CN109555792B - Electric hammer clutch device - Google Patents
Electric hammer clutch device Download PDFInfo
- Publication number
- CN109555792B CN109555792B CN201811481118.5A CN201811481118A CN109555792B CN 109555792 B CN109555792 B CN 109555792B CN 201811481118 A CN201811481118 A CN 201811481118A CN 109555792 B CN109555792 B CN 109555792B
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- teeth
- clutch
- electric hammer
- tooth
- cylinder
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D11/00—Portable percussive tools with electromotor or other motor drive
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
Abstract
The application relates to the technical field of electric hammers, in particular to an electric hammer clutch device. The utility model provides an electric hammer clutch, including electric hammer main part, the cylinder, the rotation axis, the separation and reunion tooth, the meshing tooth, first drive assembly, be used for driving rotation axis pivoted second drive assembly and the knob subassembly of being connected with the separation and reunion tooth, first drive assembly's one end and electric hammer main part are connected respectively at the piston both ends of cylinder, the meshing tooth is installed on the cylinder and is rotated with driving the cylinder, the knob subassembly rotates with the axial slip on the rotation axis of drive separation and reunion tooth, and then make separation and reunion tooth and meshing tooth meshing or separation with another end joint of first drive assembly. According to the application, the knob assembly is rotated to drive the clutch teeth to transversely move along the rotating shaft, so that the clutch teeth are driven to be meshed with or separated from the meshing teeth, the clutch teeth are driven to be clamped with or separated from the first transmission assembly, and the knob assembly is driven to be meshed with or separated from the meshing teeth, so that the four working states of the electric hammer can be conveniently converted.
Description
Technical Field
The application relates to the technical field of electric hammers, in particular to an electric hammer clutch device.
Background
The electric hammer is an electric rotary hammer drill with a safety clutch and a pneumatic hammering mechanism. An electric hammer is a device for punching holes in hard materials such as concrete, bricks, stones and the like by compressing gas by utilizing the principle of piston movement, thereby improving the hole punching efficiency.
In order to meet the demands of customers, the electric hammer in the existing market is often required to be matched with the clutch to set, has a complex structure, increases the stroke and is not beneficial to users to quickly switch the working mode of the electric hammer.
Disclosure of Invention
In order to solve the technical problem that a user cannot conveniently and quickly change the working mode of the electric hammer in the related art, the embodiment of the application provides the electric hammer clutch device, which aims to simplify the structure and eliminate the influence of the increase of the stroke caused by the clutch on the inconvenient and quick switching of the working mode.
The application provides an electric hammer clutch device which comprises an electric hammer main body, an air cylinder, a rotating shaft, clutch teeth, meshing teeth, a first transmission assembly, a second transmission assembly for driving the rotating shaft to rotate and a knob assembly connected with the clutch teeth.
The second transmission component drives the rotating shaft to rotate so as to drive the clutch teeth to rotate, and when the clutch teeth are clamped with the engagement teeth, the engagement teeth drive the air cylinder to rotate under the drive of the clutch teeth; the knob assembly is rotated to drive the clutch teeth to slide along the rotating shaft, so that the clutch teeth are meshed with or separated from the meshing teeth, and the rotating state of the cylinder is regulated; through the arrangement of the clutch teeth, the meshing teeth, the first transmission assembly, the second transmission assembly, the air cylinder and the knob assembly, the relative motion state of the clutch teeth, the meshing teeth, the first transmission assembly, the second transmission assembly, the air cylinder and the knob assembly can be conveniently adjusted through the adjusting knob assembly, and then the conversion of four working states of the electric hammer drill, the angle adjustment and the hammer is realized.
Optionally, the knob subassembly includes knob, driving pin, guide rail pin and shifting block, and the driving pin is connected with the shifting block, and shifting block slidable mounting is equipped with first draw-in groove on the guide rail pin, is equipped with the card on the shifting block, and in the first draw-in groove was located to the card, the knob was rotatory in order to drive the shifting block through the driving pin and axially slide on the guide rail pin.
The rotary motion of the knob is conveniently converted into the transverse motion of the shifting block through the transmission pin transmission, and the shifting block pushes the clutch teeth to do transverse reciprocating motion; the clamping piece of the shifting block is clamped with the first clamping groove so that the shifting block can push the clutch teeth to slide along the rotating shaft; by providing the guide rail pin, the moving path of the shifting block is conveniently guided.
