Impingement assembly and impingement device

Abstract

This application relates to the technical field of impact tools, specifically to an impact assembly and impact device. The impact assembly includes a housing, an impact structure, and a scraper ring. The housing includes a first cavity, and the impact structure includes a drive component, a transmission shaft, and a hammer. The hammer reciprocates, and the scraper ring is positioned between the hammer and the first cavity. When the hammer moves away from the drive component, the scraper ring scrapes lubricating material from the inner wall of the cavity to the impact end face area; when it moves closer, they separate to prevent reverse leakage. This configuration achieves directional delivery of lubricating material, solving the problem of it being thrown off; it provides adaptive control, improving utilization; it enhances lubrication continuity, reduces wear, and lowers maintenance costs. It solves the problem in existing impact tools where lubricating material cannot be retained on the impact end face, leading to decreased lubrication performance and easy wear on the output side.

Description

Technical Field

[0001] This application relates to the technical field of impact tools, and more particularly to an impact component and impact device. Background Technology

[0002] Impact tools such as impact wrenches and impact screwdrivers are widely used in industrial assembly and home repair due to their high-frequency impact characteristics. The core working component of these tools is the striking surface, which must withstand continuous high-intensity impacts and friction during operation, thus requiring extremely high lubrication performance. Typically, during the tool assembly stage, technicians precisely apply specialized lubricating grease to the striking surface to form a protective film to buffer impacts and reduce wear. This grease layer is a key barrier to ensure the stable operation of the tool.

[0003] However, the dynamic characteristics of the tool during operation become a hidden danger of lubrication failure. When an impact tool is started, the high-speed rotation of the internal components generates a strong centrifugal force. The grease that was originally attached to the impact surface is continuously thrown towards the inner wall of the housing under the centrifugal force. This thrown-out grease will gradually slide along the gaps in the inner wall into the depth of the inner cavity of the housing, completely detaching from the core working area.

[0004] The loss of lubricating grease directly triggers a chain of problems. When the impact surface loses sufficient grease protection, the frequency of direct contact between metal parts increases significantly, accelerating impact wear. Many tools, after a short period of high-frequency operation, exhibit malfunctions such as impact structure deformation and abnormal noises. This not only affects work efficiency but also necessitates frequent repairs and parts replacements, significantly increasing operating costs. This wear problem caused by lubrication failure has become a core technical bottleneck restricting the service life and reliability of impact tools. Utility Model Content

[0005] The purpose of this application is to provide an impact component and impact device to solve the problem that in current impact tools, the lubricating material cannot be retained on the impact end face of the impact structure, resulting in a serious decrease in the lubrication performance of the output side of the impact structure and easy wear.

[0006] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description or may be learned by practice of this application.

[0007] According to one aspect of this application, an impact assembly is provided, which mainly includes: a housing, an impact structure, and a scraper ring. The housing has a first cavity. The impact structure is disposed in the first cavity and includes a drive member, a transmission shaft, and a hammer. The hammer is sleeved on one end of the transmission shaft, and the output end of the drive member is connected to the other end of the transmission shaft. A channel for lubricant to pass through is formed between the outer wall of the hammer and the inner wall of the first cavity. The scraper ring is fixedly connected to the hammer and is disposed between the outer wall of the hammer and the inner wall of the housing. The drive member drives the transmission shaft to rotate, so that the hammer slides back and forth along the axis of the transmission shaft. When the hammer approaches the drive member, the scraper ring separates from the inner wall of the first cavity. When the hammer moves away from the drive member, the scraper ring abuts against the inner wall of the first cavity.

[0008] The specific technical solution described above can produce the following beneficial effects: First, this design achieves precise and directional delivery of lubricating material. The first chamber is divided into two parts by the cooperation of a scraper ring and an impact hammer. The reciprocating motion of the hammer creates pressure changes in the two parts of the first chamber. When the hammer moves away from the drive component, the scraper ring abuts against the inner wall of the first chamber, actively scraping the lubricating material from the inner wall towards the impact face of the hammer. Conversely, when the hammer approaches the drive component, the scraper ring moves away from the inner wall, preventing the lubricating material from flowing back. This design specifically addresses the problem of lubricating material being thrown towards the inner wall and gradually decreasing due to hammer rotation, ensuring that the lubricating material continuously concentrates towards the impact face and guarantees effective lubrication in the core area.

[0009] Secondly, the design of this scheme enables the impact component to have adaptive lubrication control capabilities. The entire directional delivery process of the lubricating material is automatically completed based on the air pressure generated by the hammer's motion, requiring no additional manual adjustment or power unit, thus achieving adaptive operation of the lubrication system. This design simplifies the operation process, reduces the need for human intervention, and improves the lubrication stability of the tool under complex working conditions.

[0010] Furthermore, the design of this scheme improves the utilization and retention of lubricating materials. When the scraper ring removes the lubricating material from the inner wall of the first cavity, it allows a larger amount of lubricating material to detach from the inner wall and enter the impact surface area, reducing material waste in non-core areas. At the same time, the directional delivery mechanism significantly reduces the ineffective loss of lubricating material caused by centrifugal force or reciprocating motion, allowing the limited lubricating material to act more efficiently on the impact end face and extending the effective duration of a single lubrication.

[0011] Furthermore, the design of this scheme enhances lubrication continuity to reduce wear. Because the impact face continuously receives sufficient and fresh lubricating material, the probability of direct contact between metal parts is further reduced, and the impact wear rate is more effectively controlled. Even in high-frequency, long-term operation scenarios, it can reduce hammer deformation, abnormal noise, and other malfunctions, further improving the operational stability and efficiency of the impact equipment.

[0012] Finally, this design also reduces maintenance costs and lowers the barrier to entry for use. Through adaptive lubrication control, it reduces the need for frequent component replacements due to insufficient lubrication, while also decreasing the frequency of periodic lubrication replenishment. From a long-term usage perspective, this significantly reduces maintenance costs and improves the tool's economy and durability.

[0013] According to some exemplary embodiments of this application, the hammer is provided with a mounting groove, and the scraper ring is embedded in the mounting groove.

[0014] In this type of embodiment, the design of the mounting groove and the scraper ring being embedded in the mounting groove firstly improves the working stability of the scraper ring. The embedded design provides a stable and reliable assembly reference for the scraper ring, effectively restricting the degree of freedom of the scraper ring in the axial direction of the hammer, avoiding problems such as the scraper ring moving or shifting during the reciprocating motion of the hammer, ensuring that the scraper ring can always fit with the inner wall of the first cavity according to the designed trajectory, and ensuring the stable realization of the lubricating material scraping and guiding functions.

[0015] Secondly, this design optimizes space utilization, featuring a compact structure. The scraper ring is embedded in the mounting slot without requiring additional cavity space, thus not increasing the overall volume of the impact assembly. This makes it particularly suitable for impact tools with limited internal space, facilitating the miniaturization of the equipment. Finally, in terms of assembly, the embedded installation method does not require a complex fixed structure, and the assembly process is convenient and efficient. It can reduce the operational difficulty in the production process, improve assembly efficiency, and reduce the risk of failure due to improper assembly.

[0016] According to some exemplary embodiments of this application, the impact assembly includes a transmission steel ball, the hammer is provided with a hollow second cavity, the inner wall of the second cavity is provided with a hammer ball groove, the transmission shaft is located in the second cavity, and a transmission shaft ball groove is provided on its radial outer side, the transmission steel ball is slidably located in both the hammer ball groove and the transmission shaft ball groove, and the mounting groove is provided on the radial outer side of the hammer corresponding to the hammer ball groove.

