WO2024008144A1 - 电锤 - Google Patents

电锤 Download PDF

Info

Publication number
WO2024008144A1
WO2024008144A1 PCT/CN2023/106056 CN2023106056W WO2024008144A1 WO 2024008144 A1 WO2024008144 A1 WO 2024008144A1 CN 2023106056 W CN2023106056 W CN 2023106056W WO 2024008144 A1 WO2024008144 A1 WO 2024008144A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
reciprocating
impact
guide rail
power source
Prior art date
Application number
PCT/CN2023/106056
Other languages
English (en)
French (fr)
Inventor
傅珂珂
李进
Original Assignee
浙江千机智能科技有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 浙江千机智能科技有限公司 filed Critical 浙江千机智能科技有限公司
Publication of WO2024008144A1 publication Critical patent/WO2024008144A1/zh

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools

Definitions

  • the present application relates to the technical field of electric tools, and in particular to an electric hammer.
  • the principle of the electric hammer is that the transmission mechanism drives the drill bit to rotate and at the same time controls the drill bit to make reciprocating hammering movements.
  • the motor drives the piston through the transmission mechanism to reciprocate the compressed air in the cylinder, and at the same time drives the drill bit to rotate through the transmission mechanism.
  • the traditional electric hammer needs to drive both the drill bit to rotate and the hammer to reciprocate, resulting in unstable transmission and affecting the use of the electric hammer; on the other hand, the traditional electric hammer is inconvenient to adjust the hammer-to-drill ratio of the electric hammer, and thus Affect the effect of use.
  • an electric hammer is provided.
  • the electric hammer includes a moving component, an impact component, and a rotating component.
  • the moving component includes a cylinder, a moving unit, and a first power source.
  • the moving unit is connected to the cylinder.
  • the first power source is used to drive the cylinder to reciprocate through the moving unit;
  • the impact assembly includes a ram, which is installed in the cylinder and is in sealing contact with the inner wall of the cylinder.
  • a rotating component the rotating component includes a rotating sleeve and a second power source, The cylinder is passed through the rotating sleeve, the impact component is provided in the rotating sleeve, and the second power source is used to drive the rotating sleeve to rotate relative to the cylinder.
  • Figure 1 is a schematic structural diagram of an electric hammer in an embodiment
  • Figure 2 is a cross-sectional view of the electric hammer shown in Figure 1;
  • Figure 3 is a schematic structural diagram of the rotating sleeve in Figure 2;
  • Figure 4 is a partially exploded view of the mobile assembly in Figure 2 with the first power source omitted;
  • Figure 5 is a schematic structural diagram of the cylinder in Figure 4.
  • FIG. 6 is a cross-sectional view of the cylinder shown in FIG. 5 .
  • the electric hammer 10 in one embodiment of the present invention can at least ensure the stability of the transmission, and can easily adjust the hammer-to-drill ratio to improve the use effect.
  • the electric hammer 10 includes a moving component 100, an impact component 200 and a rotating component 300.
  • the moving component 100 includes a cylinder 110, a moving unit 120 and a first power source 130.
  • the moving unit 120 is connected to the cylinder 110.
  • the first The power source 130 is used to drive the cylinder 110 to reciprocate through the moving unit 120;
  • the impact assembly 200 includes a ram 210, which is disposed in the cylinder 110 and is in sealing contact with the inner wall of the cylinder 110, so that the ram 210 is in contact with the inner wall of the cylinder 110.
  • a sealed impact chamber 111 is formed between the inner walls of the cylinder 110, and the ram 210 can move back and forth in the cylinder 110;
  • the rotating assembly 300 includes a rotating sleeve 310 and a second power source 320.
  • the cylinder 110 is penetrated in the rotating sleeve 310.
  • the assembly 200 is disposed in the rotating sleeve 310 , and the second power source 320 is used to drive the rotating sleeve 310 to rotate relative to the cylinder 110 .
  • the above-mentioned electric hammer 10 and ram 210 are installed in the cylinder 110 and form a sealed impact chamber 111.
  • the first moving When the force source 130 drives the cylinder 110 to reciprocate through the moving unit 120, the cylinder 110 moves relative to the ram 210 to compress the air in the impact chamber 111, and then uses the compressed air to impact the ram 210 to achieve reciprocating impact of the ram 210. sports.
  • the drill bit is arranged on the rotating sleeve 310.
  • the second power source 320 drives the rotating sleeve 310 to drive the drill bit to rotate relative to the cylinder 110.
  • the impact assembly 200 is arranged in the rotating sleeve 310, and the hammer 210 is used to impact the drill bit.
  • the above-mentioned electric hammer 10 realizes the impact movement of the drill bit through the cooperation of the first power source 130, the moving unit 120 and the cylinder 110, and realizes the rotation of the drill bit through the second power source 320 and the rotating sleeve 310.
  • the cylinder 110 and the punch The hammer 210 does not need to rotate synchronously to realize the separation of impact drive and rotation drive, ensuring the stability of the impact motion and rotation motion drive of the drill bit; on the other hand, the first power source 130 and the second power source 320 respectively drive the drill bit to achieve impact. Movement and rotation are convenient for adjusting the impact speed and rotation speed respectively, and are convenient for adjusting the hammer-drill ratio of the electric hammer 10, which is beneficial to improving the use effect of the electric hammer 10.
  • the first power source 130 is arranged in the direction of the rotation axis of the rotating sleeve 310 and is located on a side of the cylinder 110 facing away from the rotating sleeve 310; the second power source 320 is arranged on one side of the outer wall of the rotating sleeve 310. side.
  • the first power source 130 is a motor.
  • the second power source 320 is a motor.
  • the rotating assembly 300 further includes a transmission unit 330.
  • the transmission unit 330 is connected to the outer wall of the rotating sleeve 310.
  • the second power source 320 is used to drive the rotating sleeve 310 to rotate through the transmission unit 330.
  • the transmission unit 330 is provided to facilitate the transmission connection between the second power source 320 and the rotating sleeve 310 .
  • the transmission unit 330 includes a first bevel gear 332 and a second bevel gear 334.
  • the first bevel gear 332 is sleeved on the outer wall of the rotating sleeve 310.
  • the second bevel gear 334 and the first bevel gear 332 are meshed, and the second power source 320 is used for the second bevel gear 334 to rotate. Since the second power source 320 is arranged on one side of the outer wall of the rotating sleeve 310, the first bevel gear 332 and the second bevel gear 334 are provided to facilitate the rotational connection between the second power source 320 and the rotating sleeve 310.
