Nail gun

Abstract

The application discloses a nail gun, comprising: a shell formed with a containing space; a cylinder connected to the shell and used for storing gas; a firing assembly at least partially arranged in the cylinder and capable of moving in the cylinder from an initial position to a firing position to shoot a nail; a power output part arranged in the containing space of the shell and used for outputting driving force to drive the firing assembly to move in the cylinder; and a driving wheel connected with an output shaft of the power output part and used for driving the firing assembly to move in the cylinder under the driving of the power output part; wherein the driving wheel is provided with first driving teeth and second driving teeth; the addendum of the first driving teeth is smaller than that of the second driving teeth; the first driving teeth are driving teeth arranged at the starting end of the driving wheel, and the first driving teeth are engaged with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position. The nail gun can avoid the friction of parts caused by the rebounding force of the hammer and has a longer service life.

Description

TECHNICAL FIELD

[0001] The present application relates to a nail gun. BACKGROUND

[0002] The existing nail gun products on the market can be divided into mechanical type and cylinder type in principle. The cylinder type nail gun pushes out the firing assembly to perform the nailing action through the gas in the cylinder. The process that the firing assembly moves from the initial position in the cylinder to the firing position and then moves from the firing position to the initial position can be defined as a nailing cycle. Generally, after the nail is driven out, the striker of the firing assembly will rebound a small distance due to the rebounding force, so that the driving teeth of the striker will collide with the driving teeth of the driving wheel. Over time, the driving teeth or the transmission teeth will be severely worn, thereby affecting the service life of the machine. SUMMARY

[0003] To solve the problems of the prior art, the purpose of the present application is to provide a nail gun with high service life.

[0004] In order to achieve the above-mentioned goal, the present application adopts the following technical scheme:

[0005] A nail gun, comprising: a housing formed with a containing space; a cylinder connected to the housing and used for storing gas; a firing assembly at least partially disposed in the cylinder and capable of moving from an initial position to a firing position in the cylinder to drive out a nail; a power output portion disposed in the containing space formed by the housing and used for outputting driving force to drive the firing assembly to move in the cylinder; a driving wheel connected with an output shaft of the power output portion and used to drive the firing assembly to move in the cylinder under the driving of the power output portion; wherein the driving wheel has 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 tooth is a driving tooth disposed at the starting end of the driving wheel, and the first driving tooth is engaged with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position.

[0006] Further, the second driving tooth is a driving tooth on the driving wheel other than the first driving tooth.

[0007] Further, the ratio of the tooth top of the first driving tooth to the tooth top of the second driving tooth is less than 1.

[0008] Further, the ratio of the tooth top of the first driving tooth to the tooth top of the second driving tooth is greater than or equal to 0.5 and less than 1.

[0009] Further, the firing assembly comprises: a piston located in the cylinder; a striker fixed on the piston; a plurality of transmission teeth are arranged on the striker to mesh with the drive teeth of the drive wheel, and the striker moves in the cylinder under the drive of the drive wheel.

[0010] Further, the distance of the plurality of transmission teeth from the piston includes the first transmission tooth, the second transmission tooth and the third transmission tooth from near to far; the distance between the second transmission tooth and the third transmission tooth is smaller than the distance between the first transmission tooth and the second transmission tooth.

[0011] Further, a certain meshing length is defined between the drive teeth of the drive wheel except the first drive tooth and the transmission teeth of the striker except the second transmission tooth; the addendum of the first drive tooth and the addendum of the second drive tooth have a first addendum difference; the ratio of the first addendum difference to the meshing length is greater than or equal to 0.2 and less than or equal to 0.7.

[0012] Further, the ratio of the distance between the second transmission tooth and the third transmission tooth to the distance between the first transmission tooth and the second transmission tooth is less than 1.

[0013] 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.

[0014] Further, the first transmission tooth and the second transmission tooth have a second addendum difference; the ratio of the second addendum difference to the meshing length is less than 1.