[0017] In this type of embodiment, the design of the mounting slot position has advantages in terms of structural stability. The mounting slot is located on the radial outer side of the ball groove corresponding to the hammer. This area belongs to the core area of ​​the transmission. The structure itself has high strength and good stability. Setting the mounting slot will not destroy the overall structural integrity of the hammer, ensuring that the hammer remains structurally stable during high-frequency reciprocating motion.

[0018] At the same time, the mounting slot in this position can ensure the axial balance and concentricity of the hammer. This position design avoids interference with the axial balance of the hammer, effectively ensures the concentricity of the hammer axis and the drive shaft axis, reduces additional wear caused by eccentricity, and improves the operating accuracy of the impact assembly.

[0019] Based on the structural characteristics of the transmission area, the scraper ring is more reliably fixed in the mounting groove, which can prevent displacement or loosening during the reciprocating sliding of the hammer, ensuring that the scraper ring always maintains a stable working posture and ensuring the continuous effectiveness of the scraping and guiding function of lubricating material.

[0020] In addition, this design can provide some radial support during the reciprocating motion of the hammer, reduce the radial sway of the hammer, improve its operational stability, and reduce noise and component wear caused by vibration.

[0021] According to some exemplary embodiments of this application, along the axial direction of the hammer, the mounting groove divides the hammer into a first segment and a second segment, the second segment being positioned closer to the drive member than the first segment, and the ratio of the axial length of the first segment to the axial length of the second segment is i, where 0 < i ≤ 0.15, or 0.8 ≤ i ≤ 9.3.

[0022] In this type of embodiment, for the case where 0 < i ≤ 0.15, the scraping ring and mounting groove are located at the end of the hammer and away from the drive component. This allows the scraped lubricating material to be concentrated at the end of the hammer (near the impact surface), reducing interference with the lubricating material near the drive component, preventing unnecessary overflow, ensuring sufficient lubricating material near the impact surface, and improving the targeted lubrication.

[0023] For 0.8≤i≤9.3, which corresponds to the mounting slot being located at the ball-slot position, this ratio range is suitable for the structural layout of the ball-slot. It can ensure the structural balance between the first and second sections of the hammer without affecting the normal operation of the transmission steel balls, maintain the axial stability of the hammer, and ensure that the scraper ring stably scrapes off the lubricating material during reciprocating motion, thus balancing structural reliability and lubrication retention.

[0024] The two ratio ranges are optimized for different mounting slot positions, effectively improving the directional control accuracy of the lubricating material and the overall working performance of the impact hammer.

[0025] According to some exemplary embodiments of this application, the scraper ring includes a fixing part and a lip. The fixing part has an annular structure and is fixed around the radial outer surface of the hammer. The lip is connected to the radial outer surface of the fixing part. In the axial direction of the fixing part, the diameter of the outer wall surface of the lip near the drive member is smaller than the diameter away from the drive member.

[0026] In this type of embodiment, under the action of air pressure difference, the lip adapts to the cooperation requirements between the hammer and the inner wall of the first cavity during the reciprocating motion. When the hammer moves away from the drive component, the lip scrapes the lubricating material by abutting against the inner wall of the first cavity. When it moves closer to the drive component, it can flexibly disengage to reduce motion resistance, thus balancing scraping effect and smooth motion.

[0027] The diameter of the outer wall of the lip near the drive component is smaller than that of the end away from the drive component, which can accurately adapt to the deformation requirements when the air pressure changes. This allows the deformation capacity to gradually increase with the axial position, matching the dynamic working conditions in the reciprocating motion of the hammer. It ensures that the fit between the lip and the inner wall of the first cavity is always optimal under different air pressure conditions, further improving the stability and efficiency of the directional delivery of lubricating materials.

[0028] When the air pressure changes on the side of the lip closest to the drive component, the pressure difference acts on the outer wall surface, generating a radial force: when the air pressure increases, gas rushes into the gap between the lip and the inner wall of the first cavity, forcing the lip to retract radially, assisting in its separation from the inner wall of the first cavity; when the air pressure decreases, a negative pressure is formed in the gap, which, combined with the lip's structural characteristics, makes it more tightly pressed against the inner wall of the first cavity. This air pressure adaptive mechanism significantly improves the response accuracy and reliability of the lip's movement, ensuring that lubricating material efficiently accumulates on the impact surface, further reducing loss and enhancing lubrication protection.

[0029] According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part, the outer wall of the lip is straight, and the angle between the outer wall of the lip and the outer wall of the fixing part is α, 15°≤α≤85°.

[0030] In this type of embodiment, the angle range adapts to the dynamic fit requirements between the impact hammer and the inner wall of the first cavity during reciprocating motion. The included angle of 15° to 85° provides sufficient deformation margin for the lip, ensuring that the lip can reliably fit and efficiently scrape lubricating material when the impact hammer is far from the drive component and needs to be in close contact with the inner wall; it also avoids excessive rigidity due to an angle that is too small (making it difficult to adapt to dynamic changes in the inner wall) or excessive deformation due to an angle that is too large (easily generating motion resistance or structural failure), so that the lip always maintains the optimal contact state during air pressure changes and reciprocating motion, improving the stability and dynamic fit accuracy of lubricating material orientation control, and further ensuring the efficient operation of the impact assembly.

[0031] According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part, the inner wall of the lip is straight or smooth curved, and a separation gap is formed between it and the outer wall of the fixing part. The separation gap gradually increases along the direction away from the driving member along the axis of the transmission shaft.

[0032] On the one hand, the gradual design of the separation gap provides the lip with a more flexible deformation space, making it easier for the lip to undergo adaptive deformation during the reciprocating motion of the hammer. This allows it to quickly respond to changes in air pressure and the dynamic matching requirements of the inner wall, improving the adaptability to reciprocating working conditions and ensuring the stability of scraping and collecting lubricating materials.

[0033] On the other hand, while ensuring the strength of the lip structure, the design reduces the volume and material usage of the lip, achieving lightweighting while reducing the additional resistance of the lip to the reciprocating motion of the hammer, improving the smoothness of the impact component's operation, and also reducing material costs, thus balancing structural reliability and economy.

[0034] According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part, both the inner and outer walls of the lip are straight, and the angle between the outer and inner walls of the lip is β, where 5°≤β≤12°.

[0035] This angle range precisely matches the dynamic fit requirements between the hammer and the inner wall of the first cavity during reciprocating motion. The included angle β, ranging from 5° to 12°, constructs a reasonable wedge-shaped structure for the lip: the lower limit of 5° ensures that the lip retains sufficient structural rigidity, avoiding insufficient deformation capacity due to an excessively small angle. It can quickly respond to air pressure changes and stably separate from the inner wall when the hammer approaches the drive component and needs to retract radially; the upper limit of 12° provides an appropriate deformation margin for the lip, ensuring that when the hammer moves away from the drive component and needs to expand radially to fit against the inner wall, it can fit tightly against the inner wall through uniform deformation, efficiently scraping and collecting lubricating material, while avoiding the problem of the lip being too soft and easily vibrating due to airflow impact caused by an excessively large angle.

[0036] This angle design ensures that the lip remains in a state of "rigidity and elasticity balance" during reciprocating motion. It can accurately respond to changes in air pressure to achieve dynamic contact and separation, and its stable structural shape can ensure the consistency of scraping lubricating material. This further improves the adaptability of the impact component to complex working conditions and enhances the reliability of the directional control of lubricating material.

