, and the piston 3 impacts the drill rod 10 under the thrust and inertia of the hydraulic oil.
After the piston rear cavity 102 and the piston front cavity 103 are communicated, the first limiting section 304 of the piston 3 moves into the oil outlet cavity 501, the outer surface of the first limiting section 304 is tightly attached to the inner surface of the oil outlet cavity 501 to form a closed structure, and then the first limiting section 304 of the piston 3 cuts off the communication between the oil outlet cavity 501 and the piston front cavity 103.
And because the cross section annular area of the piston middle section 303 of the piston 3 is smaller than the cross section annular area of the piston rear end 301, it can be known from the formula F = PS that the hydraulic oil in the piston front cavity 103 pushes the piston 3 to move to the side far away from the drill rod 10, so that automatic reversing can be realized, and at this time, the piston 3 performs return motion.
As shown in fig. 9, after the piston 3 performs a return movement for a certain distance, the first limiting section 304 moves out of the oil outlet cavity 501, at this time, the front piston cavity 103 is communicated with the oil outlet cavity 501, the pressure of the hydraulic oil in the front piston cavity 103 is released instantaneously, and the hydraulic oil flows out through the oil outlet cavity 501, the oil drain hole 504, the oil drain groove 503 and the oil outlet 105.
At this time, the piston 3 continues to move to the side far away from the drill rod 10 under inertia, and when the piston 3 moves to a specific position, the second limiting section 302 of the piston 3 moves into the piston rear cavity 102, and at this time, the outer surface of the second limiting section 302 is matched with the inner surface of the piston rear cavity 102 to disconnect the communication between the piston rear cavity 102 and the piston front cavity 103.
Then, the piston 3 starts to perform the next stroke movement again by the pressure in the nitrogen chamber 101 and the hydraulic oil in the piston rear chamber 102.
The integral structure of the outer sleeve 7 comprises a mounting section 703 and a main body section 704, the diameter of the outer surface of the mounting section 703 is matched with the diameter of the inner surface of the drill rod mounting cavity 106, and the mounting section 703 of the outer sleeve 7 is embedded in the drill rod mounting cavity 106 of the outer cylinder 1.
In this embodiment, the mounting segment 703 is connected to the shank mounting cavity 106 by a threaded connection.
The diameter of the outer surface of body section 704 matches the diameter of the outer surface of outer cylinder 1.
A drill rod mounting hole 705 is formed in the outer sleeve 7 and located in the middle of the mounting section 703, a pilot sleeve mounting cavity 706 is formed in the middle of the main body section 704, and the drill rod mounting hole 705 and the pilot sleeve mounting cavity 706 are coaxially arranged.
The drill rod mounting hole 705 of the outer sleeve 7 is internally provided with a guide sleeve 9, the guide sleeve 9 is sleeved on the drill rod 10, and the mounting end of the drill rod 10 is arranged in the drill rod mounting hole 705.
The guide sleeve 9 is connected with the outer sleeve 7 in a threaded connection mode.
By the design, the installation end of the drill rod 10 is installed in the drill rod installation hole 705, the drill rod 10 can be conveniently installed on the outer cylinder 1 through the guide sleeve 9, the use is convenient, the whole assembly is convenient, and the use effect is greatly improved.
The buffer assembly comprises a buffer pad 6 and a buffer hydraulic cylinder 8, wherein the buffer pad 6 is arranged between the inner sleeve 5 and the outer sleeve 7.
When the drill rod 10 moves to the side close to the piston 3, the end of the piston 3 can contact the cushion pad 6, and the cushion pad 6 is used for buffering the force of the drill rod 10 moving to the side close to the piston 3.
The contact surfaces of the drill rod 10 and the buffer 6 are conical surfaces respectively.
The central portion of the cushion pad 6 is formed with a central hole having a diameter larger than the outer surface diameter of the striking end 305 of the piston 3.
By adopting the design, the buffering effect can be improved, and the end part of the piston 3 can penetrate through the central hole in the middle of the buffering cushion 6 to realize the impact drill rod 10, so that the use is convenient.
The whole buffering cushion 6 is made of polyurethane materials, and the buffering cushion 6 has the advantages of good rebound resilience, good mechanical property and small compression deformation.
The buffer hydraulic cylinder 8 is arranged between the guide sleeve 9 and the outer sleeve 7, and an oil conveying pipeline for conveying high-pressure hydraulic oil to the buffer hydraulic cylinder 8 is arranged on the outer sleeve 7.
