CN116000874A - Nail gun - Google Patents

Abstract

The invention discloses a nail gun, comprising: a housing formed with an accommodating space; a cylinder connected to the housing and for storing a gas; the firing assembly is at least partially arranged in the air cylinder and can move from an initial position to a firing position in the air cylinder to drive out nails; the power output part is arranged in the accommodating space formed by the shell and is used for outputting driving force to drive the firing assembly to move in the cylinder; the driving wheel is connected with the output shaft of the power output part and is used for driving the firing assembly to move in the cylinder under the drive of the power output part; wherein the driving wheel is provided with a first driving tooth and a second driving tooth; the tooth top of the first driving tooth is smaller than the tooth top of the second driving tooth; the first driving teeth are driving teeth arranged at the starting end of the driving wheel and meshed with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position. Provided is a nail gun which can prevent friction of parts caused by the rebound force of a firing pin and has a longer service life.

Description

Nail gun

Technical Field

The present invention relates to a nail gun.

Background

The principle modes of the existing nail gun products in the market can be divided into mechanical mode and air cylinder mode. Wherein the cylinder type nailing gun pushes out the percussion assembly through the gas in the cylinder to execute nailing action. The process of moving the firing assembly from the initial position to the firing position in the cylinder and then from the firing position to the initial position can be defined as a nailing cycle. Typically, after a staple is driven, the firing pin of the firing assembly will rebound a small distance due to the force of the rebound, causing the drive teeth of the firing pin to collide with the drive teeth of the drive wheel. Long times, the drive or transfer teeth will be severely worn, thereby affecting the service life of the machine.

Disclosure of Invention

In order to solve the defects in the prior art, the invention aims to provide a nailing gun with long service life of the whole machine.

In order to achieve the above object, the present invention adopts the following technical scheme:

a nail gun, comprising: a housing formed with an accommodating space; a cylinder connected to the housing and for storing a gas; the firing assembly is at least partially arranged in the cylinder and can move from an initial position to a firing position in the cylinder to drive out nails; a power output part, which is arranged in the accommodating space formed by the shell and is used for outputting driving force to drive the firing assembly to move in the cylinder; the driving wheel is connected with the output shaft of the power output part and is used for driving the firing assembly to move in the cylinder under the drive of the power output part; wherein the drive wheel has a first drive tooth and a second drive tooth; the tooth top of the first driving tooth is smaller than the tooth top of the second driving tooth; the first driving teeth are driving teeth arranged at the starting end of the driving wheel, and the first driving teeth are meshed with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position.

Further, the second drive teeth are drive teeth on the drive wheel other than the first drive teeth.

Further, a ratio of the tip of the first drive tooth to the tip of the second drive tooth is less than 1.

Further, a ratio of the tip of the first drive tooth to the tip of the second drive tooth is greater than or equal to 0.5 and less than 1.

Further, the firing assembly includes: a piston located within the cylinder; a striker fixed to the piston; the firing pin is provided with a plurality of transmission teeth to be meshed with the driving teeth of the driving wheel, and the firing pin is driven by the driving wheel to move in the cylinder.

Further, the distance from the piston to the plurality of transmission teeth sequentially comprises a first transmission tooth, a second transmission tooth and a third transmission tooth from the near to the far; the distance between the second transmission gear and the third transmission gear is smaller than the distance between the first transmission gear and the second transmission gear.

Further, defining a meshing length between drive teeth on the drive wheel other than the first drive tooth and drive teeth on the striker other than the second drive tooth; the tooth top of the first driving tooth and the tooth top of the second driving tooth have a first tooth top difference value; the ratio of the first tooth top difference to the meshing length is greater than or equal to 0.2 and less than or equal to 0.7.

Further, a ratio of a distance between the second gear tooth and the third gear tooth to a distance between the first gear tooth and the second gear tooth is less than 1.

Further, the tooth height of the second transmission tooth is smaller than the tooth height of the first transmission tooth or the tooth height of the third transmission tooth.

Further, the first transmission gear and the second transmission gear have a second tooth top difference value; the ratio of the second tooth tip difference to the engagement length is less than 1.

The invention has the advantages that: through reasonable adjustment of the driving force or the size or the distance of the upper teeth of the firing pin, the impact between the driving force and the firing pin can be effectively avoided when the firing pin rebounds after nailing, thereby ensuring the service life of the whole nailing gun.

