An impact device, a control method therefor, and a construction machine and a method of operating the same

Abstract

The present application relates to a kind of impact device and its control method and engineering machinery and its operation method, belong to the technical field of impact operation machinery such as impact breaking hammer, rock drilling, pile driving, deep-sea pile driving, dynamic compaction, metal forming etc..The existing problems of impact device, such as cylinder piston easy to be damaged, hydraulic impact of emptying, piston and cylinder wear and tear, etc.are solved.The main fixed connecting seat for connecting carrier, ram, hydraulic cylinder and ram guide part connected with the main fixed connecting seat are included, the cylinder body of hydraulic cylinder is connected with the main fixed connecting seat, and the piston of hydraulic cylinder is slidingly installed in the cylinder body;Ram is located outside the cylinder body, ram guide part is used for axially guiding and radially limiting ram, piston rod is used for driving ram to do axial reciprocating impact motion along ram guide part, and ram does not bear the hydraulic seal of hydraulic cylinder.The present application is used for impact breaking hammer, rock drilling, pile driving, deep-sea pile driving, dynamic compaction and metal forming etc.impact operation.

Description

Technical Field

[0001] This invention relates to the fields of impact operation machinery technology and control technology, such as impact breakers, rock drills, pile drivers, deep-sea pile drivers, dynamic compaction, and metal forming. In particular, it relates to an impact device and its control method, as well as engineering machinery and its operation method. Background Technology

[0002] Impact machinery, represented by hydraulic breakers, is widely used in mining, construction, road breaking, foundation engineering, and deep-sea operations. Its basic working principle is: a nitrogen chamber stores energy, a reversing valve controls the flow of hydraulic oil, driving a piston to reciprocate. The piston impacts a working device (such as a chisel, pile cap, or tamping plate) to perform the operation. However, existing technology has revealed some insurmountable shortcomings in long-term application:

[0003] Traditional hydraulic breakers generally employ an integrated "piston-hammer" design. In this structure, the piston rod directly acts as the hammer, moving at high speed under the drive of hydraulic oil and directly impacting external objects. This means that this moving component must simultaneously perform two functions: first, a hydraulic sealing function, requiring its outer surface to have extremely high smoothness and dimensional accuracy to cooperate with the sealing ring to maintain the airtightness of the hydraulic chamber; second, an impact function, requiring its ends to withstand repeated, severe impacts. This dual-function structure exposes fatal flaws under high-energy impact conditions. When the hammer impacts an external object at high speed, a huge radial force is transmitted to this component, causing it to sway slightly, which in turn causes severe friction and scratches on the seals and inner wall of the hydraulic cylinder. Once scratches appear on the sealing surface, hydraulic oil leakage occurs, the system efficiency drops sharply, and eventually, it fails completely. This problem fundamentally limits the development of traditional hydraulic breakers towards higher impact energy.

[0004] 1. Inherent defects of the built-in piston in the impact device

[0005] Traditional impact devices feature a hydraulic piston embedded within the cylinder, sliding precisely against the cylinder's inner wall, requiring extremely high machining precision and sealing requirements. Because the piston's rapid movement generates impact, traditional flexible seals cannot withstand the impact. Therefore, the piston and cylinder in a hydraulic breaker rely on a metal-to-metal, small-pitch oil film seal. When the impact energy and piston mass increase, the piston generates enormous lateral forces during high-speed movement, leading to severe wear between the piston and the cylinder wall, reduced sealing capacity, and even cylinder scoring. To maintain the seal, the piston's mass and impact energy must be limited, thus limiting the impact impulse of the impact device. Furthermore, the built-in piston is a wear component; repair and replacement require disassembling the entire cylinder, resulting in long downtime and high maintenance costs.

[0006] In traditional designs, the piston serves both to seal the hydraulic oil and to withstand the impact of the impact drill rod. This compact design with few parts has facilitated the widespread adoption of hydraulic breakers. However, with the demands of modern production, the required impact kinetic energy for hydraulic breakers is increasing. Limited by the upper limits of gas spring pressure and the hydraulic drive hydraulic system of the breaker carrier excavator, the diameter of the hydraulic breaker piston has become increasingly larger to meet the demands of this massive kinetic energy. However, as the piston size increases, it has been found that the impact force on the piston cylinder sidewall under massive impacts also increases. Often, the piston deforms slightly within a short period of use. The hydraulic system, which requires precision to seal the hydraulic oil, struggles to maintain ideal precision under such impacts, failing to effectively seal the hydraulic oil. This significantly shortens the breaker's lifespan, resulting in substantial waste. Currently, only a handful of domestic manufacturers can produce pistons with a diameter of 230 mm. Larger diameters are theoretically achievable, but their practical use is limited due to their lack of durability.

[0007] When attempting to increase impact energy, it is necessary to either increase the impact mass or the impact velocity. However:

[0008] Increased impact mass: The piston rod diameter and mass increase accordingly, as does the sealing surface diameter. The impact force generated by the large-mass piston at the moment of impact is directly transmitted to the cylinder sealing surface, causing severe cylinder scoring, scratches, and oil leaks. Approximately 70% of serious failures in traditional hydraulic breakers originate from cylinder scoring.

[0009] Increased impact speed: Increased piston rod movement speed, increased sealing surface linear velocity, increased frictional heat, and rapid wear and failure of the piston and cylinder.

[0010] This technological bottleneck limits the theoretical upper limit of the impact mass of traditional impact devices. This theoretical upper limit is the compressive or tensile strength exerted on the metal by friction and collision between the piston cylinder and the piston. Taking hydraulic breakers as an example, the largest known conventional products in the world have a hammer (chisel) mass of approximately 500-600 kg, a hammer diameter of approximately 280 mm, and a single impact energy of approximately 20,000-30,000 joules. Exceeding this limit leads to a sharp increase in cylinder scoring failure rates, rendering the equipment unreliable. This is the fundamental reason why there are almost no traditional hydraulic breakers in the world with a hammer diameter exceeding 280 mm and a single impact energy exceeding 50,000 joules.

[0011] Taking deep-sea piling machines as an example, the mass of the impact piston in traditional solutions is also limited by the sealing structure. Usually, the mass is close to the engineering limit at the level of 200-300 tons. Further increasing the mass would cause the sealing system to be unable to withstand it.

[0012] In addition, in the traditional structure, the piston rod is rigidly connected to the hammer, and the impact rebound force is directly transmitted back to the cylinder piston, causing the piston rod to bend, the seal to be damaged, and the cylinder to break. The damage is more serious under dry firing conditions.

[0013] Traditional hydraulic cylinders use a piston that extends into a nitrogen chamber to compress nitrogen for energy storage. Due to the overall size of the equipment, the nitrogen chamber is relatively small, resulting in a rapid change in pressure during nitrogen storage. The piston area must be designed according to the maximum nitrogen pressure, which wastes the bearing area of ​​the hydraulic piston. Hydraulic cylinders are mostly solid structures that cannot accommodate nitrogen, the nitrogen chamber volume is limited, the compression ratio is large, and the hydraulic pressure fluctuates greatly.

[0014] 2. Damage to the cylinder piston caused by impact reaction force

[0015] When the piston rod strikes the chisel, the enormous reaction force is directly transmitted to the piston in the hydraulic cylinder, causing the piston rod to bend, the seals to be damaged, and the cylinder to crack.

[0016] 3. Disadvantages of existing dry-firing buffer methods

[0017] Existing impact devices typically employ hydraulic damping for cushioning under no-load conditions: when the piston passes its normal stroke, it compresses the hydraulic oil within the sealed chamber. This hydraulic oil is then discharged through a flow-limiting orifice (throttle orifice), utilizing hydraulic resistance to generate damping force and cushion the piston's impact. While this cushioning method can absorb some energy, it has serious drawbacks: the flow-limiting orifice causes a momentary increase in hydraulic oil pressure, generating localized pressure peaks. These peaks are transmitted through the hydraulic lines to the main directional valve, hydraulic pump, and carrier hydraulic system, causing impact damage to hydraulic components. Furthermore, hydraulic damping has low energy conversion efficiency; most of the impact energy is converted into heat energy in the hydraulic oil, leading to increased oil temperature and accelerated seal aging. This is one of the main reasons for the short seal life of traditional hydraulic breakers.

[0018] 4. Traditional dynamic compaction machines are large in size and operate slowly.

[0019] Traditional dynamic compaction machines use a crane to lift a hammer weighing several to tens of tons to a height of twenty to thirty meters before releasing it, relying on the gravitational potential energy of the hammer's free fall to impact the ground. This method has the following drawbacks: First, it requires a large crane as the lifting equipment, making the entire machine bulky and difficult to relocate; second, each compaction requires completing a full cycle of "lift-release-fall-lift again," resulting in a low operating frequency, typically only a few times per minute; third, the large lifting height results in a high center of gravity, posing a risk of tipping over, and also requires a high degree of flatness in the work site; fourth, the impact energy of free fall is limited by the hammer's mass and the lifting height, making it impossible to achieve high-frequency continuous impacts. Summary of the Invention

[0020] To address the problems of existing impact devices, such as easy wear of pistons and cylinders in high-impact (impact energy exceeding 30,000 joules) devices, hindering their practical industrial application, and the issues of easily damaged cylinder pistons, dry-firing hydraulic impact, and wear and scoring of the piston and cylinder, this invention provides an impact device, its control method, and engineering machinery and its operation method. Specifically, this invention provides an impact device and its control method, as well as engineering machinery and its operation method, where the impact hammer is installed outside the hydraulic cylinder and used solely for impact, without requiring the hammer to bear the sealing hydraulic pressure. The impact device of this invention is applicable to various equipment that utilizes the principle of impact for operation, including but not limited to hydraulic breakers, rock drills, pile drivers, deep-sea pile drivers, compactors, impact drills, and metal forming impact equipment.