Optionally, the shifting block is further provided with a toothed end, and when the knob drives the clutch tooth to be clamped with the first transmission assembly and separated from the engaging tooth, the engaging tooth is engaged with or separated from the toothed end.
The toothed end is arranged at the end part of the shifting block, so that when the clutch teeth are clamped with the first transmission assembly and separated from the engaging teeth, the engaging teeth are engaged with the toothed end, and the cylinder is limited to act and is prevented from rotating.
Optionally, the knob assembly further comprises a torsion spring and a fixing frame slidably mounted on the guide rail pin, the fixing frame is sleeved outside the shifting block, the torsion spring is arranged on the fixing frame, the torsion spring and the shifting block are respectively located on two sides of the fixing frame, a first through hole is formed in the torsion spring, a second through hole is formed in the fixing frame relative to the position of the first through hole, one end of the transmission pin is connected with the knob, and the other end of the transmission pin penetrates through the first through hole and the second through hole and is connected with the shifting block.
The torsional spring is arranged so as to improve the transmission stability of the transmission pin, in particular, the knob rotates and transmits kinetic energy through the transmission pin to drive the clutch teeth to do transverse movement and reciprocating motion along the rotating shaft, and in the transmission process of the transmission pin, the transmission pin is easy to shake, so that the transmission of the transmission pin is stabilized through the torsional spring; through the setting to the mounting bracket, the torsional spring of being convenient for installs.
Optionally, the first transmission assembly includes swing rod bearing and the beat bearing of joint or separation with the separation and reunion tooth, beat the pendulum bearing suit on the rotation axis, the swing rod bearing includes the pendulum ring and is connected with the pendulum rod of pendulum ring, the other end and the piston rotation of pendulum rod are connected, the periphery side of beat bearing is equipped with the guide slot that the slope set up, the pendulum ring has along the gliding slider of guide slot.
Through setting up pendulum ring, pendulum rod and beat bearing, be convenient for beat bearing and separation and reunion tooth joint back, do synchronous rotation action with separation and reunion tooth, the slider of pendulum ring slides along the guide slot to drive the pendulum rod action, and then drive cylinder piston and do reciprocating motion.
Optionally, be equipped with trip spring, take off board knot, first jump ring and second jump ring on the cylinder, one side of meshing tooth and take off one side block setting of board knot, take off the opposite side of board knot and link to each other with first jump ring, trip spring clamp dress is between the opposite side of meshing tooth and second jump ring.
Through taking off board knot and meshing tooth block setting, preliminary restriction meshing tooth is followed the cylinder surface and is slided, and the rethread is taking off the opposite side that the board was detained and is set up first jump ring, and the meshing tooth is not equipped with the one side that takes off the board knot and is equipped with the second jump ring to further fixed meshing tooth prevents that it from sliding along the cylinder, in addition, through setting up the tripping spring between second jump ring and meshing tooth, in order to when the meshing tooth slides along the cylinder, buffering and make the meshing tooth return to the normal position through self elastic action.
Optionally, the second transmission assembly comprises a driving bevel gear and a driven bevel gear, wherein the driven bevel gear is arranged at one end of the rotating shaft, and the driving bevel gear and the driven bevel gear are meshed for transmission.
Through the arrangement of the driving bevel gear and the driven bevel gear, the driving bevel gear and the driven bevel gear are convenient to form a gear pair so as to drive the rotating shaft to do axial rotation.
Optionally, the knob assembly drives the clutch teeth to axially slide along the rotation shaft so that the clutch teeth mesh with the engagement teeth, and the clutch teeth are clamped or separated from the first transmission assembly, wherein: when the clutch teeth are clamped with the first transmission assembly, the clutch teeth drive the first transmission assembly to rotate and the meshing teeth to rotate so that the cylinder rotates and the first transmission assembly drives the piston to do reciprocating motion, and the electric hammer main body is switched to a hammer drill state; when the clutch teeth are separated from the first transmission assembly, the clutch teeth drive the air cylinder to rotate through the meshing teeth, and the electric hammer main body is switched to a drilling state.
