CN113561342B - Air pressure self-balancing cylinder structure for electric tool - Google Patents
Air pressure self-balancing cylinder structure for electric tool Download PDFInfo
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- CN113561342B CN113561342B CN202111125403.5A CN202111125403A CN113561342B CN 113561342 B CN113561342 B CN 113561342B CN 202111125403 A CN202111125403 A CN 202111125403A CN 113561342 B CN113561342 B CN 113561342B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B28—WORKING CEMENT, CLAY, OR STONE
- B28D—WORKING STONE OR STONE-LIKE MATERIALS
- B28D1/00—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor
- B28D1/26—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by impact tools, e.g. by chisels or other tools having a cutting edge
- B28D1/265—Scabbling machines or scabbling tools
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B28—WORKING CEMENT, CLAY, OR STONE
- B28D—WORKING STONE OR STONE-LIKE MATERIALS
- B28D1/00—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor
- B28D1/14—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by boring or drilling
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B28—WORKING CEMENT, CLAY, OR STONE
- B28D—WORKING STONE OR STONE-LIKE MATERIALS
- B28D7/00—Accessories specially adapted for use with machines or devices of the preceding groups
- B28D7/005—Devices for the automatic drive or the program control of the machines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1428—Cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
Abstract
The invention discloses an air pressure self-balancing cylinder structure for an electric tool, which comprises a cylinder and a cylinder shell, wherein the cylinder shell is sleeved at the outside of the cylinder, two ends of the cylinder shell are sealed, a second air cavity is formed between the cylinder and the cylinder shell, an impact rod, a punch hammer and a piston are sequentially arranged in the cylinder in a sliding manner, a first air hole and a second air hole which are respectively communicated in the front-back direction and block the air cavity are formed in the circumferential wall of the cylinder, a blocking component which is connected with the impact rod and mutually driven is sleeved outside the cylinder, the second air hole is kept open under the unstressed state that the impact rod faces the punch hammer, and one air hole is alternately blocked by the blocking component and the punch hammer in the stroke range. The improved cylinder structure has the advantages of simple manufacture and strong reliability, can optimize the balance of air pressure in the cylinder, solves the problems of breaking impact, continuous impact, self-hammering and the like, improves the impact efficiency and stability of the electric tool, prolongs the service life of the electric tool, relieves the reaction force in actual operation, and improves the operation experience of users.
Description
Technical Field
The invention relates to an electric tool transmission structure, in particular to an improved air pressure self-balancing cylinder structure for a hammer and pickaxe type electric tool.
Background
The electric hammer and electric pick of the existing electric tool mainly rely on a transmission mechanism to drive a piston to compress air in a cylinder in a reciprocating way (forming a rear air spring), and the periodic change of the air pressure in the cylinder drives a hammer to move in a reciprocating way to compress air (forming a front air spring) and strike an impact rod and a drill bit, so as to output external impact force.
The balance of front and rear air springs in the air cylinder has direct influence on the performance of a machine and the experience of a user, and at present, the air inlet and outlet holes and the compensation holes in the outer wall of the air cylinder are mainly adjusted, but the ideal state is difficult to achieve. In the actual working process of the tool, the phenomenon of breaking or continuous punching still frequently occurs, and the working efficiency, the service life and the user experience of the tool are influenced.
Disclosure of Invention
The invention aims to provide an air pressure self-balancing air cylinder structure for an electric tool, so as to optimize the air pressure balance of front and rear air springs and solve the problems of breaking, continuous punching, self-hammering and the like of the electric tool.
