• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    There is provided a pneumatic tool comprising a motor, a drive mechanism coupled to the motor, and a cylinder. The drive mechanism is suitable for a piston drive. The cylinder is filled with high-pressure gas. The piston is fitted into the cylinder and adapted to the reciprocate within the cylinder, and the piston is coupled to a striker adapted to strike the work element. The drive mechanism is adapted to drive the piston to move in a first direction during a first period of the striking cycle; and the drive mechanism is adapted to disengage from the mechanical connection with the piston during a second period of the second cycle of the second cycle. The present invention requires only a single drive mechanism (e.g., gears with unequal teeth and corresponding drive blades)
    公开号:FR3080996A3
    申请号:FR1903306
    申请日:2019-03-29
    公开日:2019-11-15
    发明作者:Ying Xiang TAN；Hai Ling LIN；Jin Lin Zhou；Xi He
    申请人:TTI Macao Commercial Offshore Ltd；
    IPC主号:
    专利说明:

    Description
    Invention Title: Pneumatic Tool
    [0001] FIELD OF THE DISCLOSURE
    This invention relates to power tools, and in particular to power tools that use compressed air to the power source to drive a work element.
    BACKGROUND OF THE INVENTION [0003] Pneumatic tools, such as nail guns and the like, can be used as a tool for driving a work element, such as nails or the like, to be ejected at a high speed. In general, in each cycle, it is necessary to firstly compress the gas in the cylinder to a certain extent, so that the piston is in its ready-to-fire place, and then release the piston at the moment to be fired, which produces a strong kinetic energy to complete the striking operation. Such a cylinder-piston is commonly known as a "gas spring".
    [0004] Conventional pneumatic tools typically use a two-cylinder configuration, one for energy storage and the other for striking. The two cylinders are coaxially arranged in a nested manner. In the energy storage cylinder, the engine is driven by a pinion gear and a rack to drive the energy storage piston, and the energy storage piston causes the high-pressure gas to be compressed. Once the compression is completed, the striking piston is released. After one cycle is completed, both the energy storage piston and the striking piston will be moved to their original positions. This working principle results in a very complicated interna structure of the pneumatic tool, which gives rise to the possibility of various types of failures. SUMMARY OF THE INVENTION [0005] Accordingly, the embodiments of the present invention provide a variety
    In one aspect of the invention, there is provided a pneumatic tool comprising a motor, a drive mechanism coupled to the motor, and a cylinder. The drive mechanism is suitable for a piston drive. The cylinder is filled with high-pressure gas. The piston is fitted into the cylinder and adapted to the reciprocate within the cylinder, and the piston is coupled to a striker adapted to strike the work element. The drive mechanism is adapted to drive the piston to move in a first direction during a first period of the striking cycle; and the drive mechanism is adapted to disengage from the mechanical connection with the piston during a second period of the second cycle of the second cycle.
    [0007] Preferably, the drive mechanism includes a speed shifting mechanism coupled to the motor, a drive member coupled with the speed shifting mechanism, and an intermediate member adapted to be driven by the drive member. The member is moving to the intermediate member for linear motion.
    [0008] More preferably, the drive member is a drive gear having a plurality of teeth. The intermediate member has a number of features that are capable of being translated into action by the steering wheel.
    [0009] In a variation of the preferred embodiment, the plurality of the first phase of a pitch is different from the first pitch. The second part of the second part of the second part of the second part of the second part of the second part of the second part of the second part of the second period of time.
    [0010] In an embodiment, the second pitch generally corresponds to a range of 180 ° along the direction of rotation.
    In another embodiment, the drive gear includes four teeth. The four teeth form the first and second pitches, respectively.
    [0012] In yet another embodiment, the intermediate member is a drive that is coupled to the piston at one end, and the other end of the driving blade is coupled to the striker. The coupling features are a number of protrusions formed on one side of the drive blade.
    In another variation of the embodiment, the power tools include only one cylinder which is maintained.