When the clutch teeth and the meshing teeth are meshed, the clutch teeth are controlled to be clamped or separated with the first transmission assembly, so that the electric hammer main body is in a drilling or hammer drilling state. Specifically, when the clutch teeth are clamped with the first transmission assembly, the first transmission assembly is stressed to drive the piston to do reciprocating motion, namely, impact motion is carried out in the cylinder, so that the function of the electric hammer drill is realized; when the clutch teeth are separated from the first transmission assembly, the first transmission assembly is not stressed and does not drive the cylinder piston to do reciprocating motion, so that the electric hammer does not output impact while drilling, and the function of the electric hammer drill is realized.
Optionally, the knob subassembly drives the separation and reunion tooth and follows rotation axis axial slip to make separation and reunion tooth and meshing tooth separate, separation and reunion tooth and first drive assembly joint, profile of tooth end and meshing tooth joint or separation, wherein: when the tooth-shaped end is separated from the meshing teeth, the cylinder performs radial rotation action, and the electric hammer main body is switched to an angle adjusting state; when the tooth-shaped end is clamped with the meshing teeth, the air cylinder is fixed, and the clutch teeth drive the first transmission assembly to rotate, so that the first transmission assembly drives the piston to do reciprocating motion, and the electric hammer is switched to a hammer state.
When the clutch teeth are separated from the meshing teeth, the clutch teeth are clamped with the first transmission assembly, the first transmission assembly drives the piston to reciprocate, and the toothed end is controlled to be clamped with or separated from the meshing teeth, so that the radial direction of the air cylinder is not stressed or the air cylinder is fixed and cannot rotate, and the electric hammer main body is in an angle adjusting or hammering state.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application as claimed.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for the description of the embodiments will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural diagram of an electric hammer clutch device provided by the application;
FIG. 2 is an exploded view of the electric hammer clutch device of FIG. 1;
FIG. 3 is a schematic view of the knob assembly of FIG. 1;
FIG. 4 is an exploded view of the knob assembly shown in FIG. 3;
fig. 5 is a schematic structural view of the stripper plate shown in fig. 1.
In the figure: 100. an electric hammer main body; 110. a cylinder; 120. a piston; 200. a first transmission assembly; 220. a swing rod bearing; 221. swing rod; 222. a swinging ring; 230. a yaw bearing; 231. a first toothed hole; 232. a guide groove; 300. meshing teeth; 310. a groove; 320. removing the plate buckle; 321. a convex plate; 330. a trip spring; 340. a second clamp spring; 350. a first clamp spring; 400. clutch teeth; 410. a first clamping groove; 420. a third through hole; 500. a second transmission assembly; 510. a driving bevel gear; 520. driven umbrella teeth; 600. a knob assembly; 610. a knob; 611. a fourth through hole; 620. a fixing frame; 621. a second through hole; 630. a shifting block; 631. a tooth end; 632. a guide rail pin; 640. a drive pin; 650. a torsion spring; 651. a first through hole; 700. and (3) rotating the shaft.
Description of the embodiments
Reference will now be made in detail to embodiments of the present application, examples of which are illustrated in the accompanying drawings. The embodiments described below by referring to the drawings are illustrative and intended to explain the present application and should not be construed as limiting the application.
In order to meet the demands of customers, the electric hammer in the existing market is often required to be matched with the clutch to set, has a complex structure, increases the stroke and is not beneficial to users to quickly switch the working mode of the electric hammer.
In order to solve the technical problem that a user cannot conveniently and quickly change the working mode of the electric hammer in the related art, the embodiment of the application provides the electric hammer clutch device, which aims to simplify the structure and eliminate the influence of the increase of the stroke caused by the clutch on the inconvenient and quick switching of the working mode. The structure of the electric hammer clutch device is exemplified below with reference to fig. 1 to 5.
The electric hammer clutch device comprises an electric hammer main body 100, a cylinder 110, a rotating shaft 700, a clutch tooth 400, a meshing tooth 300, a first transmission assembly 200, a second transmission assembly 500 for driving the rotating shaft 700 to rotate and a knob assembly 600 connected with the clutch tooth 400, wherein one end of the first transmission assembly 200 and the electric hammer main body 100 are respectively connected with two ends of a piston 120 of the cylinder 110, the meshing tooth 300 is arranged on the cylinder 110 to drive the cylinder 110 to rotate, the knob assembly 600 rotates to drive the clutch tooth 400 to axially slide on the rotating shaft 700, and then the clutch tooth 400 is clamped with or separated from the other end of the first transmission assembly 200, and the clutch tooth 400 is meshed with or separated from the meshing tooth 300, so that the switching of four states of drilling, hammering and angle adjustment of an electric hammer cylinder is realized.