[0015] The present application has the advantages that: by reasonably adjusting the driving force or the size or distance of the teeth on the striker, the impact between the driving force and the striker when the striker rebounds after driving the nail can be effectively avoided, thereby ensuring the service life of the nail gun. BRIEF DESCRIPTION OF DRAWINGS

[0016] Figure 1 is a perspective view of a nail gun;

[0017] Figure 2 is a sectional view of the nail gun in Figure 1 ;

[0018] Figure 3 is a power output structure schematic view of the nail gun in Figure 2 ;

[0019] Figure 4 is an exploded view of the firing assembly of the nail gun in Figure 2 ;

[0020] Figure 5 is a sectional view of the firing assembly of the nail gun in Figure 2 ;

[0021] Figure 6 is Figure 2 a perspective view of the driving wheel of the nail gun in the nail gun 100;

[0022] Figure 7a is Figure 2 a schematic view of the internal structure of the nail gun in the nail gun 100 in the firing position;

[0023] Figure 7b is Figure 2 another schematic view of the internal structure of the nail gun in the nail gun 100 in the firing position;

[0024] Figure 8 is Figure 2 a schematic view of the structure of the firing pin of the nail gun in the nail gun 100. DETAILED DESCRIPTION

[0025] Figures 1 to 8 The nail gun 100 shown includes a housing 11, a power output 12, a cylinder 13, a cartridge assembly 14, a battery pack 15 and a firing assembly 16.

[0026] As shown in Figure 3 , the power output 12 includes a motor 121, a gearbox 122, a reverse prevention assembly 123, an output shaft 125 and a driving wheel 125. The motor 121 can output a power to the gearbox 122, which continues to output a power to the output shaft 125 after the speed change of the gearbox 122, and the driving wheel 125 is arranged on the output shaft 125. Specifically, the motor 121, the gearbox 122, the reverse prevention assembly 123, the output shaft 125 and the driving wheel 125 are distributed along the first straight line 101 direction. The gearbox 122 is provided with a speed change mechanism, and the reverse prevention assembly 123 is arranged in the gearbox 122 and at one end or in the middle of the speed change mechanism. As an implementation manner, the reverse prevention assembly 123 makes the output shaft 125 only output a driving force in the first rotation direction, and restricts the rotation of the output shaft 125 in the second rotation direction opposite to the first rotation direction.

[0027] As shown in Figure 4 and Figure 5 , the firing assembly 16 includes a firing pin 161, a piston 162 and a metal piece 163, wherein the firing pin 161 is fixed on the metal piece 163, and the piston 162 is sleeved outside the metal piece 163. A metal groove 1631 is arranged on the metal piece 163, and a rubber ring 164 is sleeved on the metal groove 1631. The firing pin 161 is formed with a transmission tooth 161a, and the two can move in the second straight line 102 direction in the cylinder 13. The driving wheel 125 can cooperate with the transmission tooth 161a to drive the firing assembly 16 to overcome the gas pressure in the cylinder 13 to work, so that the firing assembly 16 can enter into the firing position.

[0028] AsFigure 1 and 2 As shown in FIG. 1, the housing 11 includes a first accommodating space 111 extending along a first straight line 101 and a second accommodating space 112 extending along a second straight line 102. The power output part 12 is arranged in the first accommodating space 111, and the air cylinder 13 is arranged in the second accommodating space 112. The housing 11 further includes a handle part 113 for a user to hold. One end of the handle part 113 is connected with a power interface for connecting a direct current power source or an alternating current power source. A main switch 113a is arranged on the handle part 113, and a user controls the start and stop of the nail gun 100 through the main switch 113a. In the embodiment, the power interface is connected with a battery pack 15. The other end of the handle part 113 is connected with the air cylinder 13, and the air cylinder 13 extends along the second straight line 102. The first straight line 101 and the second straight line 102 are perpendicular to each other. The clip assembly 14 is arranged along a third straight line 103 parallel to the first straight line 101. As an optional embodiment, the clip assembly 14 is further provided with a window 141 for a user to observe the remaining nails. The window 141 is arranged as one or more notches on the clip assembly 14, which can be used for a user to check the remaining nails and can also be used for simple maintenance of the clip assembly 14 without disassembling the clip assembly 14. The firing assembly 16 is arranged in the air cylinder 13, and the firing assembly 16 is driven to move by the gas in the air cylinder 13. In the embodiment, the air cylinder 13 further includes an air charging nozzle for pre-charging gas in the air cylinder 13. The power output part 12 drives the driving wheel 17 to rotate and further drives the firing assembly 16 to compress the gas from an initial position to a firing position. At this time, the gas does work and continuously drives the firing assembly 16 to have an acceleration under the action of the pre-charged gas, so that the firing assembly 16 hits the nail with a large kinetic energy and quickly moves from the firing position to the initial position after hitting the nail, thereby completing a nail hitting cycle.