    [0014] Preferably, the cylinder includes a chamber at its center and a sub-chamber located around and parallel to the main chamber. The piston is received within the chamber and adapted to the chamber.
    In another variation of the preferred embodiment, the drive blade is supported by a plurality of bearings to the housing of the pneumatic tool.
    [0016] Preferably, the plurality of the bearings is the same as the drive of the drive.
    [0009] Since only a single drive mechanism (eg, gears with unequal teeth and drive shaft matching) is required to simultaneously achieve movement of the piston in two different directions, the pneumatic tool of the present invention requires only one cylinder, without the need to conFig. two cylinders as in the prior art. By configuring the pitch over the angular extent of the teeth on the gears, it is possible to precisely control the energy storage (compression) period and the subsequent strike (release) period in each striking cycle. Moreover, the striking cycle can be automati- cally and continuously repeated, which means that the operation of the motor in the pneumatic tool is continued without any interference, and in particular the motor is rotated at a constant speed in a single direction, and the rotation of the gear described above automatically completed each year.
    [0018] Additionally, the present invention provides further improvements to further enhance the performance of the pneumatic tool. For example, a further explanation of the role of the single cylinder in a large group of gases, the release of the high pressure gas, ie, the release of the piston, the gas passage between the cylinder chambers. In addition, some embodiments of the present invention include a plurality of bearings which are clamped to opposite surfaces of the drive to the drive blade in a stable manner such that it can only move in a straight line.
    Brief description of the drawings [0019] Further understanding of the performance and advantages of the present invention can be obtained by reference to the remainder of the specification and the ac-companying drawings; the same components in the drawings havings the same reference numerals.
    [Fig.
    Fig. 1 is an exploded view of the internal structure of a pneumatic tool according to one embodiment of the present invention.
    [Fig.2]
    Fig. 2 is a perspective cross-sectional view of a portion of the internal structure of the pneumatic tool of FIG. 1.
    Fig.3a [0023] [0023] [fig.3b]
    Figs. 3a and 3b are respectively an axial cross-sectional schematic view and a radial cross-sectional view of a cylinder in the pneumatic tool of Fig. 1.
    [Fig.
    The connection diagram of the piston, the drive blade and the gear in the pneumatic tool of Fig. 1 is shown separately in FIG. 4.
    [0025] [fig.5a]
    Fig. 5a is a schematic view showing the compression of the high pressure gasket by the gear drive of the pneumatic tool of Fig. 1 during the striking cycle.
    [Fig.
    Fig. 5b is a schematic view of the pneumatic tool of FIG. 1 with the gear being released during the cycle so that the piston can be released.
    [Fig.
    Fig. 6 is a diagram showing the connection of the piston, the bearing, the drive blade and the gear in the pneumatic tool of FIG. 1.
    [0028] DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
    [0029] Embodiments of the present invention utilize a single drive mechanism for the entire striking cycle. Other embodiments and embodiments of the present invention are readily apparent from the following description.
    Referring to Figs. And a first embodiment of the invention, a pneumatic tool, in particular a nail gun, is disclosed. The nail gun includes a housing, a handle, etc., which are well-known to those skilled in the art, but which are not shown here for the sake of brevity. In contrast, the cylinder 40, the end cover 44 and the end of the cylinder 40, and the valve 46 are shown directly in Figs. 1 and 2. This cylinder 40 is the only cylinder in the nail gun. Both ends of the cylinder 40. The valve 46 is for connecting the cylinder 40 to an external source of high-pressure gas (eg, an air compressor, not shown) 40. A piston 36 is received within the cylinder 40 and is adapted to reciprocate. The piston 36 is coupled to one end of the drive blade 42 (in this embodiment as an intermediate member). The drive blade has an elongated shape to the workpiece (e.g., a nail) to achieve the working effect of the nail gun. In order to ensure airtightness of the cylinder 40, at the end of the cylinder 40, a gasket 38 and a cushion 34 are disposed to avoid accidental leakage of high-pressure gas cylinder 40 and to prevent the impact of the piston 36 from the other parts of the nail gun. The magazine is removably attached to the front end of the nail gun.