In the actual design process, the engaging teeth 300 are fixedly arranged on the cylinder 110, and the clutch teeth 400 do transverse movement and reciprocating movement relative to the engaging teeth 300. In this embodiment, the cylinder 110 is provided with a trip spring 330, a trip plate buckle 320, a first clamp spring 350 and a second clamp spring 340, one side of the engaging tooth 300 is engaged with one side of the trip plate buckle 320, the other side of the trip plate buckle 320 is connected with the first clamp spring 350, and the trip spring 330 is clamped between the other side of the engaging tooth 300 and the second clamp spring 340.
Optionally, the second clamp spring 340 is a flat clamp spring, and the first clamp spring 350 is a steel wire clamp spring.
Optionally, a groove 310 is formed on a side, adjacent to the trip plate 320, of the engaging tooth 300, a convex plate 321 is formed on a side, adjacent to the engaging tooth 300, of the trip plate 320, and the convex plate 321 is clamped in the groove 310 to realize the clamping arrangement of the engaging tooth 300 and the trip plate 320.
In order to facilitate the knob assembly 600 to drive the clutch teeth 400 to make a traversing reciprocating motion along the rotation shaft 700, the clutch teeth 400 are provided with a first clamping groove 410 and a third through hole 420, the knob assembly 600 is connected with the first clamping groove 410, the rotation shaft 700 is configured to pass through the third through hole 420, and the extending end of the rotation shaft 700 relative to the third through hole 420 are respectively provided with a locking piece so as to fix the position of the clutch teeth 400 relative to the rotation shaft 700, so that the clutch teeth 400 make a synchronous rotation motion along with the rotation shaft 700.
Specifically, the knob assembly 600 includes a knob 610, a driving pin 640, a guide pin 632 and a dial block 630, the driving pin 640 is connected with the dial block 530, the dial block 630 is slidably mounted on the guide pin 632, a card is disposed on the dial block 630, the card is disposed in the first card slot 410, and the knob 610 rotates to drive the dial block 630 to axially slide on the guide pin 632 through the driving pin 640.
In this embodiment, the gear-shaped end 631 is further disposed on the shifting block 630, and when the knob 610 drives the clutch teeth 400 to engage with the first transmission assembly 200 and disengage from the engaging teeth 300, the engaging teeth 300 engage with or disengage from the gear-shaped end 631. In a specific implementation, the toothed end 631 of the shifting block 630 is matingly disposed according to the tooth profile of the engagement tooth 300.
In practical application, the knob 610 rotates to drive the shifting block 630 to shift the clutch teeth 400, so that the clutch teeth 400 move transversely along the rotation axis 700, so that the clutch teeth 400 move transversely and reciprocally relative to the engaging teeth 300, the clutch teeth 400 engage with or disengage from the engaging teeth 300, and in addition, since the card of the shifting block 630 is clamped in the first clamping groove 410, the shifting block 630 moves synchronously and transversely relative to the engaging teeth 300 along with the clutch teeth 400, and the toothed end 631 at one end of the shifting block 630 engages with or disengages from the engaging teeth 300.
In this embodiment, the knob assembly 600 further includes a torsion spring 650 and a fixing frame 620 slidably mounted on the guide rail pin 632, the fixing frame 620 is sleeved outside the dial block 630, the torsion spring 650 is disposed on the fixing frame 620, the torsion spring 650 and the dial block 630 are respectively located on two sides of the fixing frame 620, a first through hole 651 is formed in the torsion spring 650, a second through hole 621 is formed in the fixing frame 620 at a position corresponding to the first through hole 651, one end of the transmission pin 640 is connected with the knob 610, and the other end of the transmission pin 640 penetrates through the first through hole 651 and the second through hole 621 and is connected with the dial block 630.
Further, the fixing frame 620 is provided with a receiving space for receiving the guide pin 632 and the shifting block 630, two ends of the guide pin 632 are respectively connected to two sides of the fixing frame 620, and the shifting block 630 is disposed on the guide pin 632.