When the piston 3 strikes the drill rod 10, the drill rod 10 moves towards one side far away from the piston 3, and the installation end of the drill rod 10 can be in contact with the buffer hydraulic cylinder 8 at the moment, so that the buffer hydraulic cylinder 8 is used for buffering the impact force of the drill rod 10, the idle striking prevention characteristic is realized, and the impact force is slowed down to protect the drill rod 10 from being damaged.
The whole structure of the buffer hydraulic cylinder 8 is in a ring shape, and the buffer hydraulic cylinder 8 is sleeved on the drill rod 10 through a central hole in the middle.
The buffer hydraulic cylinder 8 is arranged in the guide sleeve mounting cavity 706 of the outer sleeve 7, one end of the buffer hydraulic cylinder 8 is connected with a shaft shoulder at the joint of the guide sleeve mounting cavity 706 and the drill rod mounting hole 705 in a butting mode, and the guide sleeve 9 is connected with the other end of the buffer hydraulic cylinder 8 in a butting mode.
By the design, the buffer hydraulic cylinder 8 can be installed in the outer sleeve 7, the axial position of the buffer hydraulic cylinder 8 can be limited through the guide sleeve 9, and the assembly, installation and use are convenient.
The buffer 6 and the buffer hydraulic cylinder 8 are respectively arranged at the front side and the rear side of the installation end of the drill rod 10.
Can be used for injecing the axial position of drill rod 10 through blotter 6 and buffer hydraulic cylinder 8, facilitate the use, compare with prior art, can cancel the stop device to drill rod 10 through blotter 6 and buffer hydraulic cylinder 8, make overall structure simpler.
The buffer hydraulic cylinder 8 comprises a hydraulic cylinder main body 806, a piston body is installed in the hydraulic cylinder main body 806, a plurality of piston rods 805 are installed on one side of the piston body close to the piston 3, the piston rods 805 are annular and arranged at intervals, and the other ends of the piston rods 805 extend to the outside of the hydraulic cylinder main body 806 and are fixedly connected with a buffer cover 803.
The buffer cover 803 is slidably connected to the cylinder body 806 at a side close to the cylinder body 806.
Thus, when the impact force is applied to the drill rod 10, the brazing material 10 moves to the side away from the piston 3, and the mounting end of the brazing material 10 moves to the side close to the buffer cap 803, so that the impact force applied to the brazing material 10 acts on the buffer cap 803.
After the impact force is received by the buffer cover 803, the buffer cover 803 moves to a side close to the hydraulic cylinder body 806, at this time, the buffer cover 803 drives the piston rod 805 to move to a side close to the hydraulic cylinder body 806, and at this time, the impact force can be buffered by the reaction force of the hydraulic oil in the hydraulic cylinder body 806, so that the impact force is reduced to protect the drill rod 10 from being damaged.
The piston rod 805 is respectively sleeved with a buffer spring 804, and two ends of the buffer spring 804 are respectively connected with the buffer cover 803 and the hydraulic cylinder main body 806 in a butting mode.
The buffer spring 804 outputs elastic force to push the buffer cover 803 to drive the piston rod 805 to move to the side close to the piston 3.
The hydraulic cylinder body 806 is provided with a buffer hydraulic cylinder oil inlet 801 and a buffer hydraulic cylinder oil outlet 802 respectively, and is used for controlling the buffer hydraulic cylinder 8 to change direction.
The oil conveying pipeline comprises an outer sleeve oil inlet 701 and an outer sleeve oil outlet 702 which are arranged on the outer sleeve 7, the outer sleeve oil inlet 701 is communicated with an oil inlet 801 of the buffer hydraulic cylinder, and the outer sleeve oil outlet 702 is communicated with an oil outlet 802 of the buffer hydraulic cylinder.
An oil inlet pipe 13 is communicated with the position of the outer sleeve oil inlet 701, an overflow valve 11 is connected in parallel with the position, close to the outer sleeve oil inlet 701, of the oil inlet pipe 13, and a check valve 12 is connected in series with the downstream position of the oil inlet pipe 13.
The overflow valve 11 is connected in parallel to the oil inlet pipe 13, and excess hydraulic oil in the buffer hydraulic cylinder 8 is released through the overflow valve 11.
The check valve 12 controls the flow direction of the hydraulic oil in the oil inlet pipe 13, when the hydraulic oil in the oil inlet pipe 13 flows to the oil inlet 701 of the outer sleeve, the check valve 12 is turned on, otherwise, when the hydraulic oil in the oil inlet pipe 13 flows in the reverse direction, the check valve 12 is turned off.
The design is that when the piston 3 is in the stroke stage, the piston 3 impacts the drill rod 10 under the action of the thrust and inertia of the hydraulic oil.