[0029] It can be understood that, when the firing assembly 16 hits the nail, the rebounding force of the striker can make the firing assembly 16 rebound a small distance upward from the hitting position. The rebounding of the firing assembly 16 can cause the impact between the striker 161 and the driving wheel 125, thereby causing the abrasion of the driving teeth of the driving wheel 125 and / or the transmission teeth on the striker 161. In order to solve the above problem, the structure of the driving wheel 125 and / or the striker 161 is optimized in the application, so as to avoid the abrasion of the driving teeth and the transmission teeth caused by the impact of the striker 161 rebounding on the driving wheel 125.

[0030] In a specific implementation, as Figure 6As shown, the driving wheel 125 is a gear structure. The driving wheel 125 is further formed with a connecting hole 125a for connecting the output shaft 125. The connecting hole 125a is a flat hole. When the output shaft 125 is connected to the connecting hole 125a, the driving wheel 125 can rotate synchronously with the output shaft 125. A plurality of driving teeth 125g are formed around the main body of the driving wheel 125. The driving teeth 125g include a first driving tooth 125b arranged at the starting end and other driving teeth 125g except the first driving tooth 125b. In this application, the driving teeth 125g except the first driving tooth 125b are collectively referred to as second driving teeth. Here, the first driving tooth 125b is the driving tooth 125g that first contacts the firing pin 161 in the firing assembly 16 when the driving wheel 125 starts to drive the firing assembly 16 to reset to the initial position. The other driving teeth except the first driving tooth 125b are the second driving teeth 125d. The first driving tooth 125b and the second driving tooth 125d are uniformly distributed in the first section 125e of the driving wheel 125. The second section 125f of the driving wheel 125 is smooth and continuous and does not have driving teeth 125g distributed therein. As shown in Figure 7a and Figure 7b When the driving teeth 125g of the first section 125e engage with the transmission teeth 161a on the firing pin 161, the driving wheel 125 can drive the firing pin 161 to compress the gas in the cylinder 13 to do work. More specifically, when the first driving tooth 125b on the first section 125e starts to engage with the transmission teeth 161a on the firing pin 161, the driving wheel 125 starts to drive the firing pin 161 to push the piston to compress the gas in the cylinder 13 to do work. When the second section 125f cooperates with the firing pin 161, since the second section 125f is smooth and continuous, the firing pin 161 will be quickly pushed out by the gas in the cylinder 13 without being stopped by the driving teeth 125g, thereby achieving the effect of driving nails.

[0031] It can be understood that one side of the firing pin 161 is distributed by the transmission teeth 161a, which can engage with the driving teeth 125g of the driving wheel 125, so that the firing pin 161 can drive the piston to compress the gas in the cylinder under the driving of the driving wheel 125.

[0032] In one embodiment, as shown in Figure 6 the tooth top H1 of the first driving tooth 125b of the driving wheel 125 is smaller than the tooth top H2 of the second driving tooth 125d. Wherein, H1 and H2 are Figure 6 the heights represented by the thick solid lines in the figure. In addition, from Figure 6The diameters of the first gear ring C1 and the second gear ring C2 where the first driving tooth 125b is located can also be clearly seen. The addendum of the first driving tooth 125b is obviously smaller than the addendum of the second driving tooth 125d. In a preferred implementation, the ratio of the addendum H1 of the first driving tooth 125b to the addendum H2 of the second driving 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 addendum H1 of the first driving tooth 125b, the impact force of the driving tooth 161a on the first driving tooth 125b when the striker 161 moves upward due to the rebound force will be greatly reduced, thereby reducing the degree of wear between the two and avoiding the impact of the service life of the entire machine due to the friction between the striker 161 and the driving wheel 125.

[0033] As shown in FIG. 7, when the striker 161 moves upward due to the rebound force, the first driving tooth 125b and the driving tooth 161a cannot be engaged or the length of engagement between the two teeth is small. Figure 7a As shown in FIG. 7, when the striker 161 moves upward due to the rebound force, the first driving tooth 125b and the driving tooth 161a cannot be engaged or the length of engagement between the two teeth is small. Figure 7b As shown in FIG. 7, when the striker 161 moves upward due to the rebound force, the first driving tooth 125b and the driving tooth 161a cannot be engaged or the length of engagement between the two teeth is small.