In a specific implementation manner, the driving pin 640 includes a first cylinder, a second cylinder and a third cylinder, the ends of the second cylinder and the third cylinder are respectively and vertically connected with two ends of the first cylinder, the second cylinder and the third cylinder are parallel, the second cylinder and the third cylinder are respectively located at two sides of a vertical plane where an axis of the first cylinder is located, the second cylinder passes through the first through hole 651 and the second through hole 621, a fourth through hole 611 is formed in the knob 610, and the third cylinder is configured to be inserted into the fourth through hole 611.
Alternatively, the first transmission assembly 200 includes a swing rod bearing 220 and a swing bearing 230, the swing bearing 230 is sleeved on the rotating shaft 700, and when the clutch teeth 400 do a traversing and reciprocating motion along the rotating shaft 700, the swing bearing 230 is clamped with or separated from the clutch teeth 400. Further, the end of the yaw bearing 230 adjacent to the clutch teeth 400 is provided with a first toothed hole 231, and the first toothed hole 231 is matched with the clutch teeth 400 according to the tooth shape of the clutch teeth 400 so as to be clamped with the clutch teeth 400.
When the deflection bearing 230 is clamped with the clutch teeth 400, the rotation shaft 700 drives the clutch teeth 400 to rotate, so that the meshing teeth 300 can drive the deflection bearing 230 to rotate, so that the swing rod bearing 220 is stressed to drive the piston 120 to do impact motion in the cylinder 110, namely, the piston 120 does transverse movement and reciprocating motion in the cylinder 110; when the yaw bearing 230 is separated from the second clutch assembly 400, the swing rod bearing 220 is not stressed and the piston 120 does not act.
In a specific implementation manner, the swing rod bearing 220 includes a swing rod 221 and a swing ring 222, one end of the swing rod 221 is connected with the swing ring 222, the other end of the swing rod 221 is rotatably connected with the piston 120, a guide groove 232 which is obliquely arranged is arranged on the outer peripheral side of the yaw bearing 230, and the swing ring 222 is provided with a sliding block sliding along the guide groove 232. Further, the end of the swing link 221 is connected to the piston 120 through a pin.
Alternatively, the guide groove 232 is biased toward an outer surface of the yaw bearing 230. Specifically, the guiding groove 232 is a closed ring structure, and a part of the ring is biased towards one end of the yaw bearing 230, and the rest of the ring is biased towards the other end of the yaw bearing 230, i.e. the plane of the guiding groove 232 forms a certain angle with the side surface of the yaw bearing 230.
The second transmission assembly 500 includes a driving bevel gear 510 and a driven bevel gear 520, the driven bevel gear 520 is disposed at one end of the rotation shaft 700, and the driving bevel gear 510 and the driven bevel gear 520 are engaged for transmission. In this embodiment, the driving bevel gear 510 and the driven bevel gear 520 form a gear pair to drive the rotation shaft 700 to perform an axial rotation motion.
In one possible implementation, the knob assembly 600 drives the clutch teeth 400 axially along the rotational axis 700 such that the clutch teeth 400 engage with the engagement teeth 300, and the clutch teeth 400 are engaged with or disengaged from the first transmission assembly 200.
When the clutch teeth 400 are separated from the swing bearing 230, that is, when the knob 600 rotates for the first time, the clutch teeth 400 slide along the rotation shaft 700 toward the engaging teeth 300, the clutch teeth 400 are engaged with the engaging teeth 300, at this time, the swing bearing 230 is separated from the clutch teeth 400, the swing rod bearing 220 is not stressed, the piston 120 does not act to do impact motion in the cylinder 110, and the clutch teeth 400 drive the cylinder 110 to do rotation motion through the engaging teeth 300, so that the electric hammer is drilled without impact when being output, that is, the electric hammer is in a drilling state.
When the clutch teeth 400 are clamped with the swinging bearing 230, that is, when the knob 610 rotates for the second time, the clutch teeth 400 are meshed with the meshing teeth 300, at this time, the clutch teeth 400 slide along the rotation shaft 700 in the opposite direction of the meshing teeth 300, the swinging bearing 230 is clamped with the clutch teeth 400, the swinging rod bearing 220 is forced to drive the piston 120 to do reciprocating motion so as to generate impact in the cylinder 110, and the clutch teeth 400 drive the cylinder 110 to do rotating motion through the meshing teeth 300, so that drilling and impact during output of the electric hammer is realized, that is, the electric hammer is in a drilling hammer state.