  • the transmission unit 330 may further include two gears that mesh with each other, one gear is sleeved on the outer wall of the rotating sleeve 310 , and the other gear is connected to the second power source 320 .
  • the transmission unit 330 can also be other transmission structures, as long as it is convenient to realize the transmission connection between the rotating sleeve 310 and the second power source 320 and realize the purpose of the second power source 320 being able to drive the rotating sleeve 310 to rotate. .
  • the cylinder 110 includes an impact cylinder part 113 and a moving cylinder part 114 connected to the impact cylinder part 113.
  • the moving unit 120 is connected to the moving cylinder part 114; the ram 210 is inserted through In the impact cylinder part 113, the impact The cylinder part 113 is inserted into the rotating sleeve 310; the moving cylinder part 114 is located outside the rotating sleeve 310, and the moving unit 120 is connected to the moving cylinder part 114.
  • a sealed impact chamber 111 is formed between the ram 210 and the inner wall of the impact cylinder portion 113, and the connection positions of the impact cylinder portion 113 and the moving cylinder portion 114 are separated and connected by partitions, so that To form a sealed impact chamber 111. Furthermore, the impact cylinder portion 113 has an opening on a side facing away from the moving cylinder portion 114 , and the hammer 210 can be inserted into the impact cylinder portion 113 through the opening of the impact cylinder portion 113 .
  • the diameter of the outer wall of the impact cylinder portion 113 is consistent with the diameter of the corresponding inner wall of the rotating sleeve 310 . Since the impact cylinder part 113 can reciprocate within the rotating sleeve 310 , by setting the diameter of the outer wall of the impact cylinder part 113 to be consistent with the diameter of the inner wall of the rotating sleeve 310 , the stability of the moving direction of the impact cylinder part 113 can be further ensured.
  • the outer wall of the rotating sleeve 310 is provided with an air inlet hole 312 and an exhaust hole 314.
  • the air inlet hole 312 and the exhaust hole 314 are spaced apart along the axis of the rotating sleeve 310.
  • the cylinder part 113 moves back and forth in the rotating sleeve 310 to the maximum stroke, it covers the air inlet hole 312.
  • the ram 210 does not cover the air inlet hole 312, and the impact cylinder part 113 does not cover the air inlet hole 312 during the reciprocating movement.
  • Cover vent 314. Stable movement of the punch 210 in the rotating sleeve 310 is achieved through the air inlet hole 312 and the exhaust hole 314 to avoid being affected by air pressure and affecting the impact motion of the punch 210.
  • the moving unit 120 includes a reciprocating shaft 121 and a moving body 122.
  • the reciprocating shaft 121 is provided with a reciprocating guide rail.
  • the reciprocating guide rail is a closed curved guide rail surrounding the axis of the reciprocating shaft 121, and the curve is The wave peaks and wave troughs of the guide rail are spaced along the axis of the reciprocating shaft 121; the moving body 122 is limited to the cylinder 110 and can move on the reciprocating guide rail; the first power source 130 is used to drive the reciprocating shaft 121 to rotate, so that the moving body 122 The cylinder 110 is driven to reciprocate along the axial direction of the reciprocating shaft 121 .
  • the first power source 130 drives the reciprocating shaft 121 to rotate.
  • the moving body 122 can move on the reciprocating guide rail, so that the moving body 122 can move between the wave peaks and the wave troughs of the curved guide rail, so as to realize the moving body 122 reciprocating along the axis direction of the reciprocating shaft 121
  • the purpose of movement is to drive the cylinder 110 to achieve the purpose of reciprocating along the axial direction of the reciprocating shaft 121 .
  • the reciprocating guide rail is a reciprocating groove 123.
  • the reciprocating groove 123 is a closed curved groove surrounding the axis of the reciprocating shaft 121, and the wave peaks and troughs of the curved groove are spaced along the axis of the reciprocating shaft 121; the moving body 122 It is penetrated in the reciprocating groove 123 and can move in the reciprocating groove 123 .
  • the moving body 122 is a sphere, and the sphere can roll in the reciprocating groove 123 .
  • crank structure and the eccentric drive structure need to realize the transformation of the reciprocating movement through swinging, and thus there is a deflection angle and a deflection.
  • the problem of work due to force friction leads to poor stability of work.
  • the rotational motion of the reciprocating shaft 121 of the mobile unit 120 of the present application is converted into the linear motion of the cylinder 110, without any yaw intersection, which results in better performance stability and is conducive to miniaturization design.
  • the reciprocating guide rail is a guide protrusion
  • the guide protrusion is a closed strip-shaped curved protrusion surrounding the axis of the reciprocating shaft 121, and the peaks and troughs of the curved protrusion are spaced apart along the axis of the reciprocating shaft 121; move
  • the body 122 is disposed on the guide protrusion and can move along the length direction on the guide protrusion.
  • each reciprocating guide rail is spaced along the axis of the reciprocating shaft 121 , and at least one moving body 122 is provided on each reciprocating guide rail.
  • the two moving bodies 122 are evenly spaced around the axis of the reciprocating shaft 121 , and the two moving bodies 122 can move synchronously during reciprocating movement.
  • the stability of the movement of the cylinder 110 can be further improved and the stability of the force of the cylinder 110 can be ensured.
  • the reciprocating shaft 121 is also provided with a balance guide rail that is spaced opposite to the reciprocating guide rail along the axis of the reciprocating shaft 121.
  • the balance guide rail is a closed curve guide rail surrounding the axis of the reciprocating shaft 121, and the wave crest of the balance guide rail is The wave troughs are arranged at intervals along the axis of the reciprocating shaft 121; and the wave crests of the balance guide rail are opposite to the wave troughs of the reciprocating guide rail along the axial direction, and the wave troughs of the balance guide rail are opposite to the wave crests of the reciprocating guide rail along the axial direction.
  • a balance body is provided on the balance guide rail.
  • the balance body and the moving body 122 are arranged oppositely along the axis of the reciprocating shaft 121. When the reciprocating shaft 121 rotates, the balance body and the moving body 122 move toward or away from each other. By arranging the balance guide rail and the balance body, the two-way acceleration during the movement of the balance body and the moving body 122 can be offset, thereby reducing the vibration caused by acceleration.
  • the balance guide rail has the same structure as the reciprocating guide rail, and the balance guide rail is symmetrically arranged along the circumference of the power shaft relative to the reciprocating guide rail.
  • the balance body and the moving body 122 have the same structure.