[0037] According to another aspect of this application, an impact assembly is provided, which mainly includes: a housing, an impact structure, and a scraper ring. The housing has a first cavity, and the impact structure is disposed in the first cavity. The impact structure includes a drive member, a transmission shaft, and a hammer. The hammer is sleeved on one end of the transmission shaft, and the output end of the drive member is fixedly connected to the other end of the transmission shaft. A channel for lubricant to pass through is formed between the outer wall of the hammer and the first cavity. The scraper ring is disposed around the hammer and fixed on the inner wall of the first cavity. The drive member drives the transmission shaft to rotate, so that the hammer slides back and forth along the axis of the transmission shaft. The diameter of the scraper ring near the drive member is larger than the diameter of the scraper ring away from the drive member. When the hammer moves closer to the drive member, the scraper ring abuts against the outer wall of the hammer. When the hammer moves away from the drive member, the scraper ring separates from the outer wall of the hammer.

[0038] In this type of embodiment, when the hammer approaches the drive unit, the scraper ring abuts against the outer wall of the hammer, preventing the lubricating material from spreading to the side away from the impact surface; when the hammer moves away from the drive unit, the scraper ring separates from the outer wall of the hammer, leaving a channel for the lubricating material to flow to the impact surface, ultimately concentrating the lubricating material on one side of the impact surface, ensuring that the core working area always has sufficient lubricating material, thus achieving lubrication protection equivalent to the aforementioned solution.

[0039] Secondly, by utilizing the fluidity of the lubricating material, this structure can efficiently gather the dispersed lubricating material to the impact surface, ensuring sufficient volume to maintain the lubrication effect, reducing lubrication failure caused by material loss, significantly reducing the frequency of direct contact between metal parts, and mitigating impact wear.

[0040] Furthermore, the design of fixing the scraper ring to the inner wall of the cavity simplifies the hammer's structure, reduces the hammer load, and makes the hammer's reciprocating motion smoother. At the same time, the reverse structure is more adaptable to the cavity, can adapt to dynamic working conditions under high-frequency impact, and improves the stability of the relative motion between the scraper ring and the hammer.

[0041] Finally, by directional guidance, the lubricating material is continuously concentrated on one side of the impact surface, which extends the effective cycle of a single lubrication, reduces the need for frequent grease replenishment, lowers maintenance costs, further ensures the long-term stable operation of the impact components, and improves their reliability and service life.

[0042] According to another aspect of this application, an impact device is provided, which includes the impact components as described above.

[0043] This impact device, through the directional control and structural adaptation of the scraper ring in the impact assembly, can effectively concentrate the lubricating material on the impact surface, ensuring sufficient lubrication in the core working area. This significantly reduces problems such as component wear, deformation, and abnormal noise caused by lubrication failure, and significantly improves the stability and reliability of the equipment operation.

[0044] The efficient lubrication mechanism of the impact components extends the service life of the equipment, reduces the probability of failure under high-frequency operation, lowers the frequency and cost of maintenance and replacement of parts, and improves the continuous working capability of the equipment. It is especially suitable for high-frequency use scenarios such as industrial assembly and home repair.

[0045] The equipment operates more smoothly, with fewer instances of jamming and reduced efficiency due to insufficient lubrication, making operation more convenient. At the same time, the directional aggregation of lubricating materials reduces unnecessary loss, lowers the frequency of grease replenishment, reduces the maintenance burden, and lowers the overall operating cost of the equipment.

[0046] The various structural designs of the aforementioned impact components (such as different schemes for the position and shape of the scraper ring) can be flexibly adapted to different models of impact equipment, enabling the equipment to maintain excellent performance under design requirements such as miniaturization and high frequency, and providing strong support for the technological upgrading and application expansion of impact equipment.

[0047] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0048] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. It is obvious that the drawings described below are merely some embodiments of this application, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort.

[0049] Figure 1 This illustration shows a cross-sectional schematic diagram of an impact device according to one embodiment of this application.

[0050] Figure 2 This illustration shows a partial cross-sectional view of the impact structure of an impact assembly according to an embodiment of this application.

[0051] Figure 3 This illustration shows a cross-sectional schematic diagram of an impact device according to one embodiment of this application.

[0052] Figure 4 This illustration shows a partial cross-sectional view of a scraper ring according to one embodiment of the present application.

[0053] Figure 5 This illustration shows a three-dimensional structural diagram of a scraper ring according to one embodiment of the present application.

[0054] Figure 6 This illustration shows a partial cross-sectional view of a scraper ring according to one embodiment of the present application.

[0055] The above figures include the following reference numerals: 10. Shell; 11. First cavity; 20. Impact structure; 21. Drive component; 22. Drive shaft; 23. Hammer; 231. Mounting slot; 232. First section; 233. Second section; 24. Strike shaft; 30. Scraper ring; 31. Fixing part; 311. Outer wall of fixing part; 32. Lip; 321. Outer wall; 322. Inner wall; 33. Separation gap; α, the angle between the outer wall of the lip and the outer wall of the fixing part; β, the angle between the outer wall and the inner wall of the lip. Detailed Implementation

[0056] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, they are provided so that this application will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore their detailed description will be omitted.

[0057] The features, structures, or characteristics described above can be combined in any suitable manner in one or more embodiments, and where possible, the features discussed in the various embodiments are interchangeable. In the above description, numerous specific details are provided to give a full understanding of embodiments of this application. However, those skilled in the art will recognize that the technical solutions of this application can be practiced without one or more of the specific details described, or other methods, components, materials, etc., can be employed. In other instances, well-known structures, materials, or operations are not shown or described in detail to avoid obscuring various aspects of this application.

[0058] Although this application uses relative terms such as "up" and "down" to describe the relative relationship of one component of an icon to another, these terms are used only for convenience, such as the orientation of the example shown in the accompanying drawings. It is understood that if the icon's arrangement is flipped so that it is upside down, the component described as "up" will become the component described as "down". Other relative terms, such as "high", "low", "top", "bottom", "front", "back", "left", and "right", also have similar meanings. When a structure is "up" of another structure, it may mean that the structure is integrally formed on the other structure, or that the structure is "directly" mounted on the other structure, or that the structure is "indirectly" mounted on the other structure through another structure.

[0059] In this application, the terms “a,” “an,” “the,” “the,” and “at least one” are used to indicate the presence of one or more elements / components / etc.; the terms “comprising,” “including,” and “having” are used to indicate an open-ended inclusion meaning and to mean that there may be other elements / components / etc. in addition to the listed elements / components / etc.

[0060] Therefore, this application proposes some exemplary embodiments to at least partially address the problems or deficiencies of the prior art.

[0061] Please see Figure 1In some exemplary embodiments of this application, an impact assembly is provided, which mainly includes: a housing 10, an impact structure 20, and a scraper ring 30. The housing 10 is configured with a first cavity 11. The impact structure 20 is disposed in the first cavity 11 and includes a driving member 21, a transmission shaft 22, and a hammer 23. The hammer 23 is sleeved on one end of the transmission shaft 22, and the output end of the driving member 21 is connected to the other end of the transmission shaft 22. A channel for lubricant to pass through is formed between the outer wall of the hammer 23 and the inner wall of the first cavity 11. The scraper ring 30 is fixedly connected to the hammer 23 and is arranged around the outer wall of the hammer 23 and the inner wall of the housing 10. The driving member 21 drives the transmission shaft 22 to rotate, so that the hammer 23 slides back and forth along the axis of the transmission shaft 22. When the hammer 23 approaches the driving member 21, the scraper ring 30 separates from the inner wall of the first cavity 11. When the hammer 23 moves away from the driving member 21, the scraper ring 30 abuts against the inner wall of the first cavity 11.