In order to achieve the technical purpose, the invention provides an air pressure self-balancing cylinder structure for an electric tool, wherein an impact rod, a punch hammer and a piston which slide along the axial direction are sequentially arranged in a cylinder, a first air cavity is formed between the punch hammer and the forward impact rod, and a third air cavity is formed between the punch hammer and the backward piston, and the air pressure self-balancing cylinder structure is characterized in that: the cylinder structure comprises a plugging component and a cylinder shell which are sleeved outside the cylinder from inside to outside, a second air cavity is formed between the cylinder and the cylinder shell, a first air hole communicated with the first air cavity and the second air cavity is formed in the circumferential wall of the cylinder, a second air hole communicated with the second air cavity and the third air cavity is formed in the circumferential wall of the cylinder, the plugging component comprises a distance cylinder, a first distance ring, a second distance ring, a special-shaped gasket and an elastic part, wherein the special-shaped gasket is integrally sleeved with an impact rod in the cylinder and is provided with a boss penetrating through the cylinder and abutted against one end face of the distance cylinder, the first distance ring part is penetrated between the distance cylinder and the outer wall of the cylinder, and two sides of a flange of the first distance ring, which are far away from the first air hole, are abutted against the other end face of the distance cylinder and the second distance ring; the elastic piece is sleeved outside the cylinder, one end of the elastic piece pushes against the second distance ring, and the second distance ring opens or blocks the second air hole in the telescopic stroke of the elastic piece; the plugging component is connected with the impact rod to follow up, the second air hole is kept open when the impact rod faces the impact hammer and is not under stress, and the plugging component and the impact hammer alternately plug one of the air holes in a stroke range.
Furthermore, the distance cylinder is provided with at least one row of vent holes in the circumferential direction close to the special-shaped gasket.
Further, the axial length of the punch hammer and the sum of the lengths of the first distance ring and the second distance ring are within the maximum distance range between the two air holes.
Furthermore, the elastic part is a compression spring, a fixed sleeve which is connected in a sealing mode is arranged at one end, far away from the impact rod, of the cylinder and the cylinder shell, and one end, far away from the second distance ring, of the elastic part abuts against the fixed sleeve.
Furthermore, the cylinder is connected with a crankcase with a built-in crankshaft outside the fixed sleeve, the piston is hinged with a connecting rod through a piston pin, and the crankshaft is in hinged transmission with the connecting rod.
And furthermore, a fourth air cavity is formed in the crankcase, the crankcase is provided with a third air hole, the fixing sleeve is provided with a fourth air hole, and the second air cavity is communicated with the fourth air cavity through the third air hole and the fourth air hole.
Furthermore, at least one sliding groove is formed in the circumferential wall of the air cylinder in parallel to the axial direction, and the boss of the special-shaped gasket penetrates out of the sliding groove, is mutually transmitted with the distance cylinder and slides along the sliding groove in a guiding manner; and the length of the sliding groove is larger than the outer diameter of the special-shaped gasket.
Furthermore, a convex ring sleeved with the outer wall of the air cylinder is arranged on the inner wall of the end part of the air cylinder shell close to the impact rod, a first shock pad is connected to the convex ring, and a third gasket and a second shock pad are sleeved on the impact rod.
Compared with the prior art, the technical scheme of the invention has prominent substantive characteristics, and the beneficial effects of the technology show remarkable progress: by optimizing the layout of the air cavities and the adjustability of air hole plugging caused by the position change of the impact rod under different compression conditions, the air cavities in the air cylinder and the air cylinder shell can be freely switched between an isolated state and an open state to adjust air pressure. This atmospheric pressure self-balancing cylinder structure makes simply, the good reliability, can optimize the balance of the inside atmospheric pressure of cylinder, solves the problem of disconnected dashing, even dashing, self-hammering etc. improves electric tool's impact efficiency and stability, prolongs electric tool's life, and reaction force when alleviating the actual operation promotes user operation and experiences.
Drawings
Fig. 1 is a schematic diagram of a non-working half-section of a preferred embodiment of the pneumatic self-balancing cylinder structure for a power tool of the present invention.
Figure 2 is a schematic half-section view of the preferred embodiment of figure 1 in its operating state.
Fig. 3 is a schematic diagram of the explosion structure of the cylinder and the plugging assembly in the preferred embodiment shown in fig. 1.