[0021] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0022] An impact device includes: a main fixed connecting seat 1 for connecting a vehicle, a hammer 2, a hydraulic cylinder 3, and a hammer guide connected to the main fixed connecting seat 1. The cylinder body 301 of the hydraulic cylinder 3 is connected to the main fixed connecting seat 1, and the piston 302 of the hydraulic cylinder 3 is slidably installed inside the cylinder body 301. The hammer 2 is located outside the cylinder body 301. The hammer guide is used to axially guide and radially limit the hammer 2. The piston rod 303 is used to drive the hammer 2 to perform axial reciprocating impact motion along the hammer guide. The hammer 2 does not provide hydraulic sealing for the hydraulic cylinder 3. The hydraulic sealing is achieved by the cooperation between the piston 302 and the cylinder body 301 of the hydraulic cylinder 3.

[0023] Furthermore, the hammer guide is a lower housing 4, and the hammer 2 slides in contact with the inner wall of the lower housing 4; the lower housing 4 is fixedly connected to the main fixed connecting seat 1.

[0024] Furthermore, the hammer guide is a guide structure 5 disposed on the main fixed connecting seat 1; it also includes a guided component 6 fixedly connected to the hammer 2, and the guided component 6 slides in cooperation with the guide structure 5 of the main fixed connecting seat 1.

[0025] Furthermore, the output end of the piston rod 303 is driven to connect to the hammer 2. When the piston rod 303 extends, it drives the hammer 2 to move in the impact direction. When the piston rod 303 retracts, it drives the hammer 2 to move in the retraction direction.

[0026] Furthermore, the output end of the piston rod 303 is integrally manufactured or fixedly connected to the hammer 2, and the two complete the impact synchronously; or, the output end of the piston rod 303 is movably connected to the hammer 2, and the piston rod 303 drives the hammer 2 to accelerate and then disengages from it, and the hammer 2 completes the impact by relying on inertia.

[0027] Furthermore, when the output end of the piston rod 303 is movably connected to the hammer 2;

[0028] It also includes a limiting cap 7, which is connected to the hammer 2; the limiting cap 7 is provided with a limiting structure 701, and the output end of the piston rod 303 is provided with a flange structure 304, which is disposed between the limiting structure 701 and the hammer 2; the limiting structure 701 and the hammer 2 are provided with a movable stroke for the flange structure 304 to move axially along the piston rod 303; the flange structure 304 can drive the hammer 2 to move in the retraction direction of the piston rod 303 by engaging with the limiting structure 701; the piston rod 303 and / or the flange structure 304 can drive the hammer 2 to move in the direction of impact.

[0029] Furthermore, the piston 302 divides the cylinder 301 into a first chamber 3011 and a second chamber 3012. The first chamber 3011 is filled with hydraulic oil, and the second chamber 3012 is filled with high-pressure gas and / or hydraulic oil at room temperature.

[0030] When the second chamber 3012 is filled with high-pressure gas at room temperature, the piston 302 is a hollow cup-shaped structure with its opening facing the high-pressure gas chamber at room temperature and communicating with it. The hollow cup-shaped structure is used to expand the total volume of the high-pressure gas chamber at room temperature, thereby reducing the compression ratio when the high-pressure gas at room temperature is compressed and reducing the weight of the piston 302.

[0031] Furthermore, the hydraulic cylinder 3 is a negative pressure oil-replenishing variable cross-section hydraulic cylinder;

[0032] The cross-sectional area of ​​the negative pressure oil-replenishing variable cross-section hydraulic cylinder changes in an orderly manner according to a preset law during the sliding process. When the external load is small, the bearing area is actively reduced to increase the movement speed, and when the external load is large, the bearing area is actively increased to increase the driving force. The control of the negative pressure oil-replenishing variable cross-section hydraulic cylinder is based on the negative pressure oil replenishment effect, and the bearing area is actively adjusted according to the load change.

[0033] Furthermore, it also includes a high-pressure gas chamber at room temperature located away from the piston end of the hammer 2. The piston 302 of the hydraulic cylinder 3 extends into the high-pressure gas chamber at room temperature, forming an impact device with combined linkage of hydraulic cylinder and high-pressure gas at room temperature.

[0034] Furthermore, it also includes a buffer component 8, which is connected to a fixed connector on the main fixed connecting seat 1; when the hammer 2 moves to the set position, the hammer 2 or the component fixedly connected to the hammer 2 abuts against the buffer component 8 to achieve buffering.

[0035] Furthermore, it also includes a buffer rod 9, one end of which is connected to the hammer 2, and the other end of which is used to abut against the buffer component 8 to achieve buffering.

[0036] An engineering machine, comprising the aforementioned impact device.

[0037] Furthermore, the engineering machinery includes hydraulic breakers, down-the-hole drills, top hammer drills, hydraulic pile hammers, vibratory pile hammers, dynamic compaction machines, stamping presses, forging presses, die forging hammers, tunnel boring machines, deep-sea pile hammers, underwater breakers, or seabed compactors.

[0038] The control method for the impact device includes the following steps:

[0039] S1: The hydraulic system drives the piston 302 inside the hydraulic cylinder 3 to move, and drives the hammer 2 located outside the hydraulic cylinder 3 through the piston rod 303, so that the hammer 2 moves toward the object being impacted;

[0040] S2: The hammer 2 strikes the object being impacted, applying an impact;

[0041] S3: After the impact is completed, the hydraulic system drives the piston 302 to retract, driving the hammer 2 to retract, so as to carry out the next impact.

[0042] Furthermore, the impact device is the impact device according to claim 6, and the control method further includes:

[0043] In step S1, the flange structure 304 at the output end of the piston rod 303 abuts against the limiting structure 701, pushing the hammer 2 to move faster toward the object being impacted.

[0044] After step S1 and before step S2, there is also a disengagement step: the piston rod 303 stops or decelerates, causing the flange structure 304 to disengage from the limiting structure 701, and the hammer 2 and the piston rod 303 to achieve motion decoupling; the hammer 2 completes the impact in step S2 by relying on its own inertia.

[0045] In step S3, the piston rod 303 retracts, the flange structure 304 abuts against the limiting structure 701, and drives the hammer 2 to retract.

[0046] Furthermore, the control method also includes:

[0047] In step S1, the output end of the piston rod 303 moves synchronously with the hammer 2 toward the object being impacted, accelerating towards it.

[0048] In step S2, the piston rod 303 moves synchronously with the hammer 2 to strike the object being impacted, thus applying an impact.

[0049] In step S3: After the impact is completed, the hydraulic system drives the piston 302 to retract, driving the hammer 2 to retract for the next impact.

[0050] Furthermore,

[0051] After step S2 and before step S3, the hammer 2 or the buffer rod 9 only comes into contact with the buffer component 8 when the hammer 2 moves toward the object being impacted and passes its set position. The buffer component 8 absorbs the impact energy independently of the hydraulic system. Otherwise, the hammer 2 or the buffer rod 9 does not come into contact with the buffer component 8.

[0052] An impact operation method for engineering machinery, characterized in that the impact operation is performed using the aforementioned control method.

[0053] The present invention, by employing the above-mentioned technology, has the following positive effects compared with the prior art:

[0054] (1) In this invention, the hammer and the hydraulic cylinder piston are set separately. The hammer is located outside the hydraulic cylinder and does not undertake the hydraulic sealing function. This solves the problem that in the traditional integrated design of "piston-hammer", the moving component needs to take into account both "hydraulic sealing" and "impact". The piston in the hydraulic cylinder is only responsible for hydraulic sealing and driving the piston rod to move. It does not need to bear the impact force. The hammer is dedicated to the impact function. Its size and mass can be designed according to the impact energy requirements without being limited by the sealing accuracy.

[0055] This design fundamentally avoids the problems of piston lateral swaying, scratching of the cylinder inner wall and seals, and hydraulic oil leakage caused by radial force during impact, which are common in traditional structures. It effectively solves problems such as piston wear and cylinder scoring, significantly improving the sealing reliability and service life of the hydraulic cylinder. Simultaneously, it eliminates the need to limit the hammer's mass and size to maintain a seal, breaking the upper limit of impact energy in traditional impact devices. This allows for the design and application of larger diameter hammers, meeting the high impact kinetic energy requirements of scenarios such as mining and deep-sea operations, and solving the pain points of difficult manufacturing and poor durability of large pistons in existing technologies. Furthermore, a replaceable bushing can be installed between the hammer and the hammer guide as an independent wear part, eliminating the need to disassemble the entire hydraulic cylinder during maintenance and replacement, shortening downtime and reducing maintenance costs.

[0056] (2) The present invention achieves effective isolation between the impact reaction force and the hydraulic cylinder through the movable connection design of the piston rod and the hammer. When the hammer strikes the object being impacted, the piston rod and the hammer can be separated. The huge reaction force generated by the impact only acts on the hammer and will not be directly transmitted to the piston and cylinder of the hydraulic cylinder. This completely solves the problem that the reaction force causes the piston rod to bend, the piston cylinder seal to be damaged, and the cylinder to break in the traditional rigid connection structure.