At this time, the hydraulic oil enters the oil inlet 801 of the buffer hydraulic cylinder through the oil inlet pipe 13 via the check valve 12 and the outer sleeve oil inlet 701, enters the hydraulic cylinder main body 806, and then enters the outer sleeve oil outlet 702 from the oil outlet 802 of the buffer hydraulic cylinder to form a closed loop.
When the drill rod 10 is impacted, as shown in fig. 8, the drill rod 10 moves to the right, the mounting end of the drill rod 10 presses the buffer cover 803 and drives the piston rod 805 to move to the right, and when the stress on the buffer cover 803 is large enough, the piston rod 805 pushes the piston body to move in the cylinder main body 806, and the piston body seals the buffer cylinder oil outlet 802.
At this time, the hydraulic oil in the hydraulic cylinder main body 806 cannot be discharged through the oil outlet 802 of the buffer hydraulic cylinder, the hydraulic oil flows back to the oil inlet 801 of the buffer hydraulic cylinder, and the check valve 12 is arranged on the pipeline, so that the hydraulic oil cannot be unloaded at this time, the purpose of buffering is achieved, and the redundant hydraulic oil after buffering is released through the overflow valve 11.
When the force transmission on the drill rod 10 is completed, the buffer cover 803 returns to the original position under the action of the buffer spring 804, at the moment, the piston rod 805 moves leftwards to perform return operation, the oil outlet 802 of the buffer hydraulic cylinder is opened, and at the moment, the oil inlet 801 of the buffer hydraulic cylinder and the oil outlet 802 of the buffer hydraulic cylinder continue to form a closed loop.
In use, when the piston 3 is in a stroke stage, hydraulic oil enters the piston rear cavity 102 from the oil inlet 104 to push the piston 3 to move forward, and the piston 3 impacts the drill rod 10 under the thrust and inertia of the hydraulic oil.
After the piston rear cavity 102 and the piston front cavity 103 are communicated, the first limiting section 304 of the piston 3 moves into the oil outlet cavity 501 at the moment, the outer surface of the first limiting section 304 is tightly attached to the inner surface of the oil outlet cavity 501 to form a closed structure, the outer surface of the first limiting section 304 can be used for plugging the oil drainage hole 504 at the moment, and then the first limiting section 304 of the piston 3 cuts off the communication between the oil outlet cavity 501 and the piston front cavity 103.
And because the cross section annular area of the piston middle section 303 of the piston 3 is smaller than the cross section annular area of the piston rear end 301, it can be known from the formula F = PS that the hydraulic oil in the piston front cavity 103 pushes the piston 3 to move to the side far away from the drill rod 10, so that automatic reversing can be realized, and at this time, the piston 3 performs return motion.
As shown in fig. 9, after the piston 3 performs a return movement for a certain distance, the first limiting section 304 moves out of the oil outlet cavity 501, at this time, the front piston cavity 103 is communicated with the oil outlet cavity 501, the pressure of the hydraulic oil in the front piston cavity 103 is released instantaneously, and the hydraulic oil flows out through the oil outlet cavity 501, the oil drain hole 504, the oil drain groove 503 and the oil outlet 105.
At this time, the piston 3 continues to move to the side far away from the drill rod 10 under inertia, and when the piston 3 moves to a specific position, the second limiting section 302 of the piston 3 moves into the piston rear cavity 102, and at this time, the outer surface of the second limiting section 302 is matched with the inner surface of the piston rear cavity 102 to disconnect the communication between the piston rear cavity 102 and the piston front cavity 103.
Then, the piston 3 starts to perform the next stroke movement again by the pressure in the nitrogen chamber 101 and the hydraulic oil in the piston rear chamber 102.
When the piston 3 is in a stroke stage, the piston 3 impacts the drill rod 10 under the action of the thrust and inertia of hydraulic oil;
at this time, the hydraulic oil enters the oil inlet 801 of the buffer hydraulic cylinder through the oil inlet pipe 13 via the check valve 12 and the outer sleeve oil inlet 701, enters the hydraulic cylinder main body 806, and then enters the outer sleeve oil outlet 702 from the oil outlet 802 of the buffer hydraulic cylinder to form a closed loop.
When the drill rod 10 is subjected to an impact force, as shown in fig. 8, the drill rod 10 moves to the right, and the mounting end of the drill rod 10 presses the buffer cover 803 and drives the piston rod 805 to move to the right.
Piston rod 805 pushes against the piston body moving within cylinder body 806 and causes the piston body to close off cushioning cylinder outlet port 802.