Fig. 4 is a schematic view of an assembly structure of the cylinder and the plugging assembly in the preferred embodiment shown in fig. 3.
Wherein: 1-a first cushion, 2-a first gasket, 3-a cylinder, 4-a profiled gasket, 40-a runner, 41-a boss, 5-a distance cylinder, 6-a first distance ring, 7-a second distance ring, 8-an elastic member, 9-a second gasket, 10-a fixed sleeve, 11-a drill bit, 12-an impact rod, 13-a third gasket, 14-a second cushion, 15-a hammer, 16-a first O-ring, 17-a piston, 18-a second O-ring, 19-a piston pin, 20-a cylinder shell, 21-a crankcase, 22-a connecting rod, 23-a crankshaft, a-a compensation hole, B-a second air hole, C-a first air hole, D-an air hole, E-a third air hole, F-a fourth air hole, x-first air cavity, Y-second air cavity, Z-third air cavity, W-fourth air cavity.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from this embodiment of the invention without any inventive step, are within the scope of protection of the invention.
Referring to the structural diagrams of the preferred embodiment of the present invention shown in fig. 1 to 4 in each state, the present invention discloses an air pressure self-balancing cylinder structure for an electric tool, similar to the cylinder structure of a conventional electric tool, the cylinder 3 is internally provided with an impact rod 12, a hammer 15 and a piston 17 which slide along the axial direction in sequence, a first air chamber X is formed between the hammer 15 and the impact rod 12 in the forward direction, and a third air chamber Z is formed between the hammer 15 and the piston 17 in the backward direction. As an innovative improvement and optimization of the cylinder structure, the outer side of the cylinder 3 is sleeved with a plugging component and a cylinder shell 20 from inside to outside, a second air cavity Y is formed between the cylinder 3 and the cylinder shell 20, a first air hole C which is communicated with the first air cavity and the second air cavity is arranged on the circumferential wall of the cylinder 3, a second air hole B which is communicated with the second air cavity and the third air cavity is arranged on the circumferential wall of the cylinder, one end of the plugging component is connected with the impact rod 12 to follow up, the second air hole B is kept open under the non-stress state that the impact rod 12 faces the impact hammer 15, and the plugging component and the impact hammer 15 alternately plug one of the air holes in a stroke range.
The optimized design is understood from function realization, and when the impact rod 12 is not pressed, namely the drill bit 11 connected to the outer end of the impact rod 12 is not contacted with a wall to be pressed, the first air hole C is blocked and the second air hole B is opened by the blocking component; at the moment, the second air hole B is communicated with the second air cavity and the third air cavity inside and outside the cylinder 3, so that a larger space is provided for containing air, and a third cavity between the piston and the impact hammer cannot form negative pressure, so that the impact hammer 15 cannot be driven to reciprocate by the reciprocating motion with smaller amplitude of the piston 17, and the self-hammering of the tool in a non-working state is avoided. When the impact rod 12 is pressed, the plugging component moves along with the impact rod, so that the first air hole C is opened and the second air hole B is plugged; at the moment, the first air hole C is communicated with the first air cavity and the second air cavity inside and outside the cylinder 3, so that a larger space is provided for accommodating air, only a smaller space is provided between the impact hammer 15 and the piston 17, the reciprocating motion of the piston 17 can generate larger thrust or suction to the impact hammer 15, namely a rear air spring is formed, and the impact hammer 15 continuously and periodically pushes the impact rod 12 to do work outwards; after the impact rod 12 is reset to the initial position, the blocking component blocks the first air hole C again and opens the second air hole B, and at this time, the next cycle can be continued. Of course, when the wall surface is drilled, the hammer and the pick are operated, the impact rod is continuously stressed and pressed inwards, and the second air hole B is less opened, so that the piston 17 can continuously and stably output thrust to the hammer, and the tool is prevented from breaking on the workbench. Therefore, the air cylinder shell is utilized to add air cavities and is combined with the sliding of the plugging component to isolate and release each air cavity to realize air pressure regulation and balance, the problems of the existing electric tool are solved, and the impact efficiency and the stability of the electric tool are improved.