[0034] In one embodiment, the addendum of the first driving tooth 125b and the addendum of the second driving tooth 125d have a certain first addendum difference; the driving teeth on the driving wheel 125 other than the first driving tooth 125b and the driving teeth on the striker 161 other than the second driving tooth 1613 have a certain length of engagement. In one embodiment, the ratio of the above-mentioned first addendum difference to the above-mentioned length of engagement is greater than or equal to 0.2 and less than or equal to 0.7. For example, the ratio of the above-mentioned first addendum difference to the above-mentioned length of engagement is 0.2, 0.3, 0.4, 0.5, 0.6, 0.7. In one embodiment, as shown in FIG. 7, the ratio of the addendum H1 of the first driving tooth 125b to the addendum H2 of the second driving tooth 125d is 0.5. Figure 8As shown, the drive teeth 161a of the striker 161 are defined as a first drive tooth 1612, a second drive tooth 1613, and a third drive tooth 1614, and so on, according to the distance between the drive teeth 161a and the piston 162. It can be understood that the first drive tooth 1612 is first engaged with the first drive tooth 125b of the driving wheel 125 during the movement of the striker 161 from the firing position to the initial position. That is, when the striker 161 moves upward due to the rebound force after driving a nail, the second drive tooth 1613 is first engaged with the first drive tooth 125b. In an implementation, the distance between the first drive tooth 1612 and the second drive tooth 1613 can be increased. For example, assuming that the distance between the first drive tooth 1612 and the second drive tooth 1613 of the striker 161 is S1, and the distance between the second drive tooth 1613 and the third drive tooth 1614 is S2, S1 is greater than S2. Alternatively, the distance between the other adjacent drive teeth 161a, except the first drive tooth 1612 and the second drive tooth 1613, is S2. By increasing the distance between the first drive tooth 1612 and the second drive tooth 1613, the rebound force is converted into driving force to drive the striker 161 to move during the movement of the striker 161 by a distance of S1, so as to avoid or reduce the impact force between the driving wheel 125 and the striker 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 an embodiment, the distance between the first drive tooth 1612 and the second drive tooth 1613 can be increased according to the pressure in the cylinder 13. For example, the greater the pressure in the cylinder 13, the greater the distance S1 between the first drive tooth 1612 and the second drive tooth 1613. It can be understood that S1 is related to the pressure in the cylinder 13, and is also related to the tooth thickness of the drive teeth of the striker 161 or the module of the gear.

[0035] In one embodiment, the height H3 of the second driving tooth 1613 of the striker 161 can be reduced, i.e. the height of the second driving tooth 1613 is smaller than the height of the first driving tooth 1612 or the third driving tooth 1614. Alternatively, the height H3 of the second driving tooth 1613 is the smallest among all the driving teeth 161a. During the rebounding of the striker 161 after driving a nail, the rebounding force drives the striker 161 to move upward. Since the second driving tooth 1613 is smaller, the first driving tooth 125b can collide with the second driving tooth 1613 or not contact the second driving tooth 1613 during the upward movement of the striker 161. If the first driving tooth 125b does not contact 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 striker 161 is driven by the rebounding force to move a distance S3, where the distance S3 is the distance between the first driving tooth 1612 and the third driving tooth 1614, i.e. S3=S1+S2. If the first driving tooth 125b collides with the second driving tooth 1613 with a smaller height during the upward movement of the striker 161, the impact force will not cause great wear of the driving wheel 125, and the rebounding force will be greatly reduced in a large range, so as to avoid a second impact between the first driving tooth 125b and the third driving tooth 1614, and affect the service life of the driving wheel 125 and the striker 161.

[0036] That is, by reducing the height of the second driving tooth 1613, the distance that the striker 161 can be driven by the rebounding force is increased, and the distance is the distance between the first driving tooth 1612 and the third driving tooth 1614. Thus, the impact force between the first driving tooth 125b of the driving wheel 125 and the first driving tooth 1612 of the striker 161 is avoided or reduced.

[0037] In an alternative embodiment, the ratio of the tooth top height H3 of the second driving tooth 1613 to the tooth top height H1 of the first driving tooth 125b is less than 1. It can be understood that the tooth top height H4 of the second driving tooth 1613 can be set according to the tooth top height H1 of the first driving tooth 125b, as long as the impact force between the second driving tooth 1613 and the first driving tooth 125b is small enough for the striker 161 to move. That is, when the striker 161 rebounds upward, the second driving tooth 1613 can have a certain impact force with the first driving tooth 125b, as long as the impact force is small enough to avoid great wear between the driving teeth and / or the driving teeth.