    [0031] Further, a motor and a drive mechanism are disposed at the front end of the nail gun. The drive mechanism includes a gearbox 22, which is coupled to the gearbox 22. Specifically, the drive mechanism includes a gear gear 30b that is respectively located on the shaft of the gearbox 22 and a drive shaft that is perpendicular to the output shaft. A driven gear 30a is fixed to the drive shaft 50. The driven gear 30a and the main gear 30b are meshed with each other to perform a direction change of the rotational motion. Further, two drive gears 28 which are parallel to each other (together in a drive member) are fixed to the drive shaft 50. The drive shaft 50 is fixed to the frame 26 by bearings (not shown), and the frame 26 is fixed to a housing (not shown) of the nail gun. Note that the various gears described above and the motor 20, the gearbox 22, and the like are not shown in Fig. 2, and Fig. 2 shows the State in which the piston is at the bottom dead center of its stroke.
    The structure of the cylinder 40 is more clearly shown in Figs. 3a-3b. The cross-sectional view of Fig. The sector chamber 54 is also referred to a sub-chamber, and the circular chamber 52 is also referred to main chamber. The sub-chambers 54 surround the main chamber 52 and they are parallel to each other. Note that ail of the sub-chamber 54 and the main chamber are 44. The piston 36 is described in the following section.
    [0033] Figs. 4-6 clearly show the details of the drive mechanism described above. Spe-cifically, the drive-blade 42 and the two-drive gears 28 haven a particular meshing rela-tionship. There are four 28a-28d, and there are two drive gears 28 are always synchronously rotated due to the relationship of drive shafts 50, that is, the corresponding teeth 28a-28d on both drive gears 28 are at the same angular position at any time. Each one of the teeth 28a-28d has a shape similar to the dovetail, and they are arranged in a clockwise direction as shown in Figs. 5a-5b in the circumferential direction. On the drive blade 42, there are two rows, each row of multiple coupling features along its length. Specifically, the coupling is a plurality of protrusions 42a-42d on the side of the drive blade 42, res-pectively. 42. Since the drive gear 28 is rotatable, it is capable of converting the motion of the rotation in the linear direction of the drive 42 As shown most clearly in Fig. 4. Each of the protrusions 42a-42d corresponds in tum to each of the corresponding teeth 28a-28d to the drive gear 28. The protrusions 42a-42d are arranged equidistantly from each other. For each of the drive 28 gears, the distances between the above four teeth 28a-28d (the angular distance in the direction of rotation) is not exactly the same. In contrast, as shown in Figs. 5a-5b, the distance between the teeth 28a and the teeth 28d, 28b and 28b, the teeth 28b and 28c , the teeth 28c and 28d. As shown in Figs. 5a-5b, the second pitch is substantially less than or equal to 180 degrees.
    [0034] Further, as shown in FIG. 6, the drive blade 42. The four bearings 32 are distributed on the sides of the drive 42 and the drive side 42. It is to be noted that in the interplay between the drive 32 and the above-described between the drive gear 28 and the protrusions 42a-42d, the two sides of the bearing 32 are different from the two sides on which the protrusions 42a -42d are located.
    Now look at the working principle of the nail gun in the above embodiment. When the user activates the nail gun (e.g., by pressing the trigger), the motor 20 of Figs. 1-2 begins to rotate, and the original high speed rotational motion output by the motor 20 is converted by the gearbox 22 into a low-speed but wide-torque rotational motion of the output shaft 48. Such a rotational motion is further Rotational motion in the other direction of the drive shaft 50 by the intermeshing gears 30a and 30b, so that the tangential direction of the rotation of the drive gear 28 coincides with the direction of movement of the drive blade 42. It can be seen that the output shaft 48, the drive shaft 50, and the drive blade 42 are arranged such that their lengths are per-pendicular to each other. The rotation of the drive shaft also causes the drive gear 28 to rotate. In particular, the drive gear 28 rotates in a counterclockwise direction in Figs, 5a and 5b.