  • an accommodating cavity 115 is formed in the moving cylinder portion 114 of the cylinder 110, the reciprocating shaft 121 is disposed in the accommodating cavity 115, and the accommodating cavity 115
  • a limiting groove 116 is formed on the inner wall, and the moving body 122 is limited between the inner wall of the limiting groove 116 and the inner wall of the reciprocating groove 123 .
  • part of the moving body 122 is disposed in the limiting groove 116 , and the remaining part is disposed in the reciprocating groove 123 .
  • the rotation of the reciprocating shaft 121 occurs in the accommodating cavity 115, and the moving body 122 is limited between the reciprocating groove 123 and the limiting groove 116, ensuring that the moving body 122
  • the stability of the limit ensures the stability of the movement of the cylinder 110 driven by the moving body 122.
  • the accommodation cavity 115 passes through the side of the moving cylinder portion 114 facing away from the impact cylinder portion 113 , so that the reciprocating shaft 121 can be inserted through the side of the moving cylinder portion 114 facing away from the impact cylinder portion 113 . in the accommodation cavity 115.
  • the moving assembly 100 further includes a rolling limiter 140.
  • the rolling limiter 140 is disposed in the limit groove 116.
  • the moving body 122 is a sphere, and the sphere is rollably disposed between the rolling limiter 140 and the reciprocating groove 123. between inner walls.
  • the rolling limiting member 140 prevents the moving body 122 from directly rolling and rubbing against the inner wall of the limiting groove 116 .
  • a hemispherical groove is formed in the rolling stopper 140, and the moving body 122 is disposed in the hemispherical groove and can roll.
  • the moving cylinder part 114 of the cylinder 110 includes a first splicing part 117 and a second splicing part 118.
  • the first splicing part 117 is connected to the impact cylinder part 113, and a first splicing cavity is formed in the first splicing part 117. 1172.
  • a first splicing groove 1174 is formed on the inner wall of the first splicing cavity 1172 and is open on one side facing away from the impact cylinder part 113.
  • a second splicing cavity 1182 is formed in the second splicing part 118.
  • the second splicing cavity 1182 is A second splicing groove 1184 is formed on the inner wall, and one side of the second splicing part 118 is open; the opening side of the second splicing part 118 is connected with the opening side of the first splicing part 117, so that the first splicing cavity 1172 is connected with the second splicing part 117.
  • the cavities 1182 are correspondingly connected to form the accommodation cavity 115
  • the first splicing groove 1174 and the second splicing groove 1184 are correspondingly connected to form the limiting groove 116 .
  • the first splicing part 117 and the second splicing part 118 can facilitate the installation of the moving body 122 in the limiting groove 116. It is ensured that the moving body 122 is effectively limited in the limiting groove 116 .
  • the first splicing part 117 is integrally formed on the impact cylinder part 113 .
  • first splicing part 117 and the second splicing part 118 are welded and connected. In other embodiments, the first splicing part 117 and the second splicing part 118 may also be connected by screws or snapped together.
  • the moving assembly 100 also includes a guide rod 150.
  • the guide rod 150 is located outside the rotating sleeve 310.
  • a matching structure 112 is formed on the outer wall of the cylinder 110.
  • the guide rod 150 guides the matching structure 112.
  • the length direction of the guide rod 150 is the axis direction of the reciprocating shaft 121 .
  • the stability of the reciprocating movement of the cylinder 110 is further ensured by arranging the guide rod 150 to guide and cooperate with the matching structure 112 .
  • the matching structure 112 is a sleeve-shaped structure, and the guide rod 150 is inserted into the sleeve-shaped matching structure 112 .
  • the matching structure 112 is formed on the outer wall of the moving cylinder portion 114 .
  • the number of guide rods 150 is at least two. Each guide rod 150 is spaced around the axis of the reciprocating shaft 121 . Each guide rod 150 is guide-connected to the cylinder 110 through a matching structure 112 . By providing at least two guide rods 150, the stability of the movement of the cylinder 110 can be further improved. Specifically, each guide rod 150 is evenly arranged around the cylinder 110 . In this embodiment, the number of guide rods 150 is two. In other embodiments, the number of guide rods 150 may also be three, four, or other numbers.
  • a part is formed on the outer wall of the first splicing part 117, and the other part is formed on the outer wall of the second splicing part 118.
  • the first splicing part 117 and the second splicing part 118 are spliced together to form the matching structure 112 by splicing the two parts. Since the guide rod 150 guides and cooperates with the matching structure 112, by forming partial matching structures 112 in both the first splicing part 117 and the second splicing part 118, the guide rod 150 can be matched with the first splicing part 117 and the second splicing part 118.
  • the second splicing parts 118 all produce guide fits.
  • the matching structure 112 may be formed solely on the first splicing part 117 or separately on the second splicing part 118 .
  • the impact assembly 200 further includes an impact rod 220 , and the impact rod 220 is located on a side of the ram 210 facing away from the cylinder 110 .
  • the punch 210 can impact the drill bit in the rotating sleeve 310 through the impact rod 220 .
  • the electric hammer 1010 further includes a protective shell (not shown).
  • the moving component 100 and the rotating component 300 are both disposed in the protective shell.
  • the moving component 100 and the rotating component 300 are protected by the protective shell.
  • a lubricating oil chamber is formed in the protective shell, and the transmission unit 330 and the moving unit 120 are both located in the lubricating oil chamber.
  • the motor speed will decrease as the drilling depth load of the drill bit increases, causing the hammering speed to also decrease.
  • the above-mentioned electric hammer 10 can avoid this through the first power source 130 and the second power source 320 Even if the rotation speed decreases, the hammering speed can be maintained, thereby improving the use effect of the electric hammer 10 .
  • first and second are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise clearly and specifically limited.
  • the first feature "on” or “below” the second feature may be that the first and second features are in direct contact, or the first and second features are in direct contact through an intermediate medium. indirect contact.
  • the terms “above”, “above” and “above” the first feature is above the second feature may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is higher in level than the second feature.
  • "Below”, “below” and “beneath” the first feature to the second feature may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature has a smaller horizontal height than the second feature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)