At this time, the hydraulic oil in the hydraulic cylinder main body 806 cannot be discharged through the oil outlet 802 of the buffer hydraulic cylinder, the hydraulic oil flows back to the oil inlet 801 of the buffer hydraulic cylinder, and the check valve 12 is arranged on the pipeline, so that the hydraulic oil cannot be unloaded, the piston 3 can be prevented from continuing to advance, and the impact force on the piston 3 has an unloading effect.
When the idle driving phenomenon occurs, the displacement of the piston 3 exceeds the maximum displacement, the pressure in the hydraulic cylinder main body 806 is too large, the pressure is greater than the opening pressure of the overflow valve 11, the overflow valve 11 automatically opens under the action of hydraulic oil pressure, and redundant hydraulic oil is released through the overflow valve 11, so that the idle driving prevention phenomenon is realized, and the piston 3 and the drill rod 10 are protected.
When the force transmission on the drill rod 10 is completed, the buffer cover 803 returns to the original position under the action of the buffer spring 804, at the moment, the piston rod 805 moves leftwards to perform return operation, the oil outlet 802 of the buffer hydraulic cylinder is opened, and at the moment, the oil inlet 801 of the buffer hydraulic cylinder and the oil outlet 802 of the buffer hydraulic cylinder continue to form a closed loop.
The overall structure of the inner sleeve 5, the cushion 6 and the outer sleeve 7 is the same as that of the cushion 6 and the outer sleeve 7 in embodiment 1.
A plurality of oil drainage grooves 306 are formed in the outer surface of the first limiting section 304 of the piston 3 at a position close to one end of the inner sleeve 5, and the oil drainage grooves 306 are annularly arranged along the outer surface of the first limiting section 304 at intervals.
Design like this, accessible draining recess 306 can improve the draining effect, avoids hydraulic oil to pile up in the oil outlet cavity 501 of endotheca 5, facilitates the use.
It will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in the embodiments described above without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims.
Claims (10)
1. The utility model provides a valveless switching-over formula air defense is beaten hydraulic breaking hammer which characterized in that: including integral type outer cylinder (1), set up the installation cavity in outer cylinder (1), piston (3) are installed to the installation cavity, the oil transmission hole has been seted up on outer cylinder (1), oil transmission hole and installation cavity intercommunication are used for reversing the moving direction of piston (3), endotheca (5) and overcoat (7) are installed in proper order to be close to piston (3) front position department in the installation cavity of outer cylinder (1), install in overcoat (7) and lead just cover (9), lead and install drill rod (10) in just cover (9), the installation end of drill rod (10) is installed in overcoat (7), the both sides position department of drill rod (10) installation end is provided with the buffering subassembly that is used for carrying out the buffering to the impact force on drill rod (10).
2. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 3, wherein: a piston rear cavity (102), a piston front cavity (103) and a nitrogen chamber (101) are arranged between the outer surface of the piston (3) and the inner surface of the mounting cavity, and a piston ring (2) used for packaging the nitrogen chamber (101) is mounted on the piston (3) in a sealing mode.
3. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 1, wherein: the diameter of the outer surface of the second limiting section (302) on the piston (3) is matched with the diameter of the inner surface of the piston rear cavity (102) in the installation cavity.
4. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 2, wherein: the cross section annular area of the piston middle section (303) on the piston (3) is smaller than that of the piston rear end (301) on the piston (3).
5. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 4, wherein: the oil conveying hole comprises an oil inlet (104) and an oil outlet (105) which are arranged on the outer cylinder (1), the oil inlet (104) is communicated with the piston rear cavity (102), and the oil outlet (105) is arranged on the outer cylinder (1) and close to the inner sleeve (5).
6. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 5, wherein: the middle part of the inner sleeve (5) is provided with a mounting hole (502) and an oil outlet cavity (501), the diameter of the inner surface of the mounting hole (502) is matched with the diameter of the outer surface of the striking end (305) of the piston (3), and the diameter of the inner surface of the oil outlet cavity (501) is matched with the diameter of the outer surface of the first limiting section (304) of the piston (3).
7. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 6, wherein: an oil drainage groove (503) is formed in the position, close to the oil outlet cavity (501), on the outer surface of the inner sleeve (5), an oil drainage hole (504) is formed between the oil drainage groove (503) and the oil outlet cavity (501), the oil outlet cavity (501) is communicated with the oil drainage groove (503) through the oil drainage hole (504), and the oil outlet (105) is communicated with the oil drainage groove (503).
8. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 7, wherein: the buffer assembly comprises a buffer pad (6) and a buffer hydraulic cylinder (8), the buffer pad (6) is installed between an inner sleeve (5) and an outer sleeve (7), the buffer hydraulic cylinder (8) is installed between a guide sleeve (9) and the outer sleeve (7), and an oil conveying pipeline used for conveying hydraulic oil for the buffer hydraulic cylinder (8) is arranged on the outer sleeve (7).
9. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 8, wherein: the buffering hydraulic cylinder (8) comprises a hydraulic cylinder main body (806), a piston body is installed in the hydraulic cylinder main body (806), a piston rod (805) is installed on the piston body, the other end of the piston rod (805) extends to the outside of the hydraulic cylinder main body (806) and is fixedly connected with a buffering cover (803), a buffering spring (804) is arranged on the piston rod (805), and two ends of the buffering spring (804) are respectively connected with the buffering cover (803) and the hydraulic cylinder main body (806) in a jacking mode.
10. The valveless reversing idle-shooting prevention hydraulic breaking hammer according to claim 9, wherein: the oil pipeline comprises an outer sleeve oil inlet (701) and an outer sleeve oil outlet (702) which are arranged on an outer sleeve (7), the outer sleeve oil inlet (701) is communicated with a buffering hydraulic cylinder oil inlet (801) which is arranged on a hydraulic cylinder main body (806), the outer sleeve oil outlet (702) is communicated with a buffering hydraulic cylinder oil outlet (802) which is arranged on the hydraulic cylinder main body (806), an oil inlet pipe (13) is communicated with the outer sleeve oil inlet (701), an overflow valve (11) is connected to the oil inlet pipe (13) in parallel, and a check valve (12) is connected to the downstream position of the oil inlet pipe (13) in series.
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| CN202111012875.XA CN113718884B (en) | 2021-08-31 | 2021-08-31 | Valveless reversing type idle-driving prevention hydraulic breaking hammer |
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| CN202111012875.XA CN113718884B (en) | 2021-08-31 | 2021-08-31 | Valveless reversing type idle-driving prevention hydraulic breaking hammer |
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| CN113718884B CN113718884B (en) | 2022-12-09 |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201255153Y (en) * | 2008-09-17 | 2009-06-10 | 兰州金路交通设施有限责任公司 | Differential pressure type internal inverting automatic cycle oil cylinder |
| CN102410275A (en) * | 2011-09-08 | 2012-04-11 | 常熟理工学院 | Valve-control-free self-flow-distribution gas and liquid combined acting impactor |
| CN103352895A (en) * | 2013-06-28 | 2013-10-16 | 山河智能装备股份有限公司 | Hydraulic impacter |
| CN104563117A (en) * | 2014-11-21 | 2015-04-29 | 中南大学 | Useless driving prevention cushioning device for hydraulic pile driving hammer |
| WO2016099162A1 (en) * | 2014-12-19 | 2016-06-23 | 주식회사수산중공업 | Hammering body for hydraulic hammering device |
| CN109518754A (en) * | 2018-08-26 | 2019-03-26 | 赵德朝 | A kind of novel hydraulic crushing hammer |
| CN111894940A (en) * | 2020-08-05 | 2020-11-06 | 合力（天津）能源科技股份有限公司 | Mechanical oil cylinder structure capable of automatically reciprocating |
-
2021
- 2021-08-31 CN CN202111012875.XA patent/CN113718884B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201255153Y (en) * | 2008-09-17 | 2009-06-10 | 兰州金路交通设施有限责任公司 | Differential pressure type internal inverting automatic cycle oil cylinder |
| CN102410275A (en) * | 2011-09-08 | 2012-04-11 | 常熟理工学院 | Valve-control-free self-flow-distribution gas and liquid combined acting impactor |
| CN103352895A (en) * | 2013-06-28 | 2013-10-16 | 山河智能装备股份有限公司 | Hydraulic impacter |
| CN104563117A (en) * | 2014-11-21 | 2015-04-29 | 中南大学 | Useless driving prevention cushioning device for hydraulic pile driving hammer |
| WO2016099162A1 (en) * | 2014-12-19 | 2016-06-23 | 주식회사수산중공업 | Hammering body for hydraulic hammering device |
| CN109518754A (en) * | 2018-08-26 | 2019-03-26 | 赵德朝 | A kind of novel hydraulic crushing hammer |
| CN111894940A (en) * | 2020-08-05 | 2020-11-06 | 合力（天津）能源科技股份有限公司 | Mechanical oil cylinder structure capable of automatically reciprocating |
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|---|---|
| CN113718884B (en) | 2022-12-09 |
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