[0057] (3) The present invention is provided with a buffer component. When the hammer is firing in the dry state, the buffer component absorbs the impact energy and avoids the rigid collision of the component caused by the dry impact. Attached Figure Description

[0058] Figure 1 This is a front view of an impact device according to the present invention;

[0059] Figure 2 This is a side view of an impact device according to the present invention;

[0060] Figure 3 This is a rear view of an impact device according to the present invention;

[0061] Figure 4 This is an exploded view of an impact device according to the present invention;

[0062] Figure 5 This is an exploded view of an impact device according to the present invention;

[0063] Figure 6 This is an exploded view of an impact device according to the present invention;

[0064] Figure 7 This is a partial three-dimensional structural diagram of an impact device according to the present invention;

[0065] Figure 8 This is a partial three-dimensional structural diagram of an impact device according to the present invention;

[0066] Figure 9 This is a cross-sectional view of the piston rod retraction limit position of an impact device according to the present invention;

[0067] Figure 10 This is a cross-sectional view of the piston rod of an impact device according to the present invention when it contacts the hammer;

[0068] Figure 11 This is a cross-sectional view of the piston rod at its extreme extension position in an impact device according to the present invention;

[0069] Figure 12 This is a cross-sectional view of the piston rod and / or flange structure of an impact device according to the present invention being separated from the hammer;

[0070] Figure 13 This is a cross-sectional view of an embodiment of the hydraulic cylinder of an impact device according to the present invention;

[0071] Figure 14 This is a cross-sectional three-dimensional structural diagram of an impact device according to the present invention.

[0072] In the attached diagram: 1. Main fixed connecting seat; 2. Impact hammer; 3. Hydraulic cylinder; 301. Cylinder body; 3011. First chamber; 3012. Second chamber; 302. Piston; 303. Piston rod; 304. Flange structure; 4. Lower shell; 401. Opening; 402. Stepped surface; 403. Main body section; 404. Contraction section; 5. Guide structure; 6. Guided component; 7. Limiting cap; 701. Limiting structure; 7011. Second center hole; 702. Connecting cylinder; 703. Annular connecting part; 8. Buffer component; 9. Buffer rod; 901. Top cover; 902. Side wall; 10. Movable cavity; 11. Protective shell; 12. Mounting plate; 121. Mounting hole; 13. Chisel rod; 14. High-pressure gas chamber at room temperature. Detailed Implementation

[0073] The present invention will be further described below with reference to the accompanying drawings and specific embodiments, but this is not intended to limit the scope of the invention.

[0074] Example 1:

[0075] Please refer to Figures 1 to 14 As shown, an impact device is illustrated, comprising: a main fixed connecting seat 1 for connecting a vehicle, a hammer 2, a hydraulic cylinder 3, and a hammer guide connected to the main fixed connecting seat 1. The cylinder body 301 of the hydraulic cylinder 3 is connected to the main fixed connecting seat 1, and the piston 302 of the hydraulic cylinder 3 is slidably mounted inside the cylinder body 301. The hammer 2 is located outside the cylinder body 301. The hammer guide is used to axially guide and radially limit the hammer 2. The piston rod 303 is used to drive the hammer 2 to perform axial reciprocating impact motion along the hammer guide. The hammer 2 does not provide hydraulic sealing for the hydraulic cylinder 3. Hydraulic sealing is achieved by the cooperation between the piston 302 and the cylinder body 301 of the hydraulic cylinder 3.

[0076] The hydraulic cylinder 3 includes a cylinder body 301, a piston 302, and a piston rod 303. The piston 302 is slidably mounted inside the cylinder body 301 and is driven by hydraulic oil to reciprocate. The output end of the piston rod 303 drives the hammer 2, and the end of the piston rod 303 away from its output end is fixedly connected to the piston 302. The hammer 2 is separately disposed from the cylinder body 301 of the hydraulic cylinder 3, and the hammer 2 does not perform the hydraulic sealing function of the cylinder body 301. The hydraulic cylinder 3 acts as a power source, outputting driving force to drive the hammer 2 to impact the object being impacted. The overall structure of this invention is simple and compact, and the impact effect can be improved by using the hammer 2, while avoiding damage to the hydraulic cylinder 3.

[0077] Example 2, based on Example 1:

[0078] The hammer guide is the lower housing 4. The hammer 2 slides with the inner wall of the lower housing 4. The lower housing 4 provides sliding guidance and mounting support for the hammer 2. The lower housing 4 is fixedly connected to the main fixed connecting seat 1. The output end of the piston rod 303 is used to drive the hammer 2 to slide inside the lower housing 4.

[0079] Example 3, based on Example 2:

[0080] The lower housing 4 is a cylindrical structure with open ends. The main fixed connecting seat 1 covers one open end of the lower housing 4. The main fixed connecting seat 1 is connected to the open end of the lower housing 4 by screws or welding. The cylinder 301 is connected to the side wall of the main fixed connecting seat 1 away from the lower housing 4. If screws or welding are used, the output end of the piston rod 303 extends through the main fixed connecting seat 1 into the lower housing 4. The main fixed connecting seat 1 is provided with a central hole. The end of the piston rod 303 away from its output end is fixedly connected to the piston 302. The output end of the piston rod 303 extends through the central hole on the main fixed connecting seat 1 into the interior of the lower housing 4. The hammer 2 is columnar and is slidably installed in the lower housing 4. The open end 401 at the other end of the lower housing 4 is used for the hammer 2 to output impact force. The lower housing 4 and the main fixed connecting seat 1 combine to form a guide cavity, which is easy to assemble and can constrain the movement trajectory of the hammer 2.

[0081] Example 4, based on Example 1:

[0082] The hammer guide is a guide structure 5 provided in the main fixed connecting seat 1; it also includes a guided component 6 fixedly connected to the hammer 2, and the guided component 6 slides in cooperation with the guide structure 5 of the main fixed connecting seat 1.

[0083] Example 5, based on Example 4:

[0084] The main fixed connecting seat 1 is provided with four through holes arranged in a rectangular array. The four through holes surround the cylinder body 301. Each through hole has a guide structure 5 connected to its inner wall. Each guide structure 5 is provided with a slide rail. A guided component 6 is slidably fitted in each slide rail. The four sets of slidably fitted components can improve the stability of the guide.

[0085] Example 6 is based on any one of Examples 1 to 5:

[0086] The output end of the piston rod 303 is driven to the hammer 2. When the piston rod 303 extends, it drives the hammer 2 to move in the impact direction. When the piston rod 303 retracts, it drives the hammer 2 to move in the retraction direction.

[0087] Example 7 is based on Example 6:

[0088] The output end of the piston rod 303 is integrally manufactured or fixedly connected to the hammer 2, and the two complete the impact synchronously. When the output end of the piston rod 303 and the hammer 2 are integrally manufactured or fixedly connected (welded, screwed or threaded connection), the piston rod 303 directly drives the hammer 2 to extend or retract synchronously.

[0089] Example 8, based on Example 6:

[0090] The output end of the piston rod 303 is movably connected to the hammer 2. After the piston rod 303 drives the hammer 2 to accelerate, it disengages from the piston rod 303, and the hammer 2 completes the impact by relying on inertia.

[0091] Furthermore, when the output end of the piston rod 303 is movably connected to the hammer 2, a limiting cap 7 is also included, which is connected to the hammer 2. The limiting cap 7 is provided with a limiting structure 701, and the output end of the piston rod 303 is provided with a flange structure 304, which is located between the limiting structure 701 and the hammer 2. The flange structure 304 is threadedly connected to the piston rod 303 for easy assembly. A movable stroke is provided between the limiting structure 701 and the hammer 2 for the flange structure 304 to move axially along the piston rod 303. The flange structure 304 can drive the hammer 2 to move in the retraction direction of the piston rod 303 by engaging with the limiting structure 701. The piston rod 303 and / or the flange structure 304 can drive the hammer 2 to move in the direction of impact.

[0092] Example 9, based on Example 8:

[0093] The limiting cap 7 is connected to the hammer 2 and forms a movable cavity 10 with the outer wall of the hammer 2. A flange structure 304 is placed inside the movable cavity 10 and can slide relative to the hammer 2 axially within the movable cavity 10. The limiting cap 7 includes a limiting structure 701, a connecting cylinder 702, and an annular connecting part 703. The annular connecting part 703 is connected to the outer wall of the hammer 2 by screws for easy assembly. The limiting structure 701 is provided with a second central hole 7011, through which the piston rod 303 passes. The inner diameter of the second central hole 7011 is larger than the outer diameter of the piston rod 303. When the piston rod 303 retracts, the flange structure 304 abuts against the limiting structure 701, causing the hammer 2 to retract synchronously. When the piston rod 303 extends to impact, the flange structure 304 abuts against the hammer 2. After the abutment, the hammer 2 separates from the flange structure 304, and the hammer 2 impacts the object being impacted, so that the piston rod 303 avoids bearing axial impact load, thereby protecting the hydraulic cylinder 3.

[0094] The core of this embodiment is that the hammer 2 and the piston 302 are two completely independent components. The hammer 2 is located outside the hydraulic cylinder 3 and does not perform any hydraulic sealing function. The hydraulic sealing function is entirely provided by the piston 302 and its sealing ring located inside the cylinder body 301. The hammer 2 is an independent impact actuation component, and its outer wall does not require any hydraulic sealing structure; it only needs to meet the requirements of impact resistance and sliding guidance.

[0095] The output end of the piston rod 303 and the hammer 2 can also be connected in a non-rigid manner, such as a hinge.

[0096] Example 10 is based on any one of Examples 1 to 9:

[0097] Please refer to Figures 9 to 12 The piston 302 divides the cylinder 301 into a first chamber 3011 and a second chamber 3012. The first chamber 3011 contains hydraulic oil, and the second chamber 3012 contains high-pressure gas at room temperature and / or hydraulic oil. The high-pressure gas at room temperature is preferably nitrogen. Hydraulic oil is introduced into the first chamber 3011 to drive the piston rod 303 to extend and achieve impact. The second chamber 3012 is filled with high-pressure gas at room temperature or hydraulic oil to provide restoring force or store energy. Using high-pressure gas at room temperature results in a fast impact speed and high impact frequency; using hydraulic oil provides high control precision and stable operation, meeting the needs of different working conditions.