Drawings

FIG. 1 is a perspective view of a stapling gun;

FIG. 2 is a cross-sectional view of the nailer of FIG. 1;

FIG. 3 is a schematic view of the power take-off of the nailer of FIG. 2;

FIG. 4 is an exploded view of the firing assembly of the staple gun of FIG. 2;

FIG. 5 is a cross-sectional view of the firing assembly of the staple gun of FIG. 2;

FIG. 6 is a schematic perspective view of the drive wheel of the nailer of FIG. 2;

FIG. 7a is a schematic illustration of the internal structure of the staple gun of FIG. 2 in a fired position;

FIG. 7b is another schematic illustration of the internal structure of the staple gun of FIG. 2 in a fired position;

fig. 8 is a schematic view of the firing pin of the stapling gun of fig. 2.

Detailed Description

The nail gun 100 shown in fig. 1 to 8 includes: a housing 11, a power take off 12, a cylinder 13, a cartridge clip assembly 14, a battery pack 15 and a firing assembly 16.

As shown in fig. 3, the power output section 12 includes: the motor 121, the gearbox 122, the non-return assembly 123, the output shaft 125 and the drive wheel 125. The motor 121 can output a power to the gearbox 122, and after the speed change of the gearbox 122, the motor continues to output a power to the output shaft 125, and the driving wheel 125 is disposed on the output shaft 125. Specifically, the motor 121, the gearbox 122, the non-return assembly 123, the output shaft 125 and the driving wheel 125 are all distributed along the first straight line 101. The transmission 122 is provided with a gear mechanism, and the check assembly 123 is provided in the transmission 122 at one end or the middle of the gear mechanism. As one implementation, the backstop assembly 123 allows the output shaft 125 to output only one driving force in a first rotational direction, while limiting rotation of the output shaft 125 in a second rotational direction opposite the first rotational direction.

As shown in fig. 4 and 5, firing assembly 16 includes a firing pin 161, a piston 162, and a metallic piece 163, wherein firing pin 161 is secured to metallic piece 163 and piston 162 is sleeved outside metallic piece 163. The metal part 163 is provided with a metal groove 1631, and the rubber ring 164 is sleeved on the metal groove 1631. The striker 161 has a transmission gear 161a formed thereon, both of which are movable in the cylinder 13 in the direction of the second straight line 102. The drive wheel 125 can cooperate with the drive teeth 161a to drive the firing assembly 16 to work against the air pressure in the air cylinder 13, thereby allowing the firing assembly 16 to be moved into the firing position.

As shown in fig. 1 and 2, the housing 11 includes a first receiving space 111 formed to extend in the direction of the first straight line 101 and a second receiving space 112 formed to extend in the direction of the second straight line 102. Wherein the power output portion 12 is disposed in the first accommodation space 111, and the cylinder 13 is disposed in the second accommodation space 112. The housing 11 is also formed with a grip portion 113 that can be held by a user. One end of the handle portion 113 is connected to a power interface for connecting to a dc power supply or an ac power supply. The grip portion 113 is provided with a main switch 113a, and a user controls the start and stop of the nail gun 100 through the main switch 113 a. In the present embodiment, a battery pack 15 is connected to the power supply interface. The other end of the handle portion 113 is connected to the cylinder 13, and the cylinder 13 extends in the direction of the second straight line 102, and the first straight line 101 and the second straight line 102 are perpendicular to each other. The cartridge clip assembly 14 is disposed in a third line 103 parallel to the first line 101. As an alternative embodiment, the cartridge clip assembly 14 is also provided with a window 141 through which the user can view the remaining nails. The window 141 is provided as one or more notches in the clip assembly 14 to allow a user to view the remainder of the nail on the one hand and to allow for easy maintenance of the clip assembly 14 without the user having to disassemble the clip assembly 14 on the other hand. The air cylinder 13 is internally provided with a firing assembly 16, and the air in the air cylinder 13 is used for doing work to push the firing assembly 16 to move to drive out nails. In this embodiment, the air cylinder 13 further includes an air charging nozzle, which is used for pre-charging air in the air cylinder 13, the power output portion 12 drives the driving wheel 17 to rotate so as to drive the firing assembly 16 to compress air to move from the initial position to the firing position, at this time, the air does work, and continuously pushes the firing assembly 16 to have an acceleration under the action of the pre-charging air, so that the firing assembly 16 drives nails with a larger kinetic energy, and after the nails are driven, the driving wheel is rapidly moved from the firing position to the initial position, thereby completing a nailing cycle.