Abstract

一种电锤(10)，包括移动组件(100)、冲击组件(200)及旋转组件(300)，移动组件(100)包括缸体(110)、移动单元(120)及第一动力源(130)，冲击组件(200)包括冲锤(210)，旋转组件(300)包括转动套(310)及第二动力源(320)。冲锤(210)穿设于缸体(110)内，并形成密封的冲击腔(111)，第一动力源(130)通过移动单元(120)驱动缸体(110)往复移动，压缩冲击腔(111)内的空气，实现冲锤(210)的往复冲击运动。第二动力源(320)驱动转动套(310)相对于缸体(110)带动钻头转动，而冲击组件(200)设置于转动套(310)内，利用冲锤(210)实现对钻头的冲击作用。一方面，该电锤(10)的缸体(110)和冲锤(210)不需要同步转动，实现冲击驱动及转动驱动的分离，保证对冲击运动及旋转运动驱动的稳定性；另一方面，第一动力源(130)与第二动力源(320)分别驱动钻头实现冲击运动和转动，便于调节电锤(10)的锤钻比，有利于提高电锤(10)的使用效果。

Description

电锤
相关申请
本申请要求2022年07月06日申请的，申请号为202221725426.X，名称为“电锤”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请涉及用于电动工具技术领域，特别是涉及一种电锤。
背景技术
电锤原理是传动机构在带动钻头做旋转运动的同时，控制钻头做往复锤击的运动。传统的电锤工作时，电机通过传动机构带动活塞在汽缸内往复压缩空气的同时，通过传动结构驱动钻头做旋转运动。一方面传统的电锤由于即需要驱动钻头转动，又需要驱动冲锤往复运动，导致传动不稳定，影响电锤的使用；另一方面传统的电锤不便于调节电锤的锤钻比，进而影响使用的效果。
发明内容
根据本申请的实施例，提供一种电锤。
本申请提供一种电锤，所述电锤包括移动组件、冲击组件及旋转组件，所述移动组件包括缸体、移动单元及第一动力源，所述移动单元连接于所述缸体，所述第一动力源用于通过所述移动单元驱动所述缸体往复移动；所述冲击组件包括冲锤，所述冲锤穿设于所述缸体内，并与所述缸体内壁密封接触，以使所述冲锤与所述缸体内壁之间形成密封冲击腔，所述冲锤能够在所述缸体内往复移动；旋转组件，所述旋转组件包括转动套及第二动力源，所述缸体穿设于所述转动套内，所述冲击组件设置于所述转动套内，所述第二动力源用于驱动所述转动套相对于所述缸体转动。
附图说明
为了更清楚地说明本申请实施例或传统技术中的技术方案，下面将对实施例或传统技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据公开的附图获得其他的附图。
图1为一实施例中的电锤的结构示意图；
图2为图1所示的电锤的剖视图；
图3为图2中转动套的结构示意图；
图4为图2中的移动组件省略第一动力源的局部分解图；
图5为图4中的缸体的结构示意图；
图6为图5所示的缸体的剖视图。
附图标号说明：
10、电锤；100、移动组件；110、缸体；111、冲击腔；112、配合结构；113、冲击缸部；114、移动缸部；115、容置腔；116、限位槽；117、第一拼接部；1172、第一拼接腔；1174、第一拼接槽；118、第二拼接部；1182、第二拼接腔；1184、第二拼接槽；120、移动单元；121、往复轴；122、移动体；130、第一动力源；140、滚动限位件；150、导向杆；
200、冲击组件；210、冲锤；220、冲击杆；
300、旋转组件；310、转动套；312、进气孔；314、排气孔；320、第二动力源；330、传动单元；332、第一锥齿轮；334、第二锥齿轮。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
参阅图1及图2，本实用新型一实施例中的电锤10，至少能够保证传动的稳定性，且便于调节锤钻比，提高使用效果。具体地，电锤10包括移动组件100、冲击组件200及旋转组件300，移动组件100包括缸体110、移动单元120及第一动力源130，移动单元120连接于所述缸体110，第一动力源130用于通过移动单元120驱动缸体110往复移动；冲击组件200包括冲锤210，冲锤210穿设于缸体110内，并与缸体110内壁密封接触，以使冲锤210与缸体110内壁之间形成密封冲击腔111，冲锤210能够在缸体110内往复移动；旋转组件300包括转动套310及第二动力源320，缸体110穿设于转动套310内，冲击组件200设置于转动套310内，第二动力源320用于驱动转动套310相对于缸体110转动。
上述电锤10，冲锤210穿设于缸体110内，并形成密封的冲击腔111，进而当第一动 力源130通过移动单元120驱动缸体110往复移动时，缸体110相对于冲锤210移动，以压缩冲击腔111内的空气，进而利用压缩空气冲击冲锤210，实现冲锤210的往复冲击运动。同时，钻头设置于转动套310上，第二动力源320驱动转动套310相对于缸体110带动钻头转动，而冲击组件200设置于转动套310内，进而利用冲锤210实现对钻头的冲击作用，实现钻头在旋转运动的过程中做往复冲击运动。上述电锤10实现钻头冲击运动通过第一动力源130、移动单元120与缸体110的配合实现，而实现钻头的转动通过第二动力源320与转动套310实现，一方面缸体110和冲锤210不需要同步转动，实现冲击驱动及转动驱动的分离，保证对钻头的冲击运动及旋转运动驱动的稳定性；另一方面，第一动力源130与第二动力源320分别驱动钻头实现冲击运动和转动，便于分别调节冲击速度及转动速度，便于调节电锤10的锤钻比，有利于提高电锤10的使用效果。
一实施例中，第一动力源130设置于转动套310的转动轴线方向上，并位于缸体110背向于转动套310的一侧；第二动力源320设置于转动套310的外壁的一侧。通过将第一动力源130布置在转动套310的轴线上，第二动力源320布置在转动套310外壁的一侧，不仅便于第一动力源130与第二动力源320分别驱动移动单元120及转动套310，且便于实现电锤10的小型化。
在本实施例中，第一动力源130为电机。第二动力源320为电机。