Specifically, the ends of the cylinder 3 and the cylinder housing 20 away from the striking rod 12 are provided with a fixing cover 10 for close attachment, and a crankcase 21 is further provided outside the fixing cover 10. A crankshaft 23 is provided in the crankcase 21, and a connecting rod 22 is hinged to the piston 17 via a piston pin 19. The crankshaft 23 is hinged to the connecting rod 22. Thereby the crankshaft 23 in the crankcase 21 is driven to rotate by the power of the tool, and the transmission connecting rod 22 drives the piston 17 to reciprocate. The cylinder housing 20 is provided with a raised ring on the inner wall of the end near the impact rod. The bulge loop is established at cylinder 3 outer wall, and still is provided with first shock pad 1 and first gasket 2 in cylinder housing 20 outside the bulge loop. The drill 11 is connected to the impact rod 12, and outputs tool power to a construction object such as a wall surface. A second air chamber Y is formed between the cylinder 3 and the cylinder housing 20, a first air chamber X is formed between the striking rod 12 and the hammer 15 in the cylinder 3, and a third air chamber Z is formed between the hammer 15 and the piston 17 in the cylinder 3. The first air hole C is communicated with the first air cavity X and the second air cavity Y. The second air hole B communicates the second air chamber Y and the third air chamber Z. When the first air cavity X is communicated with the second air cavity Y and the second air cavity Y is separated from the third air cavity Z, the crank case 21 can drive the piston 17 to reciprocate and apply driving force to the impact hammer 15 through the third air cavity Z, and then the rear air spring is formed; after being driven, the impact hammer 15 transmits acting force to the impact rod 12, and the impact rod 12 transmits impact force to the drill bit 11, so that the hammer drilling operation is completed. When the second air cavity Y is communicated with the third air cavity Z, the reciprocating motion of the piston 17 in the relatively open third air cavity Z does not drive the punch hammer and the electric tool to do work externally as a whole.
As a key improvement for realizing air pressure self-balancing, the plugging assembly is composed of a distance cylinder 5, a first distance ring 6, a second distance ring 7, a special-shaped gasket 4 and an elastic part 8, and in order to reduce the abrasion of the elastic part 8 to the fixed sleeve 10, a second gasket 9 sleeved on the air cylinder 3 can be arranged at one end of the elastic part 8 far away from the second distance ring 7.
The peripheral wall of the cylinder 3 is provided with at least one sliding groove 40 parallel to the axial direction, and in the illustrated embodiment, two sliding grooves are oppositely arranged at two sides of the axial direction. The special-shaped gasket 4 is annular and is arranged in the cylinder 3 in a sliding manner. The inner ring of the special-shaped gasket 4 is sleeved on the impact rod 12 in the cylinder, and the bonding strength meets the requirement of integrated linkage. The special-shaped gasket 4 is also provided with a boss 41. The boss 41 extends out of the cylinder 3 through the slide groove 40, and on one hand, the boss moves back and forth along the slide groove 40 in a guiding mode, and on the other hand, the boss is in contact with the distance cylinder 5, and mutual transmission is achieved.
In order to facilitate the installation of the special-shaped gasket 4, the length of any one of the chutes 40 is larger than the outer diameter of the special-shaped gasket 4, as shown in fig. 3, during the installation, the surface of the special-shaped gasket 4 is parallel to the center of the cylinder 3 and is axially installed in the cylinder 3, then the special-shaped gasket 4 is turned over to be axially overlapped with the cylinder 3, and finally the impact rod 12 penetrates through the inner ring of the special-shaped gasket 4 to be sleeved and positioned, so that the forward partial assembly of the cylinder 3 is completed.