It will be appreciated that as the firing assembly 16 ejects the staples, the firing assembly 16 may rebound a small distance upward from the striking position due to the rebound force of the striker. Impact between the firing pin 161 and the drive wheel 125 can occur during rebound of the firing assembly 16, thereby wearing out the drive teeth of the drive wheel 125 and/or the drive teeth on the firing pin 161. In order to solve the above problem, the present application optimizes the structure of the driving wheel 125 and/or the striker 161, so as to avoid the abrasion of the driving teeth and the driving teeth caused by the impact of the driving wheel 125 when the striker 161 rebounds.

In particular, as shown in fig. 6, the drive wheel 125 is a gear structure. The driving wheel 125 is also formed with a coupling hole 125a to which the output shaft 125 is coupled. The connection hole 125a is specifically a flat hole, and when the output shaft 125 is connected to the connection hole 125a, the driving wheel 125 can rotate synchronously with the output shaft 125. A plurality of drive teeth 125g are formed around the main body portion of the drive wheel 125, the drive teeth 125g including a first drive tooth 125b provided at the start end and other drive teeth 125g except for the first drive tooth 125 b. The drive teeth on the drive teeth 125 that are outside of the first drive teeth 125b are referred to herein as second drive teeth. Here, the driving tooth 125g that is in contact with the firing pin 161 of the firing assembly 16 first when the driving wheel 125 starts to drive the firing assembly 16 to the initial position is the first driving tooth 125b, and the driving teeth other than the first driving tooth 125b are the second driving teeth 125d. The first drive teeth 125b and the second drive teeth 125d are evenly distributed over the first section 125e of the drive wheel 125; the second section 125f of the drive wheel 125 is smooth and continuous and is not distributed with drive teeth 125g. As shown in fig. 7a and 7b, when the drive teeth 125g of the first section 125e engage the drive teeth 161a on the striker 161, the drive wheel 125 can drive the striker 161 to compress the gas in the cylinder 13 to perform work. More specifically, as the first drive tooth 125b on the first section 125e begins to engage the drive tooth 161a on the striker 161, the drive wheel 125 begins to drive the striker 161 to push the gas in the piston compression cylinder 13 to perform work. When the second section 125f is mated with the striker 161, since the second section 125f is smooth and continuous, the striker 161 is rapidly pushed out by the gas in the cylinder 13 without the drive teeth 125g being stopped, thereby achieving a nailing effect.

It will be appreciated that the striker 161 is formed on one side by a gear tooth 161a, the gear tooth 161a being engageable with the drive tooth 125g of the drive wheel 125, such that the striker 161 is capable of driving the piston to compress the gas in the cylinder to perform work upon actuation of the drive wheel 125.

In one embodiment, as shown in FIG. 6, the top H1 of the first drive tooth 125b of the drive wheel 125 is smaller than the top H2 of the second drive tooth 125d. Where H1 and H2 are heights indicated by bold solid lines in FIG. 6. In addition, as is apparent from the diameters of the first ring gear C1 and the second ring gear C2 in which the first drive teeth 125b are located in fig. 6, the tooth tops of the first drive teeth 125b are significantly smaller than those of the second drive teeth 125d. In a preferred implementation, the ratio of the tip H1 of the first drive tooth 125b to the tip H2 of the second drive tooth 125d is less than 1. Preferably, the ratio of H1 to H2 is greater than or equal to 0.5 and less than 1. By reducing the height of the tooth top H1 of the first driving tooth 125b, when the striker 161 moves upward due to the rebound force, the impact force of the driving tooth 161a on the first driving tooth 125b is greatly reduced, thereby reducing the wear degree between the striker 161 and the driving wheel 125 and avoiding the influence on the service life of the whole machine due to friction between the striker 161 and the driving wheel 125.

As shown in fig. 7a, when the striker 161 moves upward due to the repulsive force, the first driving tooth 125b cannot be engaged with the driving tooth 161a or the length of engagement of both teeth is small. Further, as shown in fig. 7b, the second driving teeth 125d are engaged with the driving teeth 161a by a relatively long engagement length.