一实施例中，旋转组件300还包括传动单元330，传动单元330与转动套310的外壁相连接，第二动力源320用于通过传动单元330驱动转动套310转动。通过设置传动单元330便于实现第二动力源320与转动套310的传动连接。
一并参阅图3，具体地，传动单元330包括第一锥齿轮332及第二锥齿轮334，第一锥齿轮332套设于转动套310的外壁上，第二锥齿轮334与第一锥齿轮332相啮合，第二动力源320用于第二锥齿轮334转动。由于第二动力源320布置在转动套310外壁的一侧，通过设置第一锥齿轮332及第二锥齿轮334便于实现第二动力源320与转动套310的转动连接。
在另一实施例中，传动单元330还可以包括两个相互啮合的齿轮，一齿轮套设于转动套310的外壁上，另一齿轮与第二动力源320连接。
或者，在其他实施例中，传动单元330还可以为其他传动结构，只要便于实现转动套310与第二动力源320的传动连接，实现第二动力源320能够驱动转动套310转动的目的即可。
参阅图2及图4，一实施例中，缸体110包括冲击缸部113及与冲击缸部113相连接的移动缸部114，移动单元120连接于移动缸部114；冲锤210穿设于冲击缸部113内，冲 击缸部113穿设于转动套310内；移动缸部114位于转动套310外，移动单元120连接于移动缸部114。通过将移动缸部114与移动单元120设置于转动套310外，便于保证移动单元120带动移动缸部114往复移动的稳定，且避免影响转动套310驱动钻头转动的稳定性。
一并参阅图5及图6，具体地，冲锤210与冲击缸部113的内壁之间形成密封冲击腔111，进而冲击缸部113与移动缸部114的连接位置通过隔板分隔连接，以便于形成密封的冲击腔111。进一步地，冲击缸部113背向于移动缸部114的一侧开口，冲锤210能够由冲击缸部113的开口穿设于冲击缸部113内。
在本实施例中，冲击缸部113外壁的直径与对应的转动套310内壁的直径一致。由于冲击缸部113能够在转动套310内往复移动，通过将冲击缸部113外壁的直径与转动套310内壁的直径设置为一致的，能够进一步保证冲击缸部113移动的方向的稳定。
再次一并参阅图3，一实施例中，转动套310的外壁上开设有进气孔312及排气孔314，进气孔312与排气孔314沿着转动套310的轴线间隔布置，冲击缸部113在转动套310内往复移动至最大行程时，覆盖进气孔312，移动至最小行程时，冲锤210不覆盖进气孔312，而冲击缸部113在往复移动的过程中不会覆盖排气孔314。通过进气孔312与排气孔314实现冲锤210在转动套310内的稳定移动，避免受到气压影响而影响冲锤210的冲击运动。
参阅图2及图4，一实施例中，移动单元120包括往复轴121及移动体122，往复轴121上设置有往复导轨，往复导轨为环绕往复轴121轴线的闭合曲线形导轨，且曲线形导轨的波峰与波谷沿往复轴121的轴线间隔设置；移动体122限位于缸体110上，并能够在往复导轨上移动；第一动力源130用于驱动往复轴121转动，以使移动体122带动缸体110沿往复轴121的轴线方向往复移动。
在本实施例中，第一动力源130驱动往复轴121转动。往复轴121转动时，移动体122能够在往复导轨上移动，进而使得移动体122能够在呈曲线形导轨的波峰与波谷之间的运动，以实现移动体122沿着往复轴121的轴线方向往复移动的目的，进而带动缸体110实现沿着往复轴121的轴线方向往复移动的目的。
在本实施例中，所述往复导轨为往复槽123，往复槽123为环绕往复轴121轴线的闭合曲线形槽，且曲线形槽的波峰与波谷沿往复轴121的轴线间隔设置；移动体122穿设于往复槽123内并能够在往复槽123内移动。
在本实施例中，移动体122为球体，球体在往复槽123内可滚动。
上述移动单元120相比于通过曲柄结构或偏心驱动结构实现缸体110的往复移动，曲柄结构和偏心驱动结构因需要通过摆动实现往复移动的转化，进而存在偏摆角，存在偏向 力摩擦做功的问题，导致做功稳定性差。而本申请的移动单元120的往复轴121的旋转运动转化为缸体110的直线运动，不会出现偏摆交，做功稳定性更好，同时有利于小型化设计。
另一实施例中，往复导轨为导向凸起，导向凸起为环绕往复轴121轴线的闭合条状曲线形凸起，且曲线形凸起的波峰与波谷沿往复轴121的轴线间隔设置；移动体122设置于导向凸起上并能够在导向凸起上沿长度方向移动。
一实施例中，往复导轨为至少两个，各个往复导轨沿着往复轴121的轴线间隔设置，每一往复导轨上均设置有至少一移动体122。通过设置至少两个往复导轨，能够提高移动体122带动缸体110移动的稳定性。
一实施例中，每一往复导轨上设置有的移动体122可以为两个，两个移动体122绕往复轴121的轴线均匀间隔设置，且两个移动体122能够在往复移动时同步移动。通过两个移动体122同步移动带动缸体110移动，能够进一步提高缸体110移动的稳定性，且保证缸体110受力的稳定。在其他实施例中，移动体122还可以为一个。或者移动体122还可以为其他数目个，各个移动体122能够同方向同步移动。
在另一实施例中，往复轴121上还设置有与往复导轨沿往复轴121轴线间隔相对设置的平衡导轨，平衡导轨为环绕往复轴121轴线的闭合曲线形导轨，且所述平衡导轨的波峰与波谷沿往复轴121的轴线间隔设置；且所述平衡导轨的波峰沿轴线方向与往复导轨的波谷相对，所述平衡导轨的波谷沿轴线方向与往复导轨的波峰相对。平衡导轨上设置有平衡体，平衡体与移动体122沿往复轴121的轴线相对设置，进而往复轴121转动时，平衡体与移动体122相向或相背移动。通过设置平衡导轨与平衡体，能够使得平衡体与移动体122移动过程双向加速度抵消，减少加速度产生的振动。
具体地，平衡导轨与往复导轨的结构一致，平衡导轨相对于往复导轨沿动力轴的周线对称设置。在本实施例中，平衡体与移动体122结构一致。
一并参阅图4、图5及图6，一实施例中，缸体110的移动缸部114内形成有容置腔115，往复轴121穿设于容置腔115内，且容置腔115的内壁上形成有限位槽116，移动体122限位于限位槽116内壁与往复槽123内壁之间。具体地，移动体122部分设置于限位槽116内，其余部分设置于往复槽123内。通过将往复轴121穿设于容置腔115内，使得往复轴121的转动发生在容置腔115内，且移动体122限位在往复槽123与限位槽116之间，保证移动体122限位的稳定，保证移动体122带动缸体110移动的稳定。