[0062] The specific technical solution described above can produce the following beneficial effects: First, this embodiment achieves precise directional delivery of lubricating material. The first cavity 11 is divided into two parts by the dynamic interaction between the scraper ring 30 and the impact hammer 23. Utilizing the pressure changes within the cavity caused by the reciprocating motion of the impact hammer 23, an efficient directional delivery mechanism is formed: when the impact hammer 23 moves away from the drive component 21, the scraper ring 30 abuts against the inner wall of the first cavity 11, actively scraping the lubricating material adhering to the inner wall of the first cavity 11 towards the area of ​​the impact hammer 23 near the impact end face; when the impact hammer 23 moves closer to the drive component 21, the scraper ring 30 separates from the inner wall of the first cavity 11, preventing the lubricating material from flowing backwards. This design specifically solves the problem of lubricating material being thrown towards the inner wall and gradually flowing away due to the rotation of the impact hammer 23, ensuring that the lubricating material continuously concentrates towards the impact end face, stably guaranteeing the lubrication effect in the core area.

[0063] Secondly, this embodiment endows the impact assembly with adaptive lubrication control capabilities. The directional delivery of lubricating material is entirely achieved automatically based on the air pressure difference generated by the movement of the hammer 23, without the need for additional manual adjustment or power devices, thus enabling the lubrication system to have adaptive operating characteristics. This design simplifies the operation process, reduces the need for human intervention, and significantly improves the lubrication stability of the tool under complex working conditions.

[0064] Furthermore, this embodiment improves the utilization and retention of lubricating material. When scraping the lubricating material from the inner wall of the first cavity 11, the scraper ring 30 can push more material off the inner wall and flow to the impact surface area, reducing material retention and waste in non-core areas; at the same time, the directional delivery mechanism significantly reduces the ineffective loss of lubricating material caused by centrifugal force or reciprocating motion, allowing limited material to act more efficiently on the impact end face and extending the effective duration of a single lubrication.

[0065] Furthermore, this embodiment effectively reduces component wear by enhancing lubrication continuity. Because the impact face continuously receives sufficient and fresh lubricating material, the probability of direct contact between metal parts is significantly reduced, and the impact wear rate is more effectively controlled. Even in high-frequency, long-term operation scenarios, it can reduce malfunctions such as deformation and abnormal noise of the impact hammer 23, further improving the operational stability and work efficiency of the impact equipment.

[0066] Finally, this embodiment also reduces equipment maintenance costs and lowers the barrier to entry for use. The adaptive lubrication control design reduces the need for frequent component replacements due to insufficient lubrication, while also reducing the frequency of periodic lubrication replenishment. From a long-term usage perspective, this significantly reduces maintenance costs and improves the tool's economy and durability.

[0067] Furthermore, when applying the above embodiments, non-continuous contact avoids the scraper ring 30 causing additional obstruction to the operation of the hammer 23. When the hammer 23 approaches the drive member 21, the scraper ring 30 separates from the inner wall of the first cavity 11, eliminating the motion resistance generated by continuous friction, ensuring smoother reciprocating sliding of the hammer 23, avoiding increased energy consumption or action jamming caused by prolonged contact, and ensuring the operating efficiency of the impact assembly. The reduction in contact time can significantly reduce component wear. Contact only during the necessary scraping stage reduces the frequency of friction between the scraper ring 30 and the inner wall of the first cavity 11, which can slow down the wear rate of both, extend service life, reduce the risk of lubrication control failure due to component wear, and further improve the long-term reliability of the impact assembly.

[0068] The scraper ring 30 only contacts the inner wall of the first cavity 11 as the hammer 23 moves away from the drive member 21. The two are not in constant contact. This avoids affecting the operation of the hammer 23 and reduces the contact time, thus reducing the wear on the first cavity 11 and the scraper ring 30.

[0069] Based on the above embodiments, the scraper ring 30 has a roughly annular structure, which is compatible with the roughly cylindrical hammer 23, and the axes of the two are basically coincident after assembly.

[0070] In an optional embodiment, the scraper ring 30 may be made of an elastic material, and its inner ring is interference-fitted with the hammer 23, directly fitted on the radial outer side of the hammer 23, and integrated as one unit through interference fit.

[0071] In an optional embodiment, the inner ring of the scraper ring 30 is bonded to the hammer 23 by an adhesive material.

[0072] In an optional embodiment, a corresponding snap-fit ​​structure can also be provided between the scraper ring 30 and the hammer 23. For example, a radially inwardly extending snap block can be provided on the inner side of the inner ring of the scraper ring 30, and a radially inwardly extending snap groove can be provided on the hammer 23. In this way, the scraper ring 30 can be snap-fitted and fixed after being fitted together, while preventing the scraper ring 30 from rotating circumferentially relative to the hammer 23, thus reducing the risk of falling off.

[0073] Please see Figure 1 In one specific embodiment, the hammer 23 is a transmission component, and a striking shaft 24 is fitted onto its end face. The striking shaft 24 is axially connected to the hammer 23. The axial end face of the hammer 23 and the axial end face of the connecting end of the striking shaft 24 are working surfaces that require lubrication. A sealing element is provided between the striking shaft 24 and the axial inner end face of the housing 10 to prevent lubricating material from overflowing. The lubricating material can be selected as grease, solid lubricant, etc.

[0074] Optionally, the first cavity 11 of the housing 10 is generally a hollow cylinder, with an opening at one end for the extension and retraction of the striking shaft 24. The axis of the first cavity 11 generally coincides with the axis of the hammer 23, the axis of the drive shaft 22, and the axis of the striking shaft 24.

[0075] Optionally, the drive unit 21 is specifically a servo motor.

[0076] Please see Figure 1 and Figure 2 In some exemplary embodiments of this application, the hammer 23 is provided with a mounting groove 231, and the scraper ring 30 is embedded in the mounting groove 231.

[0077] In this type of embodiment, the embedded structure provides a stable assembly reference for the scraper ring 30. By restricting its axial degree of freedom, it effectively avoids the axial displacement of the hammer 23 during reciprocating motion, ensuring the stable realization of the lubricating material scraping and guiding functions. At the same time, this design does not occupy additional cavity space, achieving a compact structure that is suitable for impact tools with limited internal space, facilitating equipment miniaturization. In addition, the embedded installation without a complex fixing structure simplifies the assembly process, improving efficiency while reducing the risk of failure caused by improper assembly.

[0078] Based on the above embodiments, multiple mounting grooves 231 can be arranged radially, corresponding to multiple scraper rings 30. This reduces the risk of lubricating material escaping to the side near the drive member 21 during reciprocating motion.

[0079] Alternatively, the scraper ring 30 can be designed as multiple segments, which can be combined to form a complete annular structure. Multiple mounting slots 231 can be configured to form a complete annular groove, with adjacent mounting slots 231 spaced apart. This allows the scraper ring 30 to be individually installed into a single mounting slot 231. This design can accommodate other structural requirements within the first cavity 11, reducing interference. Furthermore, this embedding method prevents the scraper ring 30 from rotating around its axis within the mounting slot 231, improving structural stability and reducing the possibility of wear.

[0080] Please see Figure 3 According to some exemplary embodiments of this application, the impact assembly includes a transmission steel ball, the hammer 23 is provided with a hollow second cavity, the inner wall of the second cavity is provided with a hammer ball groove, a portion of the transmission shaft 22 is located in the second cavity, and a transmission shaft ball groove is provided on its radial outer side, the transmission steel ball is slidably located in both the hammer ball groove and the transmission shaft ball groove, and the mounting groove 231 is provided on the radial outer side of the hammer 23 corresponding to the hammer ball groove.