A step is provided in the cylinder 3. The faces of the steps can limit the maximum movement position of the profiled shim 4.
The distance cylinder 5 and the first distance ring 6 are sequentially sleeved outside the cylinder 3 from outside to inside, and the second distance ring 7 is also sleeved outside the cylinder 3 and arranged side by side with the first distance ring 6. The two end planes of the distance cylinder 5 are respectively contacted with the boss 41 of the special-shaped gasket 4 and the flanging of the first distance ring 6. Part of the first distance ring 6 is positioned in the distance cylinder 5 and mainly plays a role in plugging the first air hole C along with the displacement of the distance cylinder 5. The distance cylinder 5 plays a role of simultaneously supporting the shaped gasket 4 and the first distance ring 6, and plays a role of correcting the movement axes of the shaped gasket 4, the first distance ring 6 and the second distance ring 7 when reciprocating in the axial direction of the cylinder 3.
The distance cylinder 5 is provided with a plurality of vent holes D in at least one row. In the process that the cylinder 3 does work and does periodic reciprocating motion, the vent hole D can increase the limit of gas interaction between the first air cavity X and the second air cavity Y so as to relatively reduce the negative pressure change speed of the first air cavity X, so that the speed of pressure difference change of the front air spring and the rear air spring of the impact hammer 15 is reduced, the balance of the gas inside and outside the cylinder 3 is further optimized, and the problems of continuous impact, broken impact and the like of an electric tool (particularly a hammer and a pickaxe) are solved.
In the embodiment shown in fig. 3, the ventilation holes D are arranged in two rows along the circumference of the distance cylinder 5. The first distance ring 6 may close part of the ventilation holes D. The shape of the vent hole D has diversity and can be one or a combination of round holes, elliptical holes, kidney holes, triangular holes or polygonal holes.
The above-mentioned elastic element 8 is arranged between the second distance ring 7 and the fixing sleeve 10. Drill bit 11 can receive reaction force and kick-back when knocking the work piece, and this reaction force can transmit the instrument main part, and consequently, elastic component 8 can play the effect of buffering, effectively reduces the reaction force of transmitting the electric tool to the main part, makes the instrument operator obtain more comfortable operation experience, reduces intensity of labour. Simultaneously, when special-shaped gasket 4 receives axial thrust reciprocating motion, elastic component 4 can drive and circle timely follow motion apart from a section of thick bamboo 5, first distance circle 6 and second distance, improve electric tool's operating efficiency.
The elastic member 8 may be a compression spring sleeved outside the cylinder 3. The cylinder 3 is provided with a second gasket 9 at the fixing sleeve 10. The two ends of the compression spring are respectively pushed against the second distance ring 7 and the second gasket 9.
The crankcase 21 may further have a fourth air cavity W therein, the crankcase 21 has a third air hole E, and the fixing sleeve 10 has a fourth air hole F. The third air hole E and the fourth air hole F can be adjusted to communicate with each other when the electric tool is assembled, so that the second air chamber Y and the fourth air chamber W can communicate with each other. The gas in the second gas chamber Y is expanded due to the heat generated by the reciprocating motion of the ram 15 and the piston 17 in the cylinder 3. After the third air hole E and the fourth air hole F are communicated, the second air cavity Y is relatively increased, the bulging speed of air can be reduced, and therefore the internal air pressure can be well balanced.
The circumferential wall of the cylinder 3 is also provided with a compensation hole A. The compensation hole A can communicate the second air cavity Y and the third air cavity Z after the piston 17 passes by, so that the air exchange efficiency is improved.
In order to improve the sealing performance, a first O-ring 16 may be provided on the circumferential surface of the ram 15, and a second O-ring 18 may be provided on the circumferential surface of the piston 17.
In order to further absorb the reaction force of the drill bit 11, a third shim 13 and a second cushion 14 may be fitted around the striking rod 12 and flexibly abutted against the irregular shim 4.