在本实施例中，容置腔115贯穿移动缸部114背向于冲击缸部113的一侧，以使往复轴121能够由移动缸部114背向于冲击缸部113的一侧穿设于容置腔115内。
一实施例中，移动组件100还包括滚动限位件140，滚动限位件140设置于限位槽116内，移动体122为球体，球体可滚动地设置于滚动限位件140与往复槽123内壁之间。通过滚动限位件140避免移动体122直接与限位槽116的内壁滚动摩擦。具体地，滚动限位件140内形成有半球形的凹槽，移动体122设置于半球形的凹槽内并可滚动。
一实施例中，缸体110的移动缸部114包括第一拼接部117及第二拼接部118，第一拼接部117连接于冲击缸部113，第一拼接部117内形成有第一拼接腔1172，第一拼接腔1172的内壁形成有第一拼接槽1174，且背向于冲击缸部113的一侧开口，第二拼接部118内形成有第二拼接腔1182，第二拼接腔1182的内壁形成有第二拼接槽1184，且第二拼接部118的一侧开口；第二拼接部118的开口侧与第一拼接部117的开口侧对接，以使第一拼接腔1172与第二拼接腔1182对应连通形成容置腔115，第一拼接槽1174与第二拼接槽1184对应连通形成限位槽116。由于移动体122限位于限位槽116内，而往复轴121穿设于容置腔115，进而通过第一拼接部117与第二拼接部118能够便于移动体122在限位槽116的安装，保证移动体122在限位槽116内的有效限位。
在本实施例中，第一拼接部117一体成型于冲击缸部113上。
一实施例中，第一拼接部117与第二拼接部118焊接连接。在其他实施例中，第一拼接部117与第二拼接部118还可以通过螺钉连接，或者卡接在一起。
参阅图1及图4，一实施例中，移动组件100还包括导向杆150，导向杆150位于转动套310外，缸体110的外壁上形成有配合结构112，导向杆150与配合结构112导向配合，且导向杆150的长度方向为往复轴121的轴线方向。通过设置导向杆150与配合结构112的导向配合，进一步保证缸体110往复移动的稳定性。具体地，配合结构112为套状结构，导向杆150穿设于套状的配合结构112内。
在本实施例中，配合结构112形成于移动缸部114的外壁上。
一实施例中，导向杆150的数量为至少两个，各个导向杆150绕往复轴121的轴线间隔设置，每一导向杆150通过一配合结构112与缸体110导向连接。通过设置至少两个导向杆150，能够进一步提高缸体110移动的稳定性。具体地，各个导向杆150绕缸体110均匀布置。在本实施例中，导向杆150的数量为两个。在其他实施例中，导向杆150的数量还可以为三个、四个等其他数目个。
一实施例中，对于单个配合结构112，一部分形成于第一拼接部117的外壁上，另一部分形成于第二拼接部118的外壁上。第一拼接部117与第二拼接部118拼接后以拼接两个部分形成配合结构112。由于导向杆150与配合结构112导向配合，通过在第一拼接部117与第二拼接部118均形成部分配合结构112实现导向杆150能够与第一拼接部117及 第二拼接部118均产生导向配合。
在其他实施例中，配合结构112可以单独形成于第一拼接部117上，或者单独形成于第二拼接部118上。
再次参阅图2，一实施例中，冲击组件200还包括冲击杆220，冲击杆220位于冲锤210背向于缸体110的一侧。冲锤210能够通过冲击杆220冲击转动套310内的钻头。
一实施例中，电锤1010还包括保护壳(图未示)，移动组件100及旋转组件300均设置于保护壳内，通过保护壳实现对移动组件100及旋转组件300的保护。具体地，保护壳内形成有润滑油腔，传动单元330及移动单元120均位于润滑油腔内。通过在润滑油腔添加润滑油，能够保证传动单元330及移动单元120传动的稳定性，提高各个部件的寿命的同时，也可以便于增加往复速度和旋转速度，提高电锤10的冲击功。
传统电锤在工作中，电机转速会随着钻头的钻深负载增加导致速度下降，导致锤击的速度也下降，而上述电锤10，通过第一动力源130与第二动力源320可以避免即使旋转速度下降了，锤击的速度也能够保持，从而提高电锤10的使用效果。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本实用新型的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对实用新型专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本实用新型构思的前提下，还可以做出若干变形和改进，这些都属于本实用新型的保护范围。因此，本实用新型专利的保护范围应以所附权利要求为准。
在本实用新型的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本实用新型和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本实用新型的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本实用新型的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本实用新型中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固 定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本实用新型中的具体含义。
在本实用新型中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
需要说明的是，当元件被称为“固定于”或“设置于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。本文所使用的术语“垂直的”、“水平的”、“上”、“下”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (10)