[0081] The mounting groove 231 is located radially outside the ball groove corresponding to the hammer 23. This design has multiple advantages: as the core area of ​​the transmission, this area itself has high structural strength and good stability. Setting the mounting groove 231 will not damage the overall structural integrity of the hammer 23, ensuring its stability during high-frequency reciprocating motion. At the same time, this position can avoid interfering with the axial balance of the hammer 23, effectively ensuring the concentricity of the hammer 23 and the transmission shaft 22, reducing additional wear caused by eccentricity, and improving operating accuracy. Relying on the structural characteristics of the transmission area, the scraper ring 30 is more reliably fixed in the mounting groove 231, which can prevent displacement or loosening during reciprocating sliding and ensure the continuous effectiveness of the lubricating material scraping and guiding function. In addition, this design can also provide a certain radial support for the hammer 23, reduce its radial sway, improve operating stability, and reduce noise and component wear caused by vibration.

[0082] It is understandable that the ball groove of the drive shaft has a certain axial length in the axial direction of the hammer 23. When the mounting groove 231 is set here, the force such as contact and friction between it and the first cavity 11 is transmitted to the hammer 23 within the range of this axial length. Due to the presence of the steel ball and the requirements for transmission, the radial fit within this range is very stable. Therefore, the transmission of force such as contact and friction between the scraper ring 30 and the first cavity 11 will not affect the fit between the hammer 23 and the drive shaft 22.

[0083] Please see Figures 1 to 3According to some exemplary embodiments of this application, along the axial direction of the hammer 23, the mounting groove 231 is located at the two ends of the hammer 23, which are respectively a first segment 232 and a second segment 233. The second segment 233 is located closer to the drive member 21 than the first segment 232. The ratio of the axial length of the first segment 232 to the axial length of the second segment 233 is i, where 0 < i ≤ 0.15, or 0.8 ≤ i ≤ 9.3.

[0084] Please see Figure 1 For the case where 0 < i ≤ 0.15, the scraping ring 30 and the mounting groove 231 are located at the end of the hammer 23 and away from the drive member 21. This can concentrate the scraped lubricating material at the end of the hammer 23 (near the impact surface), reduce interference with the lubricating material on the drive member 21 side, avoid unnecessary overflow, ensure sufficient lubricating material near the impact surface, and improve the targeted lubrication.

[0085] Please see Figure 3 For 0.8≤i≤9.3, which corresponds to the mounting slot 231 being located in the ball-bearing groove, this ratio range is adapted to the structural layout characteristics of the ball-bearing groove. It can ensure the structural balance of the first section 232 and the second section 233 of the hammer 23 while not interfering with the normal operation of the transmission steel ball, ensuring the axial stability of the hammer 23, and ensuring that the scraper ring 30 stably scrapes off the lubricating material in reciprocating motion, thus taking into account both structural reliability and lubrication retention effect.

[0086] Understandably, the two ratio ranges are specifically optimized for different positions of the mounting slot 231, effectively improving the directional control accuracy of the lubricating material and the overall working performance of the hammer 23.

[0087] Preferably, when the mounting groove 231 is located at the ball pit position, the ratio i of the axial length of the first segment 232 to the axial length of the second segment 233 is between 0.23 and 0.78.

[0088] The specific ratio i can be 0.23, 0.24, 0.25, 0.26, 0.27, 0.28, 0.29, 0.3, 0.31, 0.32, 0.33, 0.34, 0.35, 0.36, 0.37, 0.38, 0.39, 0.4, 0.41, 0.42, 0.43, 0.44, 0.45, 0.46, 0.47, 0.48, 0.49, 0.5, 0.51, 0.52, 0.53, 0.54, 0.55, 0.56, 0.57, 0.58, 0.59, 0.6, 0.61, 0.62, 0.63, 0.64, 0.65, 0.66, 0.67, 0.68, 0.69, 0.7, 0.71, 0.72, 0.73, 0.74, 0.75, 0.76, 0.77, 0.78, etc., but not limited to these.

[0089] Preferably, when the scraper ring 30 and the mounting groove 231 are located at the end of the hammer 23 and far away from the drive member 21, the ratio i of the axial length of the first segment 232 to the axial length of the second segment 233 is between 0.5 and 0.15.

[0090] The specific ratio i can be 0.05, 0.06, 0.07, 0.08, 0.09, 0.1, 0.11, 0.12, 0.13, 0.14, 0.15, etc., but is not limited to these.

[0091] In one specific embodiment, the ratio i of the axial length of the first segment 232 to the axial length of the second segment 233 is preferably 0.0534.

[0092] Please see Figures 4 to 6 According to some exemplary embodiments of this application, the scraper ring 30 includes a fixing part 31 and a lip 32. The fixing part 31 has an annular structure and is fixed around the radial outer surface of the hammer 23. The lip 32 is connected to the radial outer surface of the fixing part 31. In the axial direction of the fixing part 31, the diameter of the outer wall 321 of the lip 32 near the drive member 21 is smaller than the diameter away from the drive member 21.

[0093] In this type of embodiment, under the action of air pressure difference, the lip 32 adapts to the matching requirements of the hammer 23 and the inner wall of the first cavity 11 during the reciprocating motion through deformation: when the hammer 23 is away from the drive member 21, the lip 32 scrapes the lubricating material efficiently by abutting against the inner wall of the first cavity 11; when it is close to the drive member 21, it can flexibly disengage to reduce motion resistance, thus balancing the scraping effect and the smoothness of motion.

[0094] The diameter of the outer wall 321 of the lip 32 near the drive member 21 is smaller than the diameter of the end away from the drive member 21. This allows for precise matching of deformation requirements under varying air pressure, enabling the deformation capacity to gradually increase with axial position. This perfectly adapts to the dynamic working conditions of the reciprocating motion of the hammer 23, ensuring that the fit between the lip 32 and the inner wall of the first cavity 11 is always optimal under different air pressure conditions, further improving the stability and efficiency of the directional delivery of lubricating materials.

[0095] Simultaneously, the pressure difference created by the change in air pressure generates a radial force on the outer wall 321 of the lip 32: when the air pressure increases, gas rushes into the gap between the lip 32 and the inner wall of the first cavity 11, pushing the lip 32 radially inward and assisting it to quickly separate from the inner wall of the first cavity 11; when the air pressure decreases, a negative pressure is formed in the gap, which, combined with the structural characteristics of the lip 32, makes it fit more tightly against the inner wall of the first cavity 11. This air pressure adaptive mechanism significantly improves the response accuracy and reliability of the lip 32's movement, ensuring that lubricating material is efficiently concentrated on the impact surface, further reducing loss and enhancing the lubrication protection effect.

[0096] Based on the above embodiments, the fixing part 31 may be a ring-shaped structure adapted to the mounting groove 231. The inner wall and outer wall of the fixing part 31 are both radial sides of a cylinder, with high concentricity, and can be adapted to the mounting groove 231.

[0097] Alternatively, the outer wall 321 of the lip 32 may be approximately a tapered conical surface.

[0098] Alternatively, the outer wall 321 of the lip 32 may vary linearly in the cross section passing through the axis of the fixing part 31.

[0099] Please see Figure 4 According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part 31, the outer wall 321 of the lip 32 is straight or smooth curved.

[0100] In this type of embodiment, the outer wall 321 of the lip 32 adopts a smooth surface design, which can significantly reduce air friction resistance, avoid creating additional obstacles to the reciprocating motion of the hammer 23, ensure smooth operation of the impact component, and directly improve the working efficiency of the tool. The low friction characteristics can also reduce the wear of the lip 32 caused by continuous friction, reduce the probability of damage, ensure the long-term stability of the lubricating material scraping effect, indirectly extend the service life of the whole machine and reduce the frequency of maintenance and replacement. At the same time, the linear or smooth curve structural design simplifies the processing technology, facilitates precise control of dimensional accuracy, reduces the difficulty of production technology and manufacturing costs, and provides convenience for stable mass production.

[0101] Please see Figure 6 According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part 31, the outer wall 321 of the lip 32 is straight, and the included angle between the outer wall 321 of the lip 32 and the outer wall 311 of the fixing part is α, 15°≤α≤85°.