In order to achieve the purpose that the second air hole B and the first air hole C are not simultaneously blocked for a long time, the sum of the axial length of the punch 15 and the lengths of the first distance ring 6 and the second distance ring 7 can be not larger than the maximum distance between the second air hole B and the first air hole C. Namely, at least one part of the two air holes keeps the communication state of the two related air cavities in the stroke range of the plugging component and the hammer. Further, the second air hole B and the first air hole C may be respectively provided with a row of holes spaced uniformly along the corresponding circumferential wall of the cylinder 3, as shown in fig. 3.
In view of the state change and the working principle realized by the air pressure self-balancing air cylinder structure. As shown in fig. 1, when the drill 11 is not pressed, the first distance ring 6 closes the first air hole C and the second distance ring 7 opens the second air hole B. The first air cavity X and the second air cavity Y are isolated to the maximum extent, the second air cavity Y is communicated with the third air cavity Z, the third air cavity Z cannot form negative pressure, and the reciprocating motion of the piston 17 cannot drive the punch hammer 15 to move, so that the self-hammering of the tool is avoided.
As shown in fig. 2, in the actual machining operation, the user applies a forward pressing force to the electric tool to press the drill bit 11 against the workpiece (for example, concrete), that is, the impact rod 12 is pressed, so that the drill bit 11 and the impact rod 12 move inward, and the irregular-shaped spacer 4, the distance cylinder 5, the first distance ring 6, and the second distance ring 7 are moved inward. At this time, the elastic member 8 is in a compressed state, and the shaped gasket 4 is at the maximum movement stroke position. The second distance ring 7 reaches the position for closing the second air hole B, the second air cavity Y is completely isolated from the third air cavity Z, negative pressure is easily formed in the third air cavity Z, and the reciprocating motion of the piston 17 drives the punch hammer 15 to move. And the first distance ring 6 gives way to the first air hole C, so that the first air cavity X is communicated with the second air cavity Y, and the hammer drill operation is facilitated.
In the actual machining operation, the electric power tool is in a state of periodic movement from fig. 1 to fig. 2 and from fig. 2 to fig. 1. In the process, the negative pressure of the first air cavity X is increased when the first air hole C starts to be closed, and the negative pressure of the third air cavity Z is reduced when the second air hole B is opened; on the contrary, the negative pressure of the first air cavity X is reduced when the air hole C is opened, and the negative pressure of the third air cavity Z is increased when the second air hole B is closed; the air interaction of the first air cavity X, the second air cavity Y and the third air cavity Z can be adjusted through the periodic movement of the vent hole D, the first distance ring 6 and the second distance ring 7 on the distance cylinder 5, and the purpose of balancing the front air spring and the rear air spring of the impact hammer 15 is achieved.
In summary, the air pressure self-balancing cylinder structure of the present invention is combined with the detailed description of the illustrated embodiment, and the present solution has the advantages of multiple aspects, and by optimizing the layout of the air cavities and the air hole plugging adjustability caused by the position change of the impact rod under different compression conditions, the air cavities in the cylinder and the cylinder shell can be freely switched between the isolated state and the open state to adjust the balanced air pressure. This scheme is made simply, the good reliability, can optimize the balance of the inside atmospheric pressure of cylinder, solves the problem of disconnected dashing, even dashing, self-hammering etc. improves electric tool's impact efficiency and stability, prolongs electric tool's life, and reaction force when alleviating the actual work promotes user operation and experiences.
In addition to the above embodiments, the present invention may have other embodiments, and any technical solutions formed by equivalent substitutions or equivalent transformations are within the scope of the present invention as claimed.