  1. 一种电锤，其特征在于，所述电锤包括：
    移动组件，所述移动组件包括缸体、移动单元及第一动力源，所述移动单元连接于所述缸体，所述第一动力源用于通过所述移动单元驱动所述缸体往复移动；
    冲击组件，所述冲击组件包括冲锤，所述冲锤穿设于所述缸体内，并与所述缸体内壁密封接触，以使所述冲锤与所述缸体内壁之间形成密封冲击腔，所述冲锤能够在所述缸体内往复移动；及
    旋转组件，所述旋转组件包括转动套及第二动力源，所述缸体穿设于所述转动套内，所述冲击组件设置于所述转动套内，所述第二动力源用于驱动所述转动套相对于所述缸体转动。
  2. 根据权利要求1所述的电锤，其特征在于，所述第一动力源设置于所述转动套的转动轴线方向上，并位于所述缸体背向于所述转动套的一侧；所述第二动力源设置于所述转动套的外壁的一侧。
  3. 根据权利要求2所述的电锤，其特征在于，所述旋转组件还包括传动单元，所述传动单元与所述转动套的外壁相连接，所述第二动力源用于通过所述传动单元驱动所述转动套转动。
  4. 根据权利要求3所述的电锤，其特征在于，所述传动单元包括第一锥齿轮及第二锥齿轮，所述第一锥齿轮套设于所述转动套的外壁上，所述第二锥齿轮与所述第一锥齿轮相啮合，所述第二动力源用于所述第二锥齿轮转动。
  5. 根据权利要求2所述的电锤，其特征在于，所述缸体包括冲击缸部及与所述冲击缸部相连接的移动缸部，所述移动单元连接于所述移动缸部；所述冲锤穿设于所述冲击缸部内，所述冲击缸部穿设于所述转动套内；其中所述移动缸部位于所述转动套外。
  6. 根据权利要求5所述的电锤，其特征在于，所述移动单元包括往复轴及移动体，所述往复轴上设置有往复导轨，所述往复导轨为环绕所述往复轴轴线的闭合曲线形导轨，且所述曲线形导轨的波峰与波谷沿所述往复轴的轴线间隔设置；所述移动体限位于所述缸体上，并能够在所述往复导轨上移动；所述第一动力源用于驱动所述往复轴转动，以使所述移动体带动所述缸体沿所述往复轴的轴线方向往复移动。
  7. 根据权利要求6所述的电锤，其特征在于，所述往复导轨为往复槽，所述往复槽为环绕所述往复轴轴线的闭合曲线形槽，所述移动体穿设于所述往复槽内并能够在所述往复槽内移动；所述缸体的移动缸部内形成有容置腔，所述往复轴穿设于所述容置腔内，且所述容置腔的内壁上形成有限位槽，所述移动体限位于所述限位槽内壁与所述往复槽内壁 之间。
  8. 根据权利要求6或7所述的电锤，其特征在于，所述往复轴上还设置有与所述往复导轨沿所述往复轴轴线间隔相对设置的平衡导轨，所述平衡导轨为环绕所述往复轴轴线的闭合曲线形导轨，且所述平衡导轨的波峰与波谷沿所述往复轴的轴线间隔设置；且所述平衡导轨的波峰沿轴线方向与所述往复导轨的波谷相对，所述平衡导轨的波谷沿轴线方向与所述往复导轨的波峰相对；所述平衡导轨上设置有平衡体，所述平衡体与所述移动体沿所述往复轴的轴线相对设置，当所述往复轴转动时，所述平衡体与所述移动体相向或相背移动。
  9. 根据权利要求6所述的电锤，其特征在于，所述移动组件还包括导向杆，所述导向杆位于所述转动套外，所述缸体的外壁上形成有配合结构，所述导向杆与所述配合结构导向配合，且所述导向杆的长度方向为所述往复轴的轴线方向。
  10. 根据权利要求1-7及9任一项所述的电锤，其特征在于，所述第一动力源与所述第二动力源均为电机。
PCT/CN2023/106056 2022-07-06 2023-07-06 电锤 WO2024008144A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202221725426.X 2022-07-06
CN202221725426.XU CN217801535U (zh) 2022-07-06 2022-07-06 电锤