    [0036] Each of the following cycles of the nail gun is defined in this embodiment by the drive of the drive 42 entire stroke as end. Fig. 5a shows the meshing relationship between the drive gear 28 and the drive blade 42 when the drive blade 42 is in its bottom dead center position. Fig. 5b shows the meshing relationship between the drive gear 28 and the drive blade 42 when the drive blade 42 is in its top dead center position. Starting from Fig. 5a, when the cycle begins, the drive gear 28 begins to rotate counterclockwise, and the tooth 28a first contact and abut against the protmsion 42a on the drive 42. Such abutment causes the drive 42 to produce a motion in the direction indicated by arrow 60. The movement of the drive 42 also causes the piston 36 to move and compress the high pressure gas in the cylinder, ie, the energy storage process of the gas spring.
    However, as the drive gear 28 continues to rotate, the tooth 28a moves 42a progressively away from the protrusions and eventually out of contact with the protrusions 42. Theoretically, such disengagement would cause the drive 42 to lose its driving force and would cause a rebound in the opposite direction. However, since the next tooth 28b will start to corne into contact with the next protrusion 42b in a short time (similar to the above-mentioned teeth 28a and 42a protmsions), the break and / or rebound of the drive 42 is very short and can be ignored. The one-to-one, sequential contact between these teeth and protrusions continues until the tooth 28d and the protrusions 42d horn into contact and eventually will disengage from the contact position (as shown in Fig. 5b). So far, it is called the first period of the striking cycle.
    [0038] Once the tooth 28d is completely out of contact with the protrusion 42d, the drive blade 42 will be driven by the drive gear 28 because the second pitch of the tooth 28d to the next tooth drive gear 28 and drive 42 are completely disengaged from the mechanical connection. At this time, the second period of the striking cycle begins. At this moment, because of the previous compression of the high-pressure gas, the high-pressure gas will cause the piston and drive blade 42 to produce a rapid reverse motion, as indicated by arrow 62. Such reverse motion releases the energy accumulated by the gas spring, turning it into a powerful kinetic energy, and the end of the drive blade 42 will strike a work element such as a nail and disengage it from the nail gun to completed the action nailing. At this moment, the drive will focus on its bottom dead center position, and the striking cycle ends. The next striking cycle begins immediately because the motor is running in the same direction at a constant speed throughout the entire time, the drive gear 28 also rotates in the same direction at a constant speed.
    [0039] The above-mentioned nail gun has three first pitches on the drive gear 28, and the rotation of the drive gear 28 at the first pitch corresponds to the first period of the above-mentioned striking cycle. The rotation of the drive gear 28 at the second pitch corresponds to the second period of the striking cycle.
    [0040] Thus, those skilled in the art will recognize that various modifications, additional structures, and equivalents may be used without departing from the spirit of the invention. Accordingly, the above description should not be taken as limiting the scope of the invention as defined by the suede.
    [0041] For example, the above-mentioned drive and drive gear are shown in a specification in the drawings, and the number of teeth-protrusions pairs in contact with each other is four. However, those skilled in the art will appreciate that in other variations of the invention, both the drive gear and the drive blade may have different shapes and the number of similar teeth-protrusions may be varied. Any movement in the two directions (e.g., reciprocating motion) of the piston through the unequal arrangement of the teeth will fall within the scope of the present invention.