In one embodiment, the tip of the first drive tooth 125b has a certain first tip difference from the tip of the second drive tooth 125 d; there is a certain length of engagement between the drive teeth on the drive wheel 125 other than the first drive tooth 125b and the drive teeth on the striker 161 other than the second drive tooth 1613. In one embodiment, a ratio of the first tooth top difference to the engagement length is greater than or equal to 0.2 and less than or equal to 0.7. In an example, the ratio of the first tooth tip difference value to the meshing length is 0.2, 0.3, 0.4, 0.5, 0.6, or 0.7. In one embodiment, as shown in FIG. 8, the gear teeth 161a of the striker 161 are defined as a first gear tooth 1612, a second gear tooth 1613, a third gear tooth 1614, etc., in that order, depending on the distance of the gear teeth 161a from the piston 162. It will be appreciated that during movement of the firing pin 161 from the firing position to the initial position, the first drive tooth 1612 initially engages the first drive tooth 125b of the drive wheel 125. That is, if the striker 161 is moved upward by the repulsive force after nailing, the second transmission teeth 1613 first collide with the first driving teeth 125 b. In one implementation, the distance between the first gear tooth 1612 and the second gear tooth 1613 may be increased. For example, assuming that the distance between the first gear 1612 and the second gear 1613 of the striker 161 is S1 and the distance between the second gear 1613 and the third gear 1614 is S2, S1 is greater than S2. Optionally, the distance between the adjacent teeth 161a is S2, except for the first tooth 1612 and the second tooth 1613. By increasing the distance between the first gear 1612 and the second gear 1613, during rebound after the firing pin 161 is nailed, the rebound force is converted into a driving force for driving the firing pin 161 to move during the distance S1 of the movement of the firing pin 161 and is consumed, thereby avoiding or reducing the impact force between the driving wheel 125 and the firing pin 161. In a preferred implementation, the ratio of S1 to S2 is less than 1. Preferably, the ratio of S1 to S2 is greater than or equal to 0.5 and less than 1. In one embodiment, the distance between the first gear 1612 and the second gear 1613 may be increased depending on the amount of pressure within the cylinder 13. Illustratively, the greater the pressure within the cylinder 13, the greater the distance S1 between the first and second drive teeth 1612, 1613 that are provided. It will be appreciated that S1 is related to the tooth thickness of the drive teeth of striker 161 or the modulus of the gear, in addition to the pressure in cylinder 13.

In one embodiment, the tooth height H3 of the second gear tooth 1613 of the striker 161 may be reduced, i.e., the tooth height of the second gear tooth 1613 is less than the tooth height of the first gear tooth 1612 or the tooth height of the third gear tooth 1614. Alternatively, the tooth height of the second gear 1613 is the gear having the smallest tooth height among all the gears 161 a. During rebound after the firing pin 161 is nailed, the rebound force drives the firing pin 161 upward, and the first drive tooth 125b may collide or not contact with the second drive tooth 1613 during the upward movement of the firing pin 161 due to the smaller size. If the first driving tooth 125b is not in contact with the second driving tooth 1613 during the upward movement of the striker 161, the impact force between the first driving tooth 125b and the third driving tooth 1614 will be greatly reduced after the rebound force drives the striker to move a distance S3. The distance S3 is the distance between the first gear 1612 and the third gear 1614, i.e., s3=s1+s2. If the first driving tooth 125b and the second moving tooth 1613 with lower tooth height strike the striker 161 during the upward movement, the striking force will not cause greater abrasion to the driving wheel 125, and the range will be greater, and the rebound force will be dropped in a lower efficiency, so as to avoid the impact force between the first driving tooth 125b and the third driving tooth 1614 for the second time, which affects the service lives of the driving wheel 125 and the striker 161.

That is, by lowering the height of the second gear 1613, the increased amount of the recoil force causes the striker 161 to move a distance between the first gear 1612 and the third gear 1614. Thereby avoiding or reducing the force of impact between the first drive tooth 125b of the drive wheel 125 and the first drive tooth 1612 of the striker 161.

In an alternative implementation, the ratio of the tip height H3 of the second drive teeth 1613 to the tip height H1 of the first drive teeth 125b is less than 1. It will be appreciated that the tooth top height H4 of the second drive teeth 1613 may be set based on the tooth top height H1 of the first drive teeth 125b, only to ensure that the striker 161 is able to strike less force between the second drive teeth 1613 and the first drive teeth 125 b. That is, as striker 161 rebounds upward, second drive tooth 1613 may also have a degree of impact with first drive tooth 125b that is small enough that it does not cause significant wear between the drive and/or drive teeth.

In one embodiment, there is a second tooth top differential between the first gear 1612 and either the second gear 1613 or the fourth gear 1514, the ratio of the tooth top differential to the engagement length being less than 1. In the example, the ratio of the second tooth tip difference value to the engagement length is 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, or the like.