Publications (1)

Publication Number Publication Date
WO2024008144A1 true WO2024008144A1 (zh) 2024-01-11

Family

ID=83962840

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2023/106056 WO2024008144A1 (zh) 2022-07-06 2023-07-06 电锤

Country Status (2)

Country Link
CN (1) CN217801535U (zh)
WO (1) WO2024008144A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN217801535U (zh) * 2022-07-06 2022-11-15 浙江千机智能科技有限公司 电锤
CN115122282A (zh) * 2022-07-06 2022-09-30 浙江千机智能科技有限公司 电锤
CN115870930A (zh) * 2022-12-19 2023-03-31 浙江马特工具有限公司 电动工具

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1254800A (zh) * 1998-11-21 2000-05-31 张寿龄 柱塞式旋转往复机构
CN200974231Y (zh) * 2006-11-20 2007-11-14 何乃镇 一种电锤钻
CN202398857U (zh) * 2011-11-22 2012-08-29 徐州联宝科技有限公司 一种振动电锤
JP2013144346A (ja) * 2012-01-16 2013-07-25 Hitachi Koki Co Ltd 打撃工具
CN206245745U (zh) * 2016-12-08 2017-06-13 中铁十四局集团第四工程有限公司 手持式混凝土凿毛机
CN217801535U (zh) * 2022-07-06 2022-11-15 浙江千机智能科技有限公司 电锤

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1254800A (zh) * 1998-11-21 2000-05-31 张寿龄 柱塞式旋转往复机构
CN200974231Y (zh) * 2006-11-20 2007-11-14 何乃镇 一种电锤钻
CN202398857U (zh) * 2011-11-22 2012-08-29 徐州联宝科技有限公司 一种振动电锤
JP2013144346A (ja) * 2012-01-16 2013-07-25 Hitachi Koki Co Ltd 打撃工具
CN206245745U (zh) * 2016-12-08 2017-06-13 中铁十四局集团第四工程有限公司 手持式混凝土凿毛机
CN217801535U (zh) * 2022-07-06 2022-11-15 浙江千机智能科技有限公司 电锤

Also Published As

Publication number Publication date
CN217801535U (zh) 2022-11-15

Similar Documents

Publication Publication Date Title
WO2024008144A1 (zh) 电锤
WO2024008135A1 (zh) 电锤
US4072210A (en) Compressor
WO2024008149A1 (zh) 往复传动机构及动力设备
WO2024008137A1 (zh) 用泵设备及柱塞泵
WO2024008141A1 (zh) 动力设备及储能***
WO2024008143A1 (zh) 动力设备
WO2024008133A1 (zh) 用泵设备
JP5161306B2 (ja) 往復回転動力変換装置
WO2024093340A1 (zh) 动力设备
CN108098694A (zh) 动力工具
WO2024008146A1 (zh) 往复传动机构及动力设备
WO2024008153A1 (zh) 往复传动组件及动力机构
EP1905983B1 (en) Kinetic energy generation device
KR960000436B1 (ko) 회전-왕복 피스톤 머신
CN217801536U (zh) 电锤
WO2024131036A1 (zh) 电动工具
US4346768A (en) Impact device with sinusoidal rotary-to-reciprocative converter
CN219005938U (zh) 电动工具
CN103790700A (zh) 用于双转子活塞发动机的功率传输装置
KR100880916B1 (ko) 왕복회전 동력변환장치
CN212508746U (zh) 一种电动隔膜泵运动机构
CN221401548U (zh) 一种动力输出装置及具有其的动力设备
JP2004537011A (ja) トーラスクランク機構
JP2001221312A (ja) ラジアルピストン

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23834911

Country of ref document: EP

Kind code of ref document: A1