[0038] In one embodiment, the first driving tooth 1612 and the second driving tooth 1613 or the fourth driving tooth 1514 have a second tooth top difference, and the ratio of the second tooth top difference to the meshing length is less than 1. For example, the ratio of the second tooth top difference to the meshing length is 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, etc.

[0039] In one embodiment, the motor speed can also be controlled by a motor controller. For example, during the process of the drive wheel 125 driving the firing pin 161 from the initial position to the firing position, the controller reduces the motor speed; or, when the drive wheel 126 drives the firing pin 161 from the initial position to the firing position and begins to rise from the firing position back to the initial position, the motor speed is reduced. In short, the motor speed can be reduced during the process of the firing pin 161 about to move upwards or already moving upwards, thereby reducing the force of the upward and downward rebound of the firing pin 161.

[0040] In one embodiment, one or more methods in combination can be used to reduce the impact force of the drive wheel 125 and the striker 161.

[0041] Understandably, the heavier the firing assembly 16, the more work the compressed gas in the cylinder 13 will do to overcome the inertia of the firing assembly 16 itself, thus greatly reducing the striking force. In other words, the heavier the firing assembly 16, i.e., the piston 162 and the firing pin 161, the worse the nail-driving effect of the nail gun.

[0042] Therefore, the nailing effect of the nail gun can be improved by reducing the weight of the firing assembly 16. Alternatively, the firing pin 161 can be made of a lighter but harder material, or the piston can be made of a lighter material with better impact resistance.

[0043] Examples can be such as Figure 4 and Figure 5 The middle part of the metal part 163 shown is hollowed out to reduce the weight of the metal 163, thereby reducing the weight of the firing assembly 16.

[0044] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the above embodiments do not limit the present invention in any way, and all technical solutions obtained by equivalent substitution or equivalent transformation fall within the protection scope of the present invention.

Claims

1. A nail gun, comprising: a housing formed with a receiving space; a cylinder connected to the housing and configured to store gas; a firing assembly disposed at least partially within the cylinder and configured to move within the cylinder from an initial position to a firing position to eject a nail; a power output disposed within the receiving space of the housing and configured to output a driving force to drive the firing assembly to move within the cylinder; a driving wheel connected to an output shaft of the power output and configured to be driven by the power output to drive the firing assembly to move within the cylinder; characterized in that: the driving wheel has a first driving tooth and a second driving tooth; a tip of the first driving tooth is smaller than a tip of the second driving tooth; the first driving tooth is a driving tooth disposed at a starting end of the driving wheel, and the first driving tooth is engaged with the firing assembly when the driving wheel starts to drive the firing assembly to reset to the initial position; the firing assembly comprises: a piston located within the cylinder; a striker fixed to the piston; a plurality of driving teeth are provided on the striker and configured to be engaged with the driving teeth of the driving wheel to move within the cylinder under the driving of the driving wheel; the distances of the plurality of driving teeth from the piston include a first driving tooth, a second driving tooth, and a third driving tooth in order from near to far; a distance between the second driving tooth and the third driving tooth is smaller than a distance between the first driving tooth and the second driving tooth. 2.The nail gun according to claim 1, characterized in that: the second driving tooth is a driving tooth of the driving wheel other than the first driving tooth. 3.The nail gun according to claim 1, characterized in that: a ratio of the tip of the first driving tooth to the tip of the second driving tooth is less than 1. 4.The nail gun according to claim 1, characterized in that: a ratio of the tip of the first driving tooth to the tip of the second driving tooth is greater than or equal to 0.5 and less than 1. 5.The nail gun according to claim 1, characterized in that: a certain engagement length is defined between the driving tooth of the driving wheel other than the first driving tooth and the driving tooth of the striker other than the second driving tooth; the tip of the first driving tooth and the tip of the second driving tooth have a first tip difference; a ratio of the first tip difference to the engagement length is greater than or equal to 0.2 and less than or equal to 0.

7. 6.The nail gun according to claim 1, characterized in that: a ratio of a distance between the second driving tooth and the third driving tooth to a distance between the first driving tooth and the second driving tooth is less than 1. 7.The nail gun according to claim 1, characterized in that: a height of the second driving tooth is smaller than a height of the first driving tooth or a height of the third driving tooth. 8.The nail gun according to claim 5, characterized in that: the first driving tooth and the second driving tooth have a second tip difference; a ratio of the second tip difference to the engagement length is less than 1.

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