[0098] When the second chamber 3012 is filled with hydraulic oil: both the first chamber 3011 and the second chamber 3012 are filled with hydraulic oil and cooperate with the oil circuit control system for oil supply and return. High-pressure hydraulic oil enters the first chamber 3011, pushing the piston 302 to slide towards the second chamber 3012. At the same time, the hydraulic oil in the second chamber 3012 is depressurized and flows back in a controlled manner, thereby driving the piston rod 303 and the hammer 2 to return smoothly to their original positions. High-pressure hydraulic oil is introduced into the second chamber 3012, while the first chamber 3011 returns oil and depressurizes. The hydraulic oil pushes the piston 302 to slide in the opposite direction, and the piston rod 303 extends to drive the hammer 2 to impact the object being impacted. Through the precise oil circuit ratio and pressure control of the dual-chamber hydraulic oil, the extension and retraction of the hydraulic cylinder is smooth and controllable, with good buffering effect, strong running rigidity, high control accuracy, and more stable operation, making it suitable for working conditions with high requirements for impact force, stroke accuracy, and running stability.

[0099] When the second chamber 3012 is filled with high-pressure gas at room temperature: high-pressure hydraulic oil is introduced into the first chamber 3011. The hydraulic oil pushes the piston 302 to slide towards the second chamber 3012, thereby causing the piston rod 303 and the hammer 2 to quickly return to their original positions. During this process, the high-pressure gas at room temperature in the second chamber 3012 is compressed, forming a gas pressure energy storage and accumulating a restoring elastic force. When the first chamber 3011 is depressurized and the oil returns, the compressed high-pressure gas at room temperature in the second chamber 3012 expands rapidly, pushing the piston 302 out, causing the piston rod 303 to extend and drive the hammer 2 to complete the impact operation. Utilizing the compressibility and fast response of high-pressure gas at room temperature, the hammer 2 can achieve rapid impact and high reciprocating impact frequency, making it suitable for high-frequency continuous impact conditions. Furthermore, when high-pressure gas at room temperature is installed in the second chamber 3012, the piston 302 has a hollow cup-shaped structure. The opening of this cup-shaped structure faces the high-pressure gas chamber at room temperature and is connected to it. The high-pressure gas chamber at room temperature is the second chamber 3012. The hollow cup-shaped structure is used to expand the total volume of the high-pressure gas chamber at room temperature, thereby reducing the compression ratio when the high-pressure gas at room temperature is compressed and reducing the weight of the piston 302.

[0100] Hydraulic cylinder 3 is a conventional cross-section fixed piston. During the sliding process, the cross-sectional area of ​​the conventional cross-section fixed piston driven by hydraulic oil remains constant. The conventional cross-section fixed piston has a simple structure and low cost, and is suitable for working conditions where the load does not change much.

[0101] Example 11, based on any one of Examples 1 to 9:

[0102] Please refer to Figure 13 Hydraulic cylinder 3 is a negative pressure oil-replenishing variable cross-section hydraulic cylinder; during the sliding process, the cross-sectional area driven by hydraulic oil in the negative pressure oil-replenishing variable cross-section hydraulic cylinder changes in an orderly manner according to a preset law. When the external load is small, the bearing area is actively reduced to increase the movement speed, and when the external load is large, the bearing area is actively increased to increase the driving force. The control of this negative pressure oil-replenishing variable cross-section hydraulic cylinder is based on the negative pressure oil-replenishing effect, and the bearing area is actively adjusted according to the load change.

[0103] The adaptive variable cross-section hydraulic cylinder involved in this invention refers to a type of hydraulic actuator whose effective driving area can be dynamically adjusted according to changes in stroke or load. Unlike the traditional hydraulic cylinder with a fixed driving area throughout its stroke, this variable cross-section hydraulic cylinder can achieve efficient matching of thrust output and load changes throughout the entire working cycle by changing the effective working area according to actual load requirements at different stages of the working cycle. This variable cross-section hydraulic cylinder can have various specific implementation forms, such as a stepped structure with multiple chambers arranged sequentially along the axial direction, a multi-chamber structure with multiple chambers arranged in a nested manner, and other structural forms that can achieve variable driving area. Although the specific constructions of the above forms differ, they are all based on a common and fundamental working principle—the negative pressure oil replenishment principle. The core of this principle is that the driving chambers not currently connected to a high-pressure oil source are not in an empty or closed state, but are mechanically dragged by the main driving chamber through a common piston rod. As the internal volume of these chambers increases due to passive stretching, the internal pressure decreases, forming a negative pressure. At this time, hydraulic oil is automatically drawn from the normal pressure oil tank through the configured oil replenishment passage, completely filling the chambers. When these chambers need to be connected to the high-pressure oil circuit in subsequent stages, since they are pre-filled with oil, there is almost no volume to fill when the high-pressure oil enters. This eliminates the pressure shock, suction vibration, and flow saturation phenomena commonly found in traditional staged drive schemes, achieving smooth and quiet switching of the drive area. The negative pressure oil replenishment principle is the cornerstone of the variable cross-section hydraulic cylinder of this invention, enabling it to achieve impact-free and stable cross-section changes.

[0104] Example 12, based on Example 11:

[0105] Please refer to Figure 13It also includes a high-pressure gas chamber 14 at room temperature, located away from the piston end of the hammer 2. The high-pressure gas chamber 14 is preferably filled with nitrogen. The piston 302 of the hydraulic cylinder 3 extends into the high-pressure gas chamber 14, forming a combined impact device of hydraulic cylinder and high-pressure gas at room temperature. As the stroke of the piston 302 compressing the high-pressure gas chamber 14 gradually increases, the high-pressure gas pressure in the high-pressure gas chamber 14 increases regularly with the increase in stroke. The negative pressure oil-replenishing variable cross-section hydraulic cylinder can, through pre-designed piston cross-section variation patterns, match the hydraulic oil bearing area of ​​the hydraulic cylinder piston with the changing pressure of the high-pressure gas chamber 14 at room temperature during the same stroke, maximizing hydraulic oil utilization. This achieves a pure hydraulic stroke adaptive reciprocating impact system configuration based on the negative pressure oil replenishment effect. This system actively matches the high-pressure gas pressure variation curve at room temperature, dynamically adjusting the piston bearing area throughout the full compression stroke, matching the hydraulic cylinder output thrust with the real-time resistance of the high-pressure gas chamber 14 at room temperature, achieving the optimal reciprocating impact system configuration that maximizes hydraulic oil utilization.

[0106] As a preferred embodiment of the aforementioned variable cross-section hydraulic cylinder, this invention employs a stepped variable cross-section hydraulic cylinder. This stepped design is also based on the principle of negative pressure oil replenishment, and its core feature is that the effective driving area is set to increase in a stepped manner with the advancement of the impact stroke, actively matching the continuous rise in the back pressure of the nitrogen chamber during the impact process. At the beginning of the impact stroke, the nitrogen compression is small and the back pressure is low; at this time, only a small working area is connected for driving, allowing for precise utilization of the hydraulic oil pressure without overflow or wasted flow, and resulting in a smooth start-up without hydraulic shock. At this time, the chamber not connected to high-pressure oil is in a passive motion state, being mechanically dragged along. Through negative pressure oil replenishment, it automatically draws oil from the tank, preparing for the upcoming connection. As the hammer moves forward, the nitrogen is further compressed, and the back pressure gradually increases. When the preset stroke position or pressure threshold is reached, subsequent driving areas at each stage are automatically integrated, resulting in a step-like increase in the total driving area to accommodate the increased load. Since the chamber to be connected is completely filled with hydraulic oil, there is almost no volume filling requirement when high-pressure oil is introduced, resulting in a smooth and shock-free connection process. Similarly, at the final impact stage with the highest nitrogen back pressure, the driving area of ​​all working chambers is fully engaged, reaching its maximum total driving area. This results in a powerful thrust for final acceleration, achieving maximum impact kinetic energy. Through this adaptive matching mechanism of "load increasing gradually, area increasing in a stepwise manner," the effective utilization rate of hydraulic oil is fundamentally improved. Compared to traditional fixed-section drive schemes, under the same pump source flow rate, the amount of hydraulic oil consumed to complete the initial stroke in the light-load stage is significantly reduced because only small-area chambers are used for drive, thus significantly shortening the single impact cycle time and achieving higher impact frequency and impact efficiency. At the same time, because the stepwise increase in driving area actively absorbs most of the load increment, the system's maximum working pressure is effectively controlled, overflow and throttling losses are reduced to extremely low levels, system heat generation is significantly reduced, oil aging is slowed down, and the lifespan of seals and hydraulic components is extended, comprehensively enhancing the reliability and durability of the entire machine. This stepwise variable cross-section scheme has a simple structure, clear control logic, and reliable operation, making it the preferred embodiment of this invention.

[0107] Furthermore, the piston 302 has a hollow cup-shaped structure with its opening facing and communicating with the high-pressure gas chamber 14 at room temperature. The hollow cup-shaped structure is used to expand the total volume of the high-pressure gas chamber at room temperature, thereby reducing the compression ratio when the high-pressure gas at room temperature is compressed and reducing the weight of the piston 302.