Claims (9)
1. A atmospheric pressure self-balancing cylinder structure for electric tool, wherein be equipped with in the cylinder in proper order along endwise slip's jump bit, impact hammer and piston, form first air cavity between impact hammer and the antecedent jump bit, form third air cavity, its characterized in that between impact hammer and the piston of backward: the cylinder structure comprises a plugging component and a cylinder shell which are sleeved outside the cylinder from inside to outside, a second air cavity is formed between the cylinder and the cylinder shell, a first air hole communicated with the first air cavity and the second air cavity is formed in the circumferential wall of the cylinder, a second air hole communicated with the second air cavity and the third air cavity is formed in the circumferential wall of the cylinder, the plugging component comprises a distance cylinder, a first distance ring, a second distance ring, a special-shaped gasket and an elastic part, wherein the special-shaped gasket is integrally sleeved with an impact rod in the cylinder and is provided with a boss penetrating through the cylinder and abutted against one end face of the distance cylinder, the first distance ring part is penetrated between the distance cylinder and the outer wall of the cylinder, and two sides of a flange of the first distance ring, which are far away from the first air hole, are abutted against the other end face of the distance cylinder and the second distance ring; the elastic piece is sleeved outside the cylinder, one end of the elastic piece pushes against the second distance ring, and the second distance ring opens or blocks the second air hole in the telescopic stroke of the elastic piece; the plugging component is connected with the impact rod to follow up, the second air hole is kept open when the impact rod faces the impact hammer and is not under stress, and the plugging component and the impact hammer alternately plug one of the air holes in a stroke range.
2. The air pressure self-balancing cylinder structure for power tools of claim 1, wherein: the distance cylinder is provided with at least one row of vent holes in the circumferential direction close to the special-shaped gasket.
3. The air pressure self-balancing cylinder structure for power tools of claim 1, wherein: the axial length of the punch hammer and the sum of the lengths of the first distance ring and the second distance ring are within the maximum distance range between the two air holes.
4. The air pressure self-balancing cylinder structure for power tools of claim 1, wherein: the elastic piece is a compression spring, a fixed sleeve which is connected in a sealing mode is arranged at one end, far away from the impact rod, of the air cylinder and the air cylinder shell, and one end, far away from the second distance ring, of the elastic piece abuts against the fixed sleeve.
5. The pneumatic self-balancing cylinder structure for power tools of claim 4, wherein: the cylinder is connected with a crankcase internally provided with a crankshaft at the outer side of the fixed sleeve, the piston is hinged with a connecting rod through a piston pin, and the crankshaft is in hinged transmission with the connecting rod.
6. The pneumatic self-balancing cylinder structure for power tools of claim 5, wherein: and a fourth air cavity is formed in the crankcase, the crankcase is provided with a third air hole, the fixing sleeve is provided with a fourth air hole, and the second air cavity is communicated with the fourth air cavity through the third air hole and the fourth air hole.
7. The air pressure self-balancing cylinder structure for power tools of claim 1, wherein: at least one sliding groove is formed in the circumferential wall of the air cylinder in parallel to the axial direction, and the boss of the special-shaped gasket penetrates out of the sliding groove, is mutually transmitted with the distance cylinder and slides along the sliding groove in a guiding mode.
8. The pneumatic self-balancing cylinder structure for power tools of claim 7, wherein: the length of the sliding groove is larger than the outer diameter of the special-shaped gasket.
9. The air pressure self-balancing cylinder structure for power tools of claim 1, wherein: the cylinder shell is provided with a convex ring which is sleeved with the outer wall of the cylinder on the inner wall of the end part close to the impact rod, a first shock pad is connected to the convex ring, and a third gasket and a second shock pad are sleeved on the impact rod.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111125403.5A CN113561342B (en) | 2021-09-26 | 2021-09-26 | Air pressure self-balancing cylinder structure for electric tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111125403.5A CN113561342B (en) | 2021-09-26 | 2021-09-26 | Air pressure self-balancing cylinder structure for electric tool |
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| US20140083728A1 (en) * | 2012-09-21 | 2014-03-27 | Black & Decker Inc. | Hammer dirll |
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| CN113561342A (en) | 2021-10-29 |
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