In another possible implementation, knob assembly 600 drives clutch teeth 400 axially along rotation axis 700 to disengage clutch teeth 400 from engagement teeth 300, clutch teeth 400 snap-fit with first transmission assembly 200, and toothed end 631 snap-fit or disengage from engagement teeth 300.
When the toothed end 631 is separated from the engaging tooth 300, that is, when the knob 610 rotates for the third time, the clutch tooth 400 continues to slide along the rotation axis 700 in the opposite direction to the engaging tooth 300, the clutch tooth 400 is separated from the engaging tooth 300, the swinging bearing 230 is clamped with the clutch tooth 400, the swinging rod bearing 220 is forced to drive the piston 120 to reciprocate so as to generate impact in the cylinder 110, at this time, the engaging tooth 300 is not forced due to the separation of the clutch tooth 400 and the engaging tooth 300, so that the cylinder 110 is not forced in the radial direction, and the electric hammer can adjust an angle at the output end, that is, the electric hammer is in an angle adjusting state.
When the toothed end 631 engages with the engagement tooth 300, i.e., when the knob 610 rotates for the fourth time, the clutch tooth 400 slides along the rotation axis 700 toward the engagement tooth 300, and at this time, the clutch tooth 400 is still in a separated state from the engagement tooth 300, but the toothed end 631 of the shifting block 630 engages with the engagement tooth 300, the cylinder 110 cannot rotate radially, the deflection bearing 230 is clamped with the clutch tooth 400, and the swing rod bearing 220 is forced to drive the piston 120 to perform impact motion in the cylinder 110, so that only impact occurs when the electric hammer outputs, i.e., the electric hammer is in a hammer working state.
In the actual design process, the motion states of the corresponding parts after the first rotation, the second rotation, the third rotation, the fourth rotation and the rotation are all matched according to four working states of the electric hammer, namely the drill, the drill hammer, the angle adjustment and the hammer, and when the working state realized correspondingly by the rotation is changed, the action modes of the corresponding parts correspondingly change, so that the application is not limited further.
In this embodiment, the rotation angle of the knob 610 may be 30 ° each time; alternatively, the rotation angle of the knob 610 may be 45 ° each time; alternatively, the rotation angle of the knob 610 may be 60 ° each time; alternatively, the rotation angle of the knob 610 may be 90 ° each time. In the actual design process, the rotation angle of the knob 610 may be determined according to the actual design requirement or the comfort level of the operator, and in addition, the rotation number of the knob 610 is set according to the kind of the function to be implemented by the electric hammer, which is not further limited in the present application.
In summary, in the method for implementing four functions provided in the embodiment of the present application, the knob assembly is rotated to drive the clutch teeth to make a traversing and reciprocating motion along the rotation axis, so as to drive the clutch teeth to engage with or disengage from the engagement teeth, and then the second transmission assembly is used to drive the rotation axis to rotate so as to drive the engagement teeth and the cylinder to rotate or not rotate, so as to drive the clutch teeth to be clamped with or disengage from the first transmission assembly so as to drive the first transmission assembly to drive the piston cluster to reciprocate to generate impact in the cylinder, and drive the knob assembly to engage with or disengage from the engagement teeth, thereby facilitating adjustment of rotation of the cylinder or limiting rotation of the cylinder, facilitating implementation of conversion of four working states of the hammer drill, the angle adjustment and the hammer drill, and simple operation.
In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the drawings are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element in question must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present application.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.
The above embodiments are merely illustrative embodiments of the present application, but the technical features of the present application are not limited thereto, and any changes or modifications made by those skilled in the art within the scope of the present application are included in the scope of the present application.