[0108] Furthermore, the negative pressure oil-replenishing variable cross-section hydraulic cylinder is particularly suitable for cooperating with the nonlinear growth law of the pressure in the high-pressure gas chamber 14 at room temperature with the compression stroke, to construct an optimal reciprocating impact system with pure hydraulic stroke self-adaptation.

[0109] Taking a high-pressure gas chamber 14 with a total length of 400mm at room temperature as an example, the pressure change pattern is explained in detail:

[0110] Assuming the initial pressure in the high-pressure gas chamber 14 is 1 MPa at room temperature, and piston 302 compresses the gas from 0 mm to 400 mm, the pressure change of the high-pressure gas at room temperature for each 1 cm (10 mm) compression is as follows:

[0111] Pressure increment and pressure growth characteristics per 1cm compression stroke

[0112] From 0 to 100 mm, the pressure increases by approximately 0.03~0.05 MPa, exhibiting slow, almost linear growth.

[0113] From 100 to 200 mm, the pressure increases by approximately 0.08 to 0.12 MPa, and the rate of increase begins to accelerate.

[0114] From 200 to 300 mm, the pressure increased significantly by approximately 0.20 to 0.35 MPa.

[0115] From 300 to 400 mm, the pressure increases rapidly by approximately 0.50 to 1.20 MPa, becoming increasingly steeper as the distance increases.

[0116] Specific examples:

[0117] When compressed from 1 cm to 2 cm, the pressure increases from 1.00 MPa to 1.03 MPa (an increase of 0.03 MPa).

[0118] When compressed from 10cm to 11cm, the pressure increases from 1.30MPa to 1.42MPa (an increase of 0.12MPa).

[0119] When compressed from 20cm to 21cm, the pressure increases from 2.10MPa to 2.45MPa (an increase of 0.35MPa).

[0120] When compressed from 30cm to 31cm, the pressure increases from 4.00MPa to 5.00MPa (an increase of 1.00MPa).

[0121] When compressed from 39cm to 40cm (the endpoint), the pressure increases from 8.00MPa to 9.20MPa (an increase of 1.20MPa).

[0122] It is evident that the pressure increment in the last 1 cm of the later stage of compression (1.20 MPa) is 40 times that of the pressure increment in the first 1 cm of the initial stage of compression (0.03 MPa). This nonlinear characteristic of "becoming more difficult to compress as the compression progresses" is severely mismatched with the constant force output characteristics of a conventional fixed-section hydraulic cylinder.

[0123] How to match the above rules with a variable cross-section hydraulic cylinder:

[0124] The negative pressure replenishing variable cross-section hydraulic cylinder, employing a stepped piston structure, automatically adjusts based on the negative pressure replenishing effect through a pure hydraulic control circuit (including switching valves, check valves, and hydraulic pilot control valves).

[0125] Initial compression phase (0→100mm): With low external load, the system automatically reduces the piston bearing area, enabling the piston to advance rapidly under the same flow rate and improving efficiency.

[0126] Mid-compression phase (100→300mm): The pressure increase gradually accelerates, the system gradually increases the pressure-bearing area, and the output thrust increases synchronously;

[0127] In the later stage of compression (300→400mm): the pressure increases sharply, and the system actively increases to the maximum pressure-bearing area to generate sufficient thrust to overcome the high-pressure gas resistance at room temperature and ensure the completion of the impact stroke.

[0128] Summary of technical effects:

[0129] Through the above configuration, the output thrust curve of the variable cross-section hydraulic cylinder achieves dynamic matching with the pressure growth curve of the high-pressure gas chamber 14 at room temperature throughout the entire stroke. This avoids the contradiction of excessive thrust (wasting energy) in the early stage of compression and insufficient thrust (unable to complete compression) in the later stage of compression, which is common with fixed cross-section hydraulic cylinders. This achieves the optimal reciprocating impact system configuration with pure hydraulic stroke self-adaptation and maximized hydraulic oil utilization. This system is particularly suitable for downhole or explosion-proof operating environments requiring high reliability and electronic control-free operation. The negative pressure replenished variable cross-section hydraulic cylinder can actively change the hydraulic oil bearing area of ​​the piston according to the external load, making it suitable for impact conditions with drastic load changes.

[0130] Example 13, based on any one of Examples 1 to 12:

[0131] It also includes a buffer component 8, which is connected to a fixed connector on the main fixed connecting seat 1; when the hammer 2 moves to the set position, please refer to... Figure 12 The impact hammer 2 or a component fixedly connected to the impact hammer 2 abuts against the buffer component 8 to achieve buffering; the fixed connection is the lower housing 4 and / or the cylinder 301. The set position of the impact hammer 2 is the position where the impact hammer 2 or the component fixedly connected to the impact hammer 2 begins to contact the buffer component 8.

[0132] When the fixed connector is the lower housing 4, the inner wall of the lower housing 4 is provided with a stepped surface 402. The buffer component 8 is connected to the stepped surface 402 and the buffer component 8 is located between the hammer 2 and the stepped surface 402. When the hammer 2 moves to the set position, the hammer 2 impacts the buffer component 8, and the buffer component 8 absorbs the impact energy to achieve the buffering effect.

[0133] When the fixed connecting component is cylinder 301, it also includes a buffer rod 9. The component that the hammer 2 is fixedly connected to is the buffer rod 9. One end of the buffer rod 9 is connected to the hammer 2, and the other end of the buffer rod 9 can be used to abut against the buffer component 8 to achieve buffering. When the hammer 2 moves to the set position, the buffer rod 9 abuts against the buffer component 8 to start buffering. Before passing the limit stroke of the set buffer component 8, the speed of the hammer 2 is zero. The buffer rod 9 includes a top cover 901 and a side wall 902. The side wall 902 surrounds the outer periphery of cylinder 301. One end of the side wall 902 passes through the main fixed connecting seat 1 and is placed in the lower housing 4 and connected to the hammer 2. The other end of the side wall 902 is connected to the top cover 901. The buffer component 8 is disposed between the top cover 901 and cylinder 301. When the hammer 2 moves to the set position, the top cover 901 abuts against the buffer component 8 to start buffering. Before passing the limit stroke of the set buffer component 8, the speed of the hammer 2 is zero, while the piston rod 303 always remains disengaged from the hammer 2. The buffer component 8 includes, but is not limited to, polyurethane elastomers, metal springs, or hydraulic dampers.

[0134] As the hammer 2 passes the set position, it contacts the buffer component 8 via the buffer rod 9. The buffer component 8 absorbs the impact energy independently of the hydraulic system, and throughout the process, the hydraulic system in the hydraulic cylinder 3 does not generate pressure peaks.

[0135] Example 14, based on Example 13:

[0136] It also includes a protective shell 11, which is a cylindrical structure with open ends. One end of the protective shell 11 is open and connected to the main fixed connection seat 1 by screws; the buffer rod 9 passes through the other end of the protective shell 11.

[0137] Example 15, based on Example 14:

[0138] It also includes two mounting plates 12, which are respectively connected to both sides of the main fixed connecting seat 1, both sides of the lower housing 4, and both sides of the protective shell 11, or simultaneously connected to both sides of the main fixed connecting seat 1, both sides of the lower housing 4, and both sides of the protective shell 11; the two mounting plates 12 are symmetrically arranged; the mounting plates 12 are provided with mounting holes 121, through which they are mounted on a carrier, including but not limited to hydraulic excavators, bulldozers, hydraulic platforms, and drilling platforms. The carrier is a mechanical device that drives construction machinery to perform work.

[0139] Example 16, based on any one of Examples 2 to 15:

[0140] The lower housing 4 includes a main body section 403 and a contraction section 404, which are connected as one unit. The inner diameter of the main body section 403 is larger than the inner diameter of the contraction section 404. The buffer component 8 and the hammer 2 are both placed inside the main body section 403.

[0141] The impact device also includes a chisel 13, which is slidably mounted on the contraction section 404; one end of the chisel 13 is used to abut against the hammer 2, and the other end of the chisel 13 extends to the outside of the contraction section 404 for direct impact on the object being impacted.

[0142] Work process:

[0143] The hydraulic system supplies high-pressure hydraulic oil to the first chamber 3011. The hydraulic oil pushes the piston 302 to slide towards the second chamber 3012, thereby causing the piston rod 303 and the hammer 2 to retract. During this process, the high-pressure gas at room temperature in the second chamber 3012 is compressed, forming a gas pressure energy storage and accumulating a restoring elastic force. When the first chamber 3011 is depressurized and the oil returns, it drives the piston 302 to move in the impact direction. The piston rod 303 drives the hammer 2 to move in the impact direction. The hammer 2 strikes the chisel 13, and the chisel 13 transfers the kinetic energy to the impacted object through the opening 401. The rebound force generated by the impact is transmitted to the piston 302 through the lower housing 4, the hammer 2, and the piston rod 303. However, since the hammer 2 itself does not perform a sealing function, even if the outer wall of the hammer 2 is scratched due to the rebound force, it will not affect any sealing performance.

[0144] The work process is carried out in the order of "push-remove-hit-pull":

[0145] Push: The hydraulic system drives the piston 302 to move in the impact direction, the piston rod 303 extends, and the end face of the flange structure 304 facing the impact direction abuts against the relative inner wall of the movable cavity 10. Please refer to... Figure 10 This propels the hammer 2 to accelerate in the direction of impact.

[0146] Disengagement: Before the hammer 2 strikes the chisel rod 13, the hydraulic system controls the piston rod 303 to stop or decelerate. The hammer 2 continues to move in the impact direction due to inertia, simultaneously causing the limit cap 7 to slide relative to the flange structure 304 in the impact direction, thus disengaging the flange structure 304 from the hammer 2. The hammer 2 and piston rod 303 are thus decoupled. Please refer to [reference needed]. Figure 11 .