[0102] Preferably, the included angle α between the outer wall 321 of the lip 32 and the outer wall 311 of the fixing part is between 15° and 45°.

[0103] Preferably, the angle α between the outer wall 321 of the lip 32 and the outer wall 311 of the fixing part is 21°.

[0104] Preferably, the included angle α between the outer wall 321 of the lip 32 and the outer wall 311 of the fixing part is 45°.

[0105] The angle α between the outer wall 321 of the lip 32 and the outer wall 311 of the fixing part can specifically be 15 degrees, 16 degrees, 17 degrees, 18 degrees, 19 degrees, 20 degrees, 21 degrees, 22 degrees, 23 degrees, 24 degrees, 25 degrees, 26 degrees, 27 degrees, 28 degrees, 29 degrees, 30 degrees, 31 degrees, 32 degrees, 33 degrees, 34 degrees, 35 degrees, 36 degrees, 37 degrees, 38 degrees, 39 degrees, 30 degrees, 41 degrees, 42 degrees, 43 degrees, 44 degrees, 45 degrees, 46 degrees, 47 degrees. The degrees range from 48 degrees, 49 degrees, 50 degrees, 51 degrees, 52 degrees, 53 degrees, 54 degrees, 55 degrees, 56 degrees, 57 degrees, 58 degrees, 59 degrees, 60 degrees, 61 degrees, 62 degrees, 63 degrees, 64 degrees, 65 degrees, 66 degrees, 67 degrees, 68 degrees, 69 degrees, 70 degrees, 71 degrees, 72 degrees, 73 degrees, 74 degrees, 75 degrees, 76 degrees, 77 degrees, 78 degrees, 79 degrees, 80 degrees, 81 degrees, 82 degrees, 83 degrees, 84 degrees, 85 degrees, etc., but are not limited to these.

[0106] Please see Figure 5 According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part 31, the inner wall 322 of the lip 32 is straight or smooth curved, and a separation gap 33 is formed between it and the outer wall 311 of the fixing part. The separation gap 33 gradually increases along the axis of the transmission shaft 22 away from the driving member 21.

[0107] From a dynamic adaptability perspective, the gradually expanding design of the separation gap 33 provides a gradient deformation buffer space for the lip 32. When the hammer 23 approaches the drive member 21, the air pressure on the side of the first cavity 11 closest to the drive member 21 increases, and the lip 32 needs to radially retract to separate from the inner wall of the first cavity 11. At this time, the smaller initial gap (closer to the drive member 21 end) can avoid structural instability caused by excessive deformation of the lip 32, while the gradually increasing gap (away from the drive member 21 end) provides sufficient shrinkage margin for the lip 32, ensuring a smooth and controllable deformation process. When the hammer 23 moves away from the drive member 21, the air pressure on the side away from the drive member 21 increases, and the lip 32 needs to radially expand to tightly fit the inner wall. The gradually expanding gap can guide the lip 32 to deform gradually from the root to the end, making the fitting pressure more uniform and avoiding wear or failure caused by local stress concentration, perfectly adapting to the complex dynamic fit requirements in reciprocating motion.

[0108] From the perspective of structural economy and operational efficiency, this design achieves "precise weight reduction" while ensuring the core function of the lip 32. The existence of the separation gap 33 reduces the amount of unnecessary material used in the lip 32. On the one hand, it reduces the inertial mass of the lip 32 itself, reducing the additional load during the reciprocating motion of the hammer 23, making the impact assembly operate more smoothly and efficiently, especially in high-frequency operation scenarios, significantly reducing drive energy consumption. On the other hand, the reduction in material usage directly reduces manufacturing costs, and the lightweight design is more suitable for the internal space constraints of miniaturized impact equipment, improving the flexibility of structural layout. At the same time, the straight or smooth curved shape of the inner wall 322 avoids stress concentration caused by complex structures, further ensuring the structural stability of the lip 32, extending its service life, and indirectly improving the reliability of the entire machine.

[0109] Please see Figure 6 According to some exemplary embodiments of this application, in a cross section passing through the axis of the fixing part 31, both the inner wall 322 and the outer wall 321 of the lip 32 are straight, and the angle between the outer wall 321 and the inner wall 322 of the lip 32 is β, 5°≤β≤12°.

[0110] An included angle β of 5° to 12° provides the lip 32 with a reasonable wedge-shaped structure that adapts to the reciprocating motion of the hammer 23 and the dynamic cooperation with the inner wall of the first cavity 11: the lower limit of the angle of 5° ensures that the lip 32 has sufficient structural rigidity, avoiding insufficient deformation capacity due to the angle being too small. When the hammer 23 is close to the drive component 21 and needs to retract radially, it can quickly respond to changes in air pressure and stably separate from the inner wall of the first cavity 11; the upper limit of the angle of 12° provides the lip 32 with a moderate deformation margin, ensuring that when the hammer 23 is far away from the drive component 21 and needs to expand radially to fit against the inner wall of the first cavity 11, it can fit tightly and efficiently scrape the lubricating material through uniform deformation, while avoiding the problem of the lip 32 being too soft and easily vibrating due to airflow impact caused by the angle being too large.

[0111] This angle design ensures that the lip 32 maintains a "rigidity-elasticity balance" during reciprocating motion. It can accurately respond to changes in air pressure to achieve dynamic fitting and separation, and the stable structure ensures the consistency of lubricant scraping. This further improves the adaptability of the impact component to complex working conditions and enhances the reliability of lubricant directional control.

[0112] Preferably, the angle β between the outer wall 321 and the inner wall 322 of the lip 32 is in the range of 7° to 10°.

[0113] Preferably, the angle β between the outer wall 321 and the inner wall 322 of the lip 32 is 9°.

[0114] The angle β between the outer wall 321 and the inner wall 322 of the lip 32 can be 5 degrees, 6 degrees, 7 degrees, 8 degrees, 9 degrees, 10 degrees, 11 degrees, 12 degrees, etc., but is not limited to this.

[0115] Please see Figure 5 According to some exemplary embodiments of this application, the thickness of the end of the lip 32 away from the fixing part 31 is less than the thickness of the end of the lip 32 close to the fixing part 31.

[0116] The connection between the outer wall 321 and the inner wall 322 of the lip 32 adopts a smooth transition design, which improves the structural strength of the connection position with the fixing part 31. This design can effectively disperse the continuous stress impact generated by the high-frequency reciprocating motion of the hammer 23, avoid root fracture or loosening caused by long-term stress, and significantly extend the service life of the lip 32. At the same time, the smaller size of the end of the lip 32 gives it greater deformation flexibility and can accurately respond to changes in air pressure: when the hammer 23 is away from the drive member 21 and needs to fit against the inner wall of the first cavity 11, the end can tightly wrap the inner wall of the first cavity 11 through appropriate deformation to ensure thorough scraping of lubricating material; when the hammer 23 is close to the drive member 21 and needs to separate, the end can flexibly retract to reduce frictional resistance. This structure not only strengthens the stability of the connection part, but also ensures the dynamic adaptability of the end, taking into account both strength and flexibility, and provides reliable support for the efficient control of lubricating material.

[0117] According to some exemplary embodiments of this application, the lip 32 and the fixing part 31 are integrally formed, or the lip 32 and the fixing part 31 are an integral structure, and both the lip 32 and the fixing part 31 are made of elastic material.

[0118] From a structural reliability perspective, the integrated structure completely eliminates assembly gaps and weak points between components, resulting in superior overall rigidity and continuity. It can effectively resist the continuous stress impact and vibration generated during the high-frequency reciprocating motion of the hammer 23. Compared to a split structure, it can fundamentally avoid failures such as separation or loosening of the lip 32 and the fixing part 31 caused by long-term stress, significantly improving the overall structural strength and durability of the scraper ring 30 and greatly extending its service life.