Claims (6)
1. The electric hammer clutch device is characterized by comprising an electric hammer main body, a cylinder, a rotating shaft, clutch teeth, meshing teeth, a first transmission assembly, a second transmission assembly for driving the rotating shaft to rotate and a knob assembly connected with the clutch teeth, wherein one end of the first transmission assembly and the electric hammer main body are respectively connected with two ends of a cylinder piston, the meshing teeth are arranged on the cylinder to drive the cylinder to rotate, the knob assembly rotates to drive the clutch teeth to axially slide on the rotating shaft, so that the clutch teeth are clamped or separated from the other end of the first transmission assembly, and the clutch teeth are meshed or separated from the meshing teeth, so that the four states of drilling, hammering and angle adjustment of the electric hammer main body are switched; the knob assembly comprises a knob, a transmission pin, a guide rail pin and a shifting block, wherein the transmission pin is connected with the shifting block, the shifting block is slidably arranged on the guide rail pin, a first clamping groove is formed in the clutch tooth, a card is arranged on the shifting block and is clamped in the first clamping groove, and the knob rotates to drive the shifting block to axially slide on the guide rail pin through the transmission pin; the shifting block is also provided with a tooth-shaped end, and when the knob drives the clutch teeth to be clamped with the first transmission assembly and separated from the meshing teeth, the meshing teeth are meshed with or separated from the tooth-shaped end; the knob assembly further comprises a torsion spring and a fixing frame which is slidably mounted on the guide rail pin, the fixing frame is sleeved outside the shifting block, the torsion spring is arranged on the fixing frame, the torsion spring and the shifting block are respectively located on two sides of the fixing frame, a first through hole is formed in the torsion spring, a second through hole is formed in the fixing frame relative to the position of the first through hole, one end of the transmission pin is connected with the knob, and the other end of the transmission pin penetrates through the first through hole and the second through hole.
2. The electric hammer clutch device according to claim 1, wherein the first transmission assembly comprises a swing rod bearing and a deflection bearing which is clamped with or separated from the clutch teeth, the deflection bearing is sleeved on the rotating shaft, the swing rod bearing comprises a swing ring and a swing rod connected with the swing ring, the other end of the swing rod is rotatably connected with the piston, a guide groove which is obliquely arranged is arranged on the outer peripheral side of the deflection bearing, and the swing ring is provided with a sliding block which slides along the guide groove.
3. The electric hammer clutch device according to claim 1, wherein a tripping spring, a trip plate buckle, a first clamping spring and a second clamping spring are arranged on the cylinder, one side of the meshing tooth is clamped with one side of the trip plate buckle, the other side of the trip plate buckle is connected with the first clamping spring, and the tripping spring is clamped between the other side of the meshing tooth and the second clamping spring.
4. The electric hammer clutch device according to claim 1, wherein the second transmission assembly comprises a driving bevel gear and a driven bevel gear, the driven bevel gear is arranged at one end of the rotating shaft, and the driving bevel gear and the driven bevel gear are meshed for transmission.
5. The electric hammer clutch device of claim 1, wherein the knob assembly drives the clutch teeth to slide axially along the rotational axis to engage the clutch teeth with the engagement teeth, the clutch teeth being engaged with or disengaged from the first transmission assembly, wherein:
when the clutch teeth are clamped with the first transmission assembly, the clutch teeth drive the first transmission assembly to rotate and the meshing teeth to rotate, so that the cylinder rotates and the first transmission assembly drive the piston to reciprocate, and the electric hammer main body is switched to a hammer drill state;
when the clutch teeth are separated from the first transmission assembly, the clutch teeth drive the air cylinder to rotate through the meshing teeth, so that the electric hammer main body is switched to a drilling state.
6. The electric hammer clutch device of claim 1, wherein the knob assembly drives the clutch teeth to slide axially along the rotational axis to disengage the clutch teeth from the engagement teeth, the clutch teeth being engaged with the first transmission assembly, the toothed end being engaged with or disengaged from the engagement teeth, wherein:
when the tooth-shaped end is separated from the meshing teeth, the cylinder performs radial rotation action, and the electric hammer main body is switched to an angle adjusting state;
when the tooth-shaped end is clamped with the meshing teeth, the air cylinder is fixed, the clutch teeth drive the first transmission assembly to rotate, so that the first transmission assembly drives the piston to do reciprocating motion, and the electric hammer is switched to a hammer state.
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| CN110561350B (en) * | 2019-08-28 | 2020-09-11 | 浙江信源电器制造有限公司 | Electric hammer |
| CN112962147B (en) * | 2021-02-03 | 2022-02-11 | 中国农业科学院麻类研究所 | Mountain region ramie feeds numb device |
| CN113414746B (en) * | 2021-07-02 | 2022-09-06 | 重庆弘愿工具(集团)有限公司 | Electric hammer keeps off position switching subassembly |
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