[0147] Strike: Next, hammer 2 strikes the chisel 13 at high speed due to its own inertia. Because it has been pre-decoupled, the impact rebound force cannot be transmitted to the piston rod 303 and the hydraulic sealing system. It should be noted that because the chisel 13 has axial movement space within the lower housing 4, hammer 2 moves in the impact direction under inertia and reaches the set position. Hammer 2 will continue to move in the impact direction under inertia. At this time, the buffer rod 9 contacts the buffer component 8. Please refer to... Figure 12 This compresses the buffer component 8. When the buffer component 8 is compressed to its limit position, it restricts the hammer 2 from continuing to move in the impact direction before the flange structure 304 contacts the limiting structure 701. This serves to decelerate and limit the hammer 2, and at the same time prevents the hammer 2 from pulling the piston rod 303.

[0148] Pull: After the impact, the hydraulic system drives the piston 302 to retract, the piston rod 303 retracts, and the upper end face of the flange structure 304 hooks onto the limiting structure 701, pulling the hammer 2 back to its initial position. Please refer to... Figure 9 .

[0149] An engineering machine, comprising an impact device.

[0150] Furthermore, the engineering machinery includes hydraulic breakers, down-the-hole drills, top hammer drills, hydraulic pile hammers, vibratory pile hammers, dynamic compaction machines, stamping presses, forging presses, die forging hammers, tunnel boring machines, deep-sea pile hammers, underwater breakers, or seabed compactors.

[0151] A method for controlling an impact device, comprising the following steps:

[0152] S1: The hydraulic system drives the piston 302 inside the hydraulic cylinder 3 to move, and drives the hammer 2 located outside the hydraulic cylinder 3 through the piston rod 303, so that the hammer 2 moves towards the object being impacted.

[0153] S2: Hammer 2 strikes the object being impacted, applying impact;

[0154] S3: After the impact is completed, the hydraulic system drives the piston 302 to retract, driving the hammer 2 to retract, so as to carry out the next impact.

[0155] Furthermore, the impact device is the impact device of Embodiments 8 and 9, and the control method further includes:

[0156] In step S1, the flange structure 304 at the output end of the piston rod 303 abuts against the limiting structure 701, pushing the hammer 2 to move faster toward the object being impacted.

[0157] After step S1 and before step S2, there is also a disengagement step: the piston rod 303 stops or decelerates, causing the flange structure 304 to disengage from the limiting structure 701, and the hammer 2 and the piston rod 303 achieve motion decoupling; the hammer 2 completes the impact in step S2 by relying on its own inertia.

[0158] In step S3, the piston rod 303 retracts, the flange structure 304 abuts against the limiting structure 701, and the hammer 2 is driven to retract.

[0159] Furthermore, the impact device is the impact device of Embodiment Seven, and the control method further includes:

[0160] In step S1, the output end of piston rod 303 accelerates and moves synchronously with hammer 2 toward the object being impacted.

[0161] In step S2, the piston rod 303 moves synchronously with the hammer 2 to strike the object being impacted, thus applying the impact.

[0162] In step S3: After the impact is completed, the hydraulic system drives the piston 302 to retract, driving the hammer 2 to retract for the next impact.

[0163] Furthermore, the impact device is the impact device of Embodiment Thirteen, and the control method further includes:

[0164] After step S2 and before step S3, the hammer 2 or the buffer rod 9 only comes into contact with the buffer component 8 when the hammer 2 moves toward the object being impacted and passes its set position. The buffer component 8 absorbs the impact energy independently of the hydraulic system. Otherwise, the hammer 2 or the buffer rod 9 does not come into contact with the buffer component 8.

[0165] An impact operation method for engineering machinery, wherein the impact operation is carried out using a control method.

[0166] In summary, this invention separates the traditionally integrated "sealing drive piston" and "external impact hammer" into two independent structural components. The piston 302 inside the hydraulic cylinder 3 is dedicated to hydraulic sealing and reciprocating drive functions. It operates in a closed, clean hydraulic oil environment and does not participate in the external impact process, thus completely avoiding damage to the sealing system from impact reaction forces. The impact hammer 2, which performs the high-speed impact task, is independently housed within the lower housing 4 outside the hydraulic cylinder 3. It does not need to perform hydraulic sealing functions; it only needs to withstand and transmit impact kinetic energy. This "separation of sealing and impact functions" architecture resolves the contradiction between hydraulic sealing and impact, so that the magnitude of impact energy is no longer limited by the seal life, significantly improving the reliability and energy ceiling of the device.

[0167] In the description of the invention, the terms "upper," "lower," "left," "right," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. The terms "connection," "installation," "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0168] The above are merely preferred embodiments of the present invention and are not intended to limit the implementation methods and protection scope of the present invention. Those skilled in the art should recognize that any equivalent substitutions and obvious changes made based on the description and illustrations of the present invention should be included within the protection scope of the present invention.

[0169] Typical application examples:

[0170] Example 1: Large hydraulic breaker (5-10 ton impact hammer)

[0171] This embodiment is a large hydraulic breaker, suitable for ultra-high energy demand scenarios such as crushing ultra-hard rocks and secondary crushing of ultra-large ore blocks.

[0172] Comparison with traditional solutions:

[0173] Traditional large hydraulic breakers utilize the piston rod of a hydraulic cylinder as the impact hammer. The piston rod has a maximum mass of approximately 500-600 kg and a maximum diameter of approximately 280 mm, with a single impact energy of approximately 20,000-30,000 J. Limited by the integrated sealing and impact structure, further increasing the hammer mass would lead to severe cylinder scoring failure, rendering the equipment unreliable. Therefore, there are virtually no traditional hydraulic breakers in the world with an impact hammer diameter exceeding 280 mm and a mass exceeding 600 kg.

[0174] This embodiment's solution:

[0175] This embodiment adopts an external design for the impact hammer 2, which has a mass of 5 tons (5000 kg) or 10 tons (10000 kg) and a diameter of over 500 mm. The impact hammer 2 does not participate in the hydraulic seal and only performs impact operations.

[0176] The hammer 2 and piston rod 303 are detachably connected, realizing "push-detach-strike-pull". At the moment of impact, the multi-ton hammer 2 and piston rod 303 automatically detach, and the huge rebound force generated is entirely borne by the hammer itself, without being transmitted back to the hydraulic cylinder, thus completely eliminating failures such as cylinder scoring, piston rod 303 bending, and cylinder body 301 cracking.

[0177] Technical effects:

[0178] Hammer 2 weight: 5000kg or 10000kg (traditionally about 500-600kg)

[0179] Single impact energy: 250,000-500,000J (traditional is about 20,000-30,000J)

[0180] Rock hardness that can be broken: It can efficiently break ultra-hard rocks such as granite and basalt.

[0181] Crustable ore diameter: Can directly crush extra-large ore blocks with a diameter of 3-5 meters or more.

[0182] Applications: Large-scale mines, tunnel excavation, crushing of large ore at screens.

[0183] Example 2: High-pressure gas-driven large impact rammer

[0184] This embodiment provides a large impact rammer driven by high-pressure gas, which can be used as an alternative to traditional dynamic compaction machines and applied to heavy-duty operation scenarios such as foundation compaction and demolition.

[0185] This embodiment of the impact ram includes a high-pressure air chamber, a hammer 2, a hydraulic cylinder 3, and a lower housing 4. The high-pressure air chamber is filled with high-pressure gas, preferably a high-pressure gas that is gaseous at room temperature, and more preferably a high-pressure gas that is at room temperature. The hammer 2 is assembled inside the lower housing 4 and can reciprocate along the axis of the lower housing 4. A distribution system is used to control the filling and releasing of the high-pressure gas, realizing the cyclic process of lifting and storing energy and accelerating the impact of the hammer 2.

[0186] Its working cycle is as follows:

[0187] Energy storage and lifting stage: The distribution system controls the high-pressure gas to enter the lifting chamber of the lower shell 4, and the high-pressure gas pushes the hammer 2 upward. During this process, the internal energy of the high-pressure gas is converted into the gravitational potential energy of the hammer 2, and the hammer 2 is lifted to the set height. Unlike traditional dynamic compaction machines that require a lifting height of twenty to thirty meters, this embodiment only requires a few meters of stroke to complete energy storage, significantly reducing the overall height of the equipment.

[0188] Impact Release Phase: Once hammer 2 reaches the set position, the flow distribution system switches, and high-pressure gas enters the impact chamber of the cylinder, while the lifting chamber is depressurized. The high-pressure gas drives hammer 2 to accelerate downwards, combining its gravitational potential energy with the expansion work of the high-pressure gas. Hammer 2 impacts the working surface at extremely high speed, releasing impact energy. The energy of a single impact can reach hundreds of thousands of joules, breaking the energy limit of traditional hydraulic breakers.

[0189] Reset preparation phase: After the strike is completed, the distribution system switches again and enters the next energy storage and boosting cycle.

[0190] Compared with traditional dynamic compaction machines, this embodiment has the following advantages:

[0191] 1. Breakthrough in Energy Limits: Traditional hydraulic breakers are limited by the pressure and flow rate of the hydraulic system, resulting in limited single-impact energy that cannot meet the needs of large-scale compaction operations. While traditional dynamic compaction machines can achieve higher energy levels, they rely on large cranes and extremely high lifting heights. This embodiment uses high-pressure gas energy storage drive, releasing energy through the instantaneous expansion of gas to accelerate the hammer 2 to a high speed. The single-impact energy can reach hundreds of thousands of joules, effectively bridging the energy gap between traditional hydraulic breakers and large-scale dynamic compaction machines.