[0119] From the perspective of deformation adaptability, the integrated structure endowed by the elastic material possesses excellent elastic deformation capability. During the reciprocating motion of the hammer 23, the lip 32 needs to frequently deform to achieve contact or separation with the inner wall of the first cavity 11. The integrated elastic structure ensures that the deformation process is uniform and continuous—neither excessive local rigidity hinders the action response, nor insufficient elasticity affects the tightness of the contact. This characteristic is perfectly adapted to the high-frequency dynamic working conditions of the impact component, accurately responding to changes in air pressure to achieve flexible deformation, stably ensuring the scraping and directional delivery effect of lubricating material, and further enhancing the lubrication protection of the impact surface.

[0120] Based on the above embodiments, the lip 32 and the fixing part 31 can be formed into an integral structure by subtractive processing, or integrally formed by injection molding, 3D printing or other methods.

[0121] According to some exemplary embodiments of this application, the lip 32 is made of fluororubber, perfluoroether rubber, fluorosilicone rubber, hydrogenated nitrile rubber or high-temperature silicone rubber.

[0122] When fluororubber is used for the lip 32, it exhibits excellent high-temperature resistance (typically withstanding 200~260℃), maintaining structural stability in the medium-to-high temperature environment generated by high-frequency friction of impact components, and is not prone to hardening or cracking; it also has strong wear resistance, withstanding long-term scraping against the inner wall of the first cavity 11; and it has good compatibility with most lubricating greases and is not prone to swelling. However, its low-temperature elasticity is poor (it easily becomes brittle below -20℃), its deformation response decreases under extreme low-temperature conditions, and its cost is higher than that of ordinary rubber.

[0123] When the lip 32 is made of perfluoroelastomer rubber, its high-temperature resistance is the best in its class (withstanding temperatures above 300°C), and it has extremely strong chemical stability, capable of resisting extreme high temperatures and complex media corrosion that may occur within impact components. It also boasts outstanding wear resistance and tear resistance, resulting in a long service life. However, its elasticity is slightly inferior to other fluororubbers, and its cost is high, making it suitable for applications with extremely high-temperature resistance requirements, thus limiting its versatility.

[0124] When the lip 32 is made of fluorosilicone rubber, it combines the high-temperature resistance of fluororubber (temperature resistance of approximately -60~200℃) with the excellent elasticity of silicone rubber, exhibiting outstanding low-temperature performance and maintaining stable deformation even under conditions with large temperature differences. It also has good compatibility with lubricating greases and is not prone to aging. However, its wear resistance is slightly weaker than that of fluororubber and perfluoroether rubber, and it may experience accelerated wear under long-term high-frequency scraping. It is more suitable for scenarios with large temperature fluctuations but moderate friction intensity.

[0125] When the lip 32 is made of hydrogenated nitrile rubber, it exhibits excellent wear resistance and tear resistance, resulting in slow wear during frequent contact with the inner wall of the cavity 11. It also demonstrates outstanding oil resistance, excellent compatibility with lubricating greases, and is less prone to swelling. Furthermore, its cost is relatively low. However, its high-temperature resistance is limited (typically not exceeding 150℃). In high-temperature environments where impact components operate at long-term high frequencies, it may experience a decrease in elasticity or hardening, making it suitable for medium-low temperature, high-friction conditions.

[0126] When the lip 32 is made of high-temperature silicone rubber, it exhibits good high-temperature resistance (withstanding temperatures from -60°C to 200°C), excellent elasticity, and flexible deformation response, enabling it to quickly adapt to the bonding and separation requirements of the hammer 23 during reciprocating motion. It also boasts lower cost and greater ease of processing. However, its wear resistance is a weakness; prolonged friction with the inner wall can easily cause wear, and its oil resistance is slightly weaker, potentially leading to slight swelling upon contact with certain lubricating greases. Therefore, it is more suitable for low-friction, medium-to-high-temperature, light-load applications.

[0127] In addition, these materials are highly compatible with lubricating greases and are not prone to swelling or aging. They can maintain their elasticity and structural stability, further improving the adaptability and reliability of the lip 32 under complex working conditions, and providing a lasting guarantee for the efficient operation of impact components.

[0128] According to another aspect of this application, an impact assembly is provided, which mainly includes: a housing 10, an impact structure 20, and a scraper ring 30. The housing 10 has a first cavity 11, and the impact structure 20 is disposed within the first cavity 11. The impact structure 20 includes a drive member 21, a transmission shaft 22, and a hammer 23. The hammer 23 is sleeved on one end of the transmission shaft 22, and the output end of the drive member 21 is fixedly connected to the other end of the transmission shaft 22. A channel for lubricant to pass is formed between the outer wall of the hammer 23 and the first cavity 11. The scraper ring 30 is disposed around the hammer 23 and fixed to the inner wall of the first cavity 11. The drive member 21 drives the transmission shaft 22 to rotate, so that the hammer 23 reciprocates along the axis of the transmission shaft 22. The diameter of the scraper ring 30 near the drive member 21 is larger than the diameter of the scraper ring 30 away from the drive member 21. When the hammer 23 moves closer to the drive member 21, the scraper ring 30... The scraper ring 30 abuts against the outer wall of the hammer 23, and when the hammer 23 moves away from the drive member 21, the scraper ring 30 separates from the outer wall of the hammer 23.

[0129] In this type of embodiment, when the hammer 23 approaches the drive member 21, the scraper ring 30 abuts against the outer wall of the hammer 23, preventing the lubricating material from spreading to the side away from the impact surface; when the hammer 23 moves away from the drive member 21, the scraper ring 30 separates from the outer wall of the hammer 23, leaving a channel for the lubricating material to flow to the impact surface, ultimately concentrating the lubricating material on one side of the impact surface, ensuring that the core working area always has sufficient lubricating material, thus achieving lubrication protection equivalent to the aforementioned solution.

[0130] Secondly, by utilizing the fluidity of the lubricating material, this structure can efficiently gather the dispersed lubricating material to the impact surface, ensuring sufficient volume to maintain the lubrication effect, reducing lubrication failure caused by material loss, significantly reducing the frequency of direct contact between metal parts, and mitigating impact wear.

[0131] Furthermore, the design of fixing the scraper ring 30 to the inner wall of the cavity 11 simplifies the structure of the hammer 23 itself, reduces the load on the hammer 23, and makes the reciprocating motion of the hammer 23 smoother. At the same time, the reverse structure is more compatible with the cavity 11, can adapt to the dynamic working conditions under high-frequency impact, and improves the stability of the relative motion between the scraper ring 30 and the hammer 23.

[0132] Finally, by directional guidance, the lubricating material is continuously concentrated on one side of the impact surface, which extends the effective cycle of a single lubrication, reduces the need for frequent grease replenishment, lowers maintenance costs, further ensures the long-term stable operation of the impact components, and improves their reliability and service life.

[0133] Based on the above embodiments, a corresponding mounting groove 231 can be provided in the first cavity 11 for mounting the scraper ring 30.

[0134] Optionally, the mounting slot 231 and the scraper ring 30 are positioned to correspond to the hammer ball groove of the hammer 23.

[0135] Optionally, the scraper ring 30 may be provided with a lip 32.

[0136] Furthermore, in a cross section passing through the axis of the fixing part 31, the angle between the outer wall 321 of the lip 32 and the inner wall of the first cavity 11 ranges from 15° to 85°.

[0137] Furthermore, both the inner wall 322 and the outer wall 321 of the lip 32 are straight, and the angle between the outer wall 321 and the inner wall 322 of the lip 32 is between 5° and 12°.