In one embodiment, the motor speed change may also be controlled by a controller of the motor. For example, the controller may control the motor to reduce the rotational speed during movement of the drive wheel 125 to drive the firing pin 161 from the initial position to the firing position, or reduce the motor rotational speed during movement of the drive wheel 126 to drive the firing pin 161 from the initial position to the firing position and begin to rise from the firing position to the initial position. In short, the motor rotation speed can be reduced during the period when the striker 161 is about to move upward or has moved upward, so that the force of the striker 161 bouncing up and down can be reduced.

In one embodiment, a combination of one or more approaches may be used to reduce the impact force of the drive wheel 125 and striker 161.

It will be appreciated that the greater the weight of the firing assembly 16, the more work is done by the compressed gas in the cylinder 13 to overcome the inertial work of the firing assembly 16 itself, and thus the striking force will be greatly reduced. That is, the greater the weight of firing assembly 16, i.e., piston 162 and firing pin 161, the less effective the stapling of the stapling gun.

The stapling effect of the stapling gun can thus be enhanced by reducing the weight of the firing assembly 16 of the present application. Alternatively, the striker 161 may be made of a lighter but harder material, or the piston may be made of a lighter, more impact resistant material.

For example, the middle portion of the metallic member 163 shown in FIGS. 4 and 5 may be hollowed out to reduce the weight of the metallic member 163 and thus the weight of the firing assembly 16.

The foregoing has shown and described the basic principles, principal features and advantages of the invention. It will be appreciated by persons skilled in the art that the above embodiments are not intended to limit the invention in any way, and that all technical solutions obtained by means of equivalent substitutions or equivalent transformations fall within the scope of the invention.

Claims (10)

1. A nail gun, comprising:

a housing formed with an accommodating space;

a cylinder connected to the housing and for storing a gas;

the firing assembly is at least partially arranged in the cylinder and can move from an initial position to a firing position in the cylinder to drive out nails;

a power output part, which is arranged in the accommodating space formed by the shell and is used for outputting driving force to drive the firing assembly to move in the cylinder;

the driving wheel is connected with the output shaft of the power output part and is used for driving the firing assembly to move in the cylinder under the drive of the power output part;

it is characterized in that the method comprises the steps of,

the drive wheel has a first drive tooth and a second drive tooth;

the tooth top of the first driving tooth is smaller than the tooth top of the second driving tooth;

the first driving teeth are driving teeth arranged at the starting end of the driving wheel, and the first driving teeth are meshed with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position.

2. The nail gun of claim 1, wherein the nail gun comprises a nail gun,

the second drive teeth are drive teeth on the drive wheel other than the first drive teeth.

3. The nail gun of claim 1, wherein the nail gun comprises a nail gun,

the ratio of the tooth top of the first drive tooth to the tooth top of the second drive tooth is less than 1.

4. The nail gun of claim 1, wherein the nail gun comprises a nail gun,

the ratio of the tooth top of the first drive tooth to the tooth top of the second drive tooth is greater than or equal to 0.5 and less than 1.

5. The nail gun of claim 1, wherein the nail gun comprises a nail gun,

the firing assembly includes:

a piston located within the cylinder;

a striker fixed to the piston;

the firing pin is provided with a plurality of transmission teeth to be meshed with the driving teeth of the driving wheel, and the firing pin is driven by the driving wheel to move in the cylinder.

6. The nail gun of claim 5, wherein the nail gun comprises a nail gun,

the distance from the piston to the plurality of transmission teeth sequentially comprises a first transmission tooth, a second transmission tooth and a third transmission tooth from the near to the far;

the distance between the second transmission gear and the third transmission gear is smaller than the distance between the first transmission gear and the second transmission gear.

7. The nail gun of claim 6, wherein the nail gun comprises a nail gun,

defining a certain meshing length between a driving tooth of the driving wheel except the first driving tooth and a driving tooth of the firing pin except the second driving tooth;

the tooth top of the first driving tooth and the tooth top of the second driving tooth have a first tooth top difference value;

the ratio of the first tooth top difference to the meshing length is greater than or equal to 0.2 and less than or equal to 0.7.

8. The nail gun of claim 6, wherein the nail gun comprises a nail gun,

the ratio of the distance between the second and third drive teeth to the distance between the first and second drive teeth is less than 1.

9. The nail gun of claim 6, wherein the nail gun comprises a nail gun,

the tooth height of the second transmission tooth is smaller than the tooth height of the first transmission tooth or the tooth height of the third transmission tooth.

10. The nail gun of claim 7, wherein the nail gun comprises a nail gun,

the first transmission gear and the second transmission gear have a second tooth top difference value;

the ratio of the second tooth tip difference to the engagement length is less than 1.

Images