[0192] 2. Compact size and flexible mobility: Compared with the massive size of traditional dynamic compaction machines, which are often tens of meters high and weigh hundreds of tons, the impact compactor in this embodiment eliminates the crane and ultra-high gantry, significantly reducing the overall height and making it compact. It can be mounted on the chassis of general engineering machinery such as excavators and loaders, enabling rapid relocation and flexible deployment, and is especially suitable for working conditions with limited space.

[0193] 3. High operating frequency and significantly improved construction efficiency: Traditional dynamic compaction machines require a complete cycle of "lifting-releasing-falling-lifting" to complete each compaction operation. Limited by the crane's lifting speed, only a few operations can be completed per minute. This embodiment achieves reciprocating motion through rapid reversal of high-pressure gas, eliminating the need for a free fall process, greatly increasing the operating frequency and multiplying construction efficiency.

[0194] 4. High safety: Traditional dynamic compaction machines have a high center of gravity due to their large lifting height, posing multiple safety hazards during lifting, rotation, and release, such as overturning, wire rope breakage, and hammer swaying. In this embodiment, the hammer 2 moves within the lower housing 4, with a short stroke and a low center of gravity, completely eliminating the need for wire ropes and lifting equipment, significantly improving operational safety.

[0195] 5. Energy-saving and efficient: Traditional dynamic compaction machines rely on cranes to repeatedly lift the hammer, consuming a large amount of fuel or electricity each time. The high-pressure gas energy storage drive method in this embodiment can recover some energy during braking by utilizing the compressibility of gas. At the same time, the distribution system optimizes the timing of gas charging and releasing, resulting in a higher energy utilization rate than traditional mechanical lifting methods.

[0196] 6. Wide range of applicable working conditions: In addition to replacing traditional dynamic compaction machines for foundation compaction, this embodiment can also adapt to various working conditions such as demolition, pile foundation construction, and soil compaction by replacing different types of impact hammers 2, and has the advantage of being a multi-functional machine.

[0197] Explanation of overall system performance contribution rate:

[0198] This invention makes a significant contribution to improving the overall performance of the machine through the synergistic effect of four core innovations. Among them, the first major innovation (external impact hammer, not involved in sealing) is a fundamental breakthrough; the fourth major innovation (independent buffer scheme) provides a key safety guarantee for achieving high impact energy.

[0199] I. Breakthrough in the Upper Limit of Impact Energy – The Core Contribution of this Invention

[0200] The fundamental flaw of traditional solutions:

[0201] In traditional impact devices, the hammer and piston are an integral structure. The same piston rod must perform both the hydraulic sealing function and directly bear the impact load. When attempting to increase the impact energy, the increased impact mass leads to a sharp increase in lateral forces on the piston's hydraulic sealing surface, exceeding the limits of existing piston and piston cylinder metal materials, resulting in rapidly worsening damage to the hydraulic sealing surface. The high impact force and large mass piston reduce the device's stability and significantly shorten its service life, failing to meet the requirements of long-term continuous operation.

[0202] This technological bottleneck limits the theoretical upper limit of impact mass in traditional impact devices. For example, hydraulic breakers have significant engineering limits on hammer mass and diameter because the sealing surface cannot withstand the impact of a larger hammer. Similarly, rammers have significant engineering limits on hammer mass because the sealing structure cannot withstand the impact and rebound of a larger hammer. Exceeding these limits leads to a sharp increase in failure rates such as cylinder scoring, oil leakage, and seal failure, rendering the equipment unreliable. Therefore, in traditional solutions, the impact mass is "locked" by sealing precision, making it impossible to achieve higher energy impacts through simple scaling up.

[0203] Breakthrough solution of the present invention:

[0204] This invention places the hammer entirely outside the hydraulic cylinder, and the hammer does not perform any hydraulic sealing function. The sealing system of the hydraulic cylinder is only responsible for driving the reciprocating motion of the piston rod and does not bear any impact load.

[0205] This fundamental change brings breakthroughs in several ways: Traditional hydraulic breaker hammers have a significant engineering limit on their impact hammer mass, while this invention can achieve a mass significantly greater than that of traditional solutions, resulting in a substantial improvement. Traditional hydraulic breaker hammer diameters also have a significant engineering limit, but this invention is unrestricted and can be infinitely increased, with no theoretical upper limit. Traditional deep-sea pile driver impact pistons also have a significant engineering limit, but this invention can achieve a mass significantly greater than that of traditional solutions, resulting in a substantial improvement. Similarly, traditional rammer hammers also have a significant engineering limit, but this invention can achieve a mass significantly greater than that of traditional solutions, resulting in a substantial improvement. Furthermore, traditional solutions suffer from high rates of cylinder scoring and seal failure, which worsen with increasing energy levels; this invention has an extremely low failure rate (due to complete isolation between the impact hammer and the seal), significantly reducing these issues.

[0206] This innovation contributes the most to the improvement of overall machine performance and is the core contribution of this invention.

[0207] II. Elimination of rebound damage – Feasibility of ensuring ultra-massive impacts

[0208] In traditional methods, the greater the impact mass, the greater the rebound force. The rebound force of a large-mass ram is extremely high; if it doesn't detach from the structure, the rebound force will directly destroy the hydraulic system. Therefore, detachment from the structure is a necessary guarantee for achieving ultra-large mass impacts.

[0209] This invention employs a "push-detach-strike-pull" structure, where the hammer automatically detaches from the piston rod upon impact, and the rebound force is entirely borne by the hammer itself, without being transmitted back to the hydraulic cylinder. The greater the impact mass, the more crucial the protective function of the detachment structure becomes.

[0210] This innovation makes a significant contribution to improving the overall performance of the machine.

[0211] III. Auxiliary Optimization of Hollow Cup Piston Structure

[0212] This invention employs a hollow cup-shaped piston structure, with the cup opening facing and communicating with the nitrogen chamber. This expands the overall volume of the nitrogen chamber, thereby reducing the compression ratio of nitrogen and lightening the piston weight. This structure makes the hydraulic system pressure changes smoother, improving operational comfort and system response characteristics.

[0213] This innovation contributes to the overall performance improvement of the machine.

[0214] IV. Independent Buffering Solution – A Key Safety Guarantee for Extremely High Impact Energy (Protecting the Main System and, More Importantly, the Impact Device Itself)

[0215] The shortcomings of traditional solutions:

[0216] Existing impact devices typically employ hydraulic damping for cushioning under no-load conditions, using a flow-limiting orifice to generate hydraulic damping force to buffer piston impact. This method has serious drawbacks: the flow-limiting orifice causes a momentary surge in hydraulic oil pressure, creating localized pressure peaks. These peaks are transmitted through the hydraulic lines to the main directional valve, hydraulic pump, and vehicle hydraulic system, causing impact damage to hydraulic components. Furthermore, hydraulic damping has low energy conversion efficiency; most of the impact energy is converted into heat energy in the hydraulic oil, leading to increased oil temperature and accelerated seal aging.

[0217] More importantly, in traditional solutions, the impact energy is ultimately borne by the structural components of the impact device itself (cylinder, piston, sealing system). Once dry firing occurs, the enormous impact energy acts directly on the inside of the device, causing cylinder scoring, seal damage, structural deformation, or even breakage—essentially "damaging itself."

[0218] In scenarios involving extremely high impact energy, the aforementioned problems are amplified dramatically: the greater the impact energy, the stronger the destructive force on the device itself during a dry-firing operation. Without a reliable independent buffering solution, operators will be hesitant to use high-energy impacts, as a single misoperation (dry firing) could render the entire device unusable. This is one of the underlying reasons why traditional solutions cannot handle extremely high impact energy.

[0219] Breakthrough solution of the present invention:

[0220] This invention features an independent buffer component connected to a fixed connector on the main fixed connecting seat. When the hammer moves to a set position (i.e., during dry firing or overtravel conditions), the hammer or a component fixedly connected to it (such as a buffer rod) contacts the buffer component to achieve buffering. This buffer component is independent of the hydraulic system, directly absorbing impact energy through mechanical components such as polyurethane elastomers and metal springs. It does not require the participation of the main hydraulic system, nor does it require the impact device's own structural components to withstand dry firing impacts.

[0221] In dry-firing mode, after the hammer passes the set position, it contacts the buffer component through the buffer rod, and the buffer component independently absorbs all the remaining impact energy. Throughout the entire process: the hydraulic system in the hydraulic cylinder does not generate any pressure peaks—protecting the main hydraulic system; the cylinder body, piston, piston rod, and sealing structure of the impact device do not bear any dry-firing impact force—protecting the impact device itself.

[0222] Technical effects and core value:

[0223] The independent buffer design provides dual safety for the high-impact energy device: First, it protects the main hydraulic system—preventing damage to components such as the main directional valve and hydraulic pump from hydraulic shock peaks; second, and more importantly, it protects the impact device itself—during dry firing, the impact energy is absorbed by an independent buffer component, rather than being borne by the core structural components of the impact device such as the cylinder, seals, and piston rod. This means that even if dry firing occurs, the impact device itself will not be damaged.

[0224] It is precisely because of this independent buffer scheme as the "last line of defense" that operators can use devices with extremely high impact energy with confidence, without worrying about misoperation or dry firing causing equipment self-destruction. This scheme fundamentally eliminates the contradiction between "high impact energy" and "dry firing self-destruction," making the engineering application of extremely high impact energy truly possible.

[0225] This innovation makes a crucial contribution to the overall performance improvement and is one of the key supports for achieving high impact energy.