[0138] Furthermore, the thickness of the end of the lip 32 is less than the thickness of the root of the lip 32.

[0139] Furthermore, the connection between the outer wall 321 of the lip 32 and the inner wall 322 of the lip 32 is smoothly transitioned.

[0140] Furthermore, the scraper ring 30 is integrally molded, or is a one-piece structure made of elastic material.

[0141] Furthermore, the lip 32 or scraping ring 30 is made entirely of fluororubber, perfluoroether rubber, fluorosilicone rubber, hydrogenated nitrile rubber, or high-temperature silicone rubber.

[0142] It should be added that the basic working principle of the impact assembly is as follows: The drive unit 21 uses a combination of a motor and a planetary reducer to output power outward and transmit it to the drive shaft 22. The drive shaft 22 is driven to output torque and rotation outward. The drive shaft 22 drives the hammer 23 to rotate through the hammer ball groove and the steel ball between the drive shaft ball groove. The end of the hammer 23 away from the drive unit 21 is connected to the striking shaft 24, forming a whole. The side away from the drive unit 21 is provided with a striking surface. When the striking shaft 24 and the hammer 23 collide with the striking surface, the rotation of the hammer 23 is hindered. At this time, the hammer 23 drives the transmission steel ball to move axially backward along the axis of the hammer ball groove and the drive shaft ball groove, overcoming the spring force, until the striking surface jumps, and the striking shaft 24 and the striking surface are completely misaligned. Subsequently, the drive shaft 22 continues to rotate, and through the drive steel ball, drives the hammer 23 to rotate. Under the action of the spring and the drive steel ball, the hammer 23 and the striking shaft 24 move forward along their axis and approach the striking surface until the striking shaft 24 and the hammer 23 collide with the striking surface. This reciprocating motion of the hammer 23 and the striking shaft 24 is achieved.

[0143] Please see Figure 1 According to another aspect of this application, an impact device is provided, which includes the impact components as described above.

[0144] This impact device, through the directional control and structural adaptation of the scraper ring in the impact assembly, can effectively concentrate the lubricating material on the impact surface, ensuring sufficient lubrication in the core working area. This significantly reduces problems such as component wear, deformation, and abnormal noise caused by lubrication failure, and significantly improves the stability and reliability of the equipment operation.

[0145] The efficient lubrication mechanism of the impact components extends the service life of the equipment, reduces the probability of failure under high-frequency operation, lowers the frequency and cost of maintenance and replacement of parts, and improves the continuous working capability of the equipment. It is especially suitable for high-frequency use scenarios such as industrial assembly and home repair.

[0146] The equipment operates more smoothly, with fewer instances of jamming and reduced efficiency due to insufficient lubrication, making operation more convenient. At the same time, the directional aggregation of lubricating materials reduces unnecessary loss, lowers the frequency of grease replenishment, reduces the maintenance burden, and lowers the overall operating cost of the equipment.

[0147] The various structural designs of the aforementioned impact components (such as different schemes for the position and shape of the scraper ring) can be flexibly adapted to different models of impact equipment, enabling the equipment to maintain excellent performance under design requirements such as miniaturization and high frequency, and providing strong support for the technological upgrading and application expansion of impact equipment.

[0148] For details on the specific structure and beneficial effects of the impact component, please refer to the above embodiments, which will not be repeated here.

[0149] Specifically, impact equipment can be impact wrenches, impact drills, impact screwdrivers, impact hammers, etc.

[0150] It should be understood that this application is not limited to the detailed structure and arrangement of the components proposed in this application. This application can have other embodiments and can be implemented and executed in various ways. The foregoing variations and modifications fall within the scope of this application. It should be understood that the disclosure and definition of this application extends to all alternative combinations of two or more individual features mentioned or apparent in the text and / or drawings. All these different combinations constitute multiple alternative aspects of this application. The embodiments described in this application illustrate the best known mode for implementing this application and will enable those skilled in the art to utilize this application.

Claims

1. An impact assembly, characterized in that, include: A housing having a first cavity; An impact structure is disposed in the first cavity. The impact structure includes a driving member, a transmission shaft and a hammer. The hammer is sleeved on one end of the transmission shaft. The output end of the driving member is connected to the other end of the transmission shaft. A channel for lubricant to pass through is formed between the outer wall of the hammer and the inner wall of the first cavity. A scraper ring is fixedly connected to the hammer and is arranged in a ring between the outer wall of the hammer and the inner wall of the housing. The driving component drives the transmission shaft to rotate, causing the hammer to slide back and forth along the axis of the transmission shaft. As the hammer approaches the driving component, the scraper ring separates from the inner wall of the first cavity. As the hammer moves away from the driving component, the scraper ring abuts against the inner wall of the first cavity.

2. The impact assembly according to claim 1, characterized in that, The hammer is provided with a mounting groove, and the scraper ring is embedded in the mounting groove.

3. The impact assembly according to claim 2, characterized in that, The impact assembly includes a transmission steel ball, the hammer has a hollow second cavity, the inner wall of the second cavity has a hammer ball groove, the transmission shaft is located in the second cavity, and a transmission shaft ball groove is provided on its radial outer side, the transmission steel ball is slidably located in both the hammer ball groove and the transmission shaft ball groove, and the mounting groove is provided on the radial outer side of the hammer corresponding to the hammer ball groove.

4. The impact assembly according to claim 2, characterized in that, Along the axial direction of the hammer, the mounting groove divides the hammer into a first segment and a second segment. The second segment is positioned closer to the drive member than the first segment. The ratio of the axial length of the first segment to the axial length of the second segment is i, where 0 < i ≤ 0.15, or 0.8 ≤ i ≤ 9.

3.

5. The impact assembly according to claim 1, characterized in that, The scraper ring includes a fixing part and a lip. The fixing part has an annular structure and is fixed around the radial outer surface of the hammer. The lip is connected to the radial outer surface of the fixing part. In the axial direction of the fixing part, the diameter of the outer wall surface of the lip near the end of the driving member is smaller than the diameter away from the end of the driving member.

6. The impact assembly according to claim 5, characterized in that, On a cross section passing through the axis of the fixing part, the outer wall of the lip is straight, and the angle between the outer wall of the lip and the outer wall of the fixing part is α, where 15°≤α≤85°.

7. The impact assembly according to claim 5, characterized in that, On a cross section passing through the axis of the fixed part, the inner wall of the lip is straight or smooth curved, and a separation gap is formed between it and the outer wall of the fixed part. The separation gap gradually increases along the direction away from the driving member along the axis of the transmission shaft.

8. The impact assembly according to claim 7, characterized in that, On a cross section passing through the axis of the fixing part, both the inner and outer walls of the lip are straight, and the angle between the outer and inner walls of the lip is β, where 5°≤β≤12°.

9. An impact assembly, characterized in that, include: A housing having a first cavity; An impact structure is disposed in the first cavity. The impact structure includes a driving member, a transmission shaft and a hammer. The hammer is sleeved on one end of the transmission shaft. The output end of the driving member is fixedly connected to the other end of the transmission shaft. A channel for lubricant to pass through is formed between the outer wall of the hammer and the first cavity. A scraping ring is arranged around the hammer and fixed to the inner wall of the first cavity; The driving member drives the transmission shaft to rotate, so that the hammer slides back and forth along the axis of the transmission shaft. The diameter of the scraper ring at the end near the driving member is larger than the diameter at the end away from the driving member. When the hammer moves closer to the driving member, the scraper ring abuts against the outer wall of the hammer. When the hammer moves away from the driving member, the scraper ring separates from the outer wall of the hammer.

10. An impact device, characterized in that, The impact device includes an impact component as described in any one of claims 1 to 9.

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