[0226] Summary of overall contributions:

[0227] The core contribution is the breakthrough in impact energy limits (external hammer placement), which removes the seal-based limitations on hammer mass, allowing for unlimited increases. Rebound damage elimination (detachment from the structure) is essential for ensuring ultra-massive impacts. The hollow cup piston structure is an auxiliary optimization, reducing the compression ratio, lightening the piston weight, and stabilizing pressure changes. The independent buffer scheme provides safety assurance, independently absorbing energy under extreme conditions such as dry-firing, protecting the main system and the impact device itself, making large impacts possible. This invention makes a core contribution to improving overall machine performance, with four major innovations jointly supporting the ultra-massive impact solution.

[0228] in conclusion:

[0229] The most fundamental and core technical contribution of this invention is that it completely breaks through the theoretical and engineering limits of the impact energy of traditional impact devices.

[0230] Traditional solutions are limited by the "integrated sealing and impact" structure, resulting in significant engineering limitations on the impact hammer's mass. This invention, through a fundamental innovation of externally positioned impact hammer and complete separation of sealing and impact, enables the impact mass to break through the original limits, reaching a level far exceeding that of traditional solutions.

[0231] Building upon this foundation, the present invention further transforms ultra-high energy impacts from a theoretical possibility into an engineering reality through four innovative synergistic effects: eliminating rebound damage through structural separation, optimizing system response through a hollow cup piston, and providing air-firing safety protection through an independent buffer scheme.

[0232] This breakthrough will redefine the performance boundaries of impact equipment such as hydraulic breakers and large rammers, and will have revolutionary significance in fields such as ultra-hard rock crushing, ultra-large ore processing, and ultra-high energy dynamic compaction foundation treatment.

[0233] Furthermore, this invention, "An Impact Device and Its Control Method, and Engineering Machinery and Its Operation Method," along with two other invention applications filed on the same day by the applicant—namely, "An Inertial Rebound Suppression High Conductivity Impact Device and Force Transmission Method and Engineering Machinery" and "An Adjustable Pressure-Bearing and Force-Receiving Area Multi-Drive Chamber Hydraulic Cylinder and Hydraulic Cylinder System and Control Method"—work synergistically and mutually supportively, forming a complete technological innovation system. Through the organic combination of these three applications, a more efficient, durable, and reliable ultra-high energy impact operation system can be formed.

Claims

1. An impact device, characterized in that: It includes a main fixed connecting seat (1) for connecting the vehicle, a hammer (2), a hydraulic cylinder (3) and a hammer guide connected to the main fixed connecting seat (1). The cylinder body (301) of the hydraulic cylinder (3) is connected to the main fixed connecting seat (1), and the piston (302) of the hydraulic cylinder (3) is slidably installed in the cylinder body (301). The hammer (2) is located outside the cylinder body (301). The hammer guide is used to guide the hammer (2) axially and limit its radial movement. The piston rod (303) is used to drive the hammer (2) to make axial reciprocating impact movements along the hammer guide. The hammer (2) does not bear the hydraulic seal of the hydraulic cylinder (3). The hydraulic seal is achieved by the cooperation between the piston (302) of the hydraulic cylinder (3) and the cylinder body (301).

2. The impact device according to claim 1, characterized in that: The hammer guide is a lower housing (4), and the hammer (2) slides in contact with the inner wall of the lower housing (4); the lower housing (4) is fixedly connected to the main fixed connecting seat (1).

3. The impact device according to claim 1, characterized in that: The hammer guide is a guide structure (5) provided on the main fixed connecting seat (1); it also includes a guided component (6) fixedly connected to the hammer (2), and the guided component (6) slides in cooperation with the guide structure (5) of the main fixed connecting seat (1).

4. The impact device according to any one of claims 1 to 3, characterized in that: The output end of the piston rod (303) is driven to connect to the hammer (2). When the piston rod (303) extends, it drives the hammer (2) to move in the impact direction. When the piston rod (303) retracts, it drives the hammer (2) to move in the retraction direction.

5. The impact device according to claim 4, characterized in that: The output end of the piston rod (303) is integrally manufactured or fixedly connected to the hammer (2), and the two complete the impact synchronously; or, the output end of the piston rod (303) is movably connected to the hammer (2), and the piston rod (303) drives the hammer (2) to accelerate and then disengages from it, and the hammer (2) completes the impact by relying on inertia.

6. The impact device according to claim 5, characterized in that: When the output end of the piston rod (303) is movably connected to the hammer (2); It also includes a limiting cap (7), which is connected to the hammer (2); the limiting cap (7) is provided with a limiting structure (701), and the output end of the piston rod (303) is provided with a flange structure (304), which is located between the limiting structure (701) and the hammer (2); the limiting structure (701) and the hammer (2) are provided with an active stroke for the flange structure (304) to move axially along the piston rod (303) by contacting and cooperating with the limiting structure (701); the flange structure (304) can drive the hammer (2) to move in the retraction direction of the piston rod (303); the piston rod (303) and / or the flange structure (304) can drive the hammer (2) to move in the direction of the impact object.

7. The impact device according to claim 1, characterized in that: The piston (302) divides the cylinder (301) into a first chamber (3011) and a second chamber (3012). The first chamber (3011) is filled with hydraulic oil, and the second chamber (3012) is filled with high-pressure gas and / or hydraulic oil at room temperature. When the second chamber (3012) is filled with high-pressure gas at room temperature, the piston (302) is a hollow cup-shaped structure with the opening of the cup facing the high-pressure gas chamber at room temperature and communicating with it. The hollow cup-shaped structure is used to expand the total volume of the high-pressure gas chamber at room temperature, thereby reducing the compression ratio when the high-pressure gas at room temperature is compressed and reducing the weight of the piston (302).

8. The impact device according to claim 1, characterized in that: The hydraulic cylinder (3) is a negative pressure oil replenishment variable cross-section hydraulic cylinder; The cross-sectional area of ​​the negative pressure oil-replenishing variable cross-section hydraulic cylinder changes in an orderly manner according to a preset law during the sliding process. When the external load is small, the bearing area is actively reduced to increase the movement speed, and when the external load is large, the bearing area is actively increased to increase the driving force. The control of the negative pressure oil-replenishing variable cross-section hydraulic cylinder is based on the negative pressure oil replenishment effect, and the bearing area is actively adjusted according to the load change.

9. The impact device according to claim 8, characterized in that: It also includes a high-pressure gas chamber at room temperature located at the piston end away from the hammer (2), and the piston (302) of the hydraulic cylinder (3) extends into the high-pressure gas chamber at room temperature to form an impact device with hydraulic cylinder and high-pressure gas combined linkage at room temperature.

10. The impact device according to claim 1, characterized in that: It also includes a buffer component (8), which is connected to a fixed connector on the main fixed connector (1); when the hammer (2) moves to the set position, the hammer (2) or the component fixedly connected to the hammer (2) abuts against the buffer component (8) to achieve buffering.

11. The impact device according to claim 10, characterized in that: It also includes a buffer rod (9), one end of which is connected to the hammer (2), and the other end of which is used to abut against the buffer component (8) to achieve buffering.

12. An engineering machinery, characterized in that: The impact device includes any one of claims 1 to 11.

13. The engineering machinery according to claim 12, characterized in that: The engineering machinery mentioned includes hydraulic breakers, down-the-hole drills, top hammer drills, hydraulic pile hammers, vibratory pile hammers, dynamic compaction machines, stamping presses, forging presses, die forging hammers, tunnel boring machines, deep-sea pile hammers, underwater breakers, or seabed compactors.

14. A control method for an impact device according to any one of claims 1 to 11, characterized in that, Includes the following steps: S1: The hydraulic system drives the piston (302) inside the hydraulic cylinder (3) to move, and drives the hammer (2) located outside the hydraulic cylinder (3) through the piston rod (303), so that the hammer (2) moves toward the object being impacted; S2: The hammer (2) strikes the object being impacted, applying an impact; S3: After the impact is completed, the hydraulic system drives the piston (302) to retract, and drives the hammer (2) to retract, so as to carry out the next impact.

15. The control method according to claim 14, characterized in that, The impact device is the impact device according to claim 6, and the control method further includes: In step S1, the flange structure (304) at the output end of the piston rod (303) abuts against the limiting structure (701), pushing the hammer (2) to accelerate towards the impacted object; After step S1 and before step S2, there is also a disengagement step: the piston rod (303) stops or decelerates, causing the flange structure (304) to disengage from the limiting structure (701), and the hammer (2) and the piston rod (303) achieve motion decoupling; the hammer (2) completes the impact in step S2 by relying on its own inertia. In step S3, the piston rod (303) retracts, the flange structure (304) abuts against the limiting structure (701), and drives the hammer (2) to retract.

16. The control method according to claim 14, characterized in that, The impact device is the impact device according to claim 5, and the control method further includes: In step S1, the output end of the piston rod (303) moves synchronously with the hammer (2) toward the object being impacted and accelerates. In step S2, the piston rod (303) moves synchronously with the hammer (2) to strike the object being impacted, thus applying an impact. In step S3: After the impact is completed, the hydraulic system drives the piston (302) to retract, driving the hammer (2) to retract for the next impact.

17. The control method according to claim 14, characterized in that, The impact device is the impact device according to claim 10 or 11. After step S2 and before step S3, the hammer (2) or the buffer rod (9) only comes into contact with the buffer component (8) when the hammer (2) moves toward the object being impacted and passes its set position. The buffer component (8) absorbs the impact energy independently of the hydraulic system. Otherwise, the hammer (2) or the buffer rod (9) does not come into contact with the buffer component (8).

18. A method for impact operation of engineering machinery, characterized in that, Impact operations are performed using the control method described in any one of claims 14 to 17.

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