    权利要求:
    Claims (1)
    [1" id="c-fr-0001]
    Claims [Claim 1] A pneumatic tool comprising a motor; a drive mechanism coupled to the motor; the drive mechanism adapted to drive a piston; a cylinder fdled with high-pressure gas; the piston is received within the cylinder and adapted to be re-ciprocated within the cylinder; the piston coupled to a striker adapted to strike the work element; the drive mechanism is adapted to drive the piston to move in a first direction during the first period of the striking cycle; The second phase of the second phase of the second phase of the second phase of the second cycle [Claim 2] The pneumatic tool according to claim, the driving mechanism includes a speed shifting mechanism coupled to the motor, a member driven to the speed shifting mechanism, and an intermediate member adapted to be driven by the drive member; the moving member adapts to rotate and drive the intermediate member to move linearly. [Claim 3] The pneumatic tool according to claim; the intermediate member having a plurality of coupling functions that are capable of being driven by the movement of the driving force. [Claim 4] The pneumatic tool according to claim 3, wherein the first and second positions are separated by the first pitch; The present invention relates to a second part of the second part of the second part of the second part of the second part of the second part of the second part of the second part of the second period of time. [Claim 5] The pneumatic tool according to claim 4, wherein the second pitch corresponds to a range of 180 ° along the direction of rotation. [Claim 6] The pneumatic tool after claim; the four teeth form said second pitches, respectively. [Claim 7] The pneumatic tool according to claim 3, wherein the intermediate member is a driving force that is coupled to the piston at one end, and another end of the driving blade is coupled to the striker; the features being a plurality of protrusions formed on one side of the drive blade. [Claim 8] The pneumatic tool, which includes the pneumatic tool. [Claim 9] The pneumatic tool according to claim 8, wherein the cylinder is included in its center chamber and its sub-chamber located around and parallel to the main chamber; the piston being received within the chamber and adapted to the chamber. [Claim 10] The pneumatic tool according to claim 3, which is the driving force of the pneumatic tool. [Claim 11] The pneumatic tool according to claim 10, wherein the plurality of the bearings of the two-wheel drive is the same as the other.
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3080996A3|2019-11-15|Pneumatic Tool
    JP4008865B2|2007-11-14|Fastener
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    CN108098694B|2020-09-01|Power tool
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    WO2022011631A1|2022-01-20|Fastening tool with a crank transmission
    SU950517A1|1982-08-15|Percussive nut-driver
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    US10406664B2|2019-09-10|Impact structure
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    KR0156839B1|1998-11-16|Rotary engine with reciprocating piston
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    SU896297A2|1982-01-07|Mechanism for converting reciprocation to rotary motion
    CZ15667U1|2005-07-25|Engine with rotary combustion chambers
    同族专利:
    公开号 | 公开日
    EP3790707A1|2021-03-17|
    EP3790708A4|2022-02-16|
    WO2019214087A1|2019-11-14|
    EP3790708A1|2021-03-17|
    WO2019214088A1|2019-11-14|
    CN110450108A|2019-11-15|
    CA3099601A1|2019-11-14|
    CN112236268A|2021-01-15|
    CA3099602A1|2019-11-14|
    US20210008701A1|2021-01-14|
    FR3080996B3|2020-06-12|
    US20210023686A1|2021-01-28|
    引用文献:
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    CN107803790A|2017-10-25|2018-03-16|成都四零三科技有限公司|A kind of nailing tools for being used for heat-insulation layer terminal operation in construction and installation|
    CN107914242A|2017-12-22|2018-04-17|王家宏|Integral electric air pressure nailing gun|CA3145413A1|2019-11-29|2021-06-03|Techtronic Cordless Gp|Fastener tool with locking mechanism|
    WO2021195188A1|2020-03-25|2021-09-30|Milwaukee Electric Tool Corporation|Powered fastener driver|
    DE102020113084A1|2020-05-14|2021-11-18|Isaberg Rapid Ab|Electric tacker|
    法律状态:
    2020-02-27| PLFP| Fee payment|Year of fee payment: 2 |
    2021-03-25| PLFP| Fee payment|Year of fee payment: 3 |
    优先权:
    申请号 | 申请日 | 专利标题
    CN201810431869.XA|CN110450108A|2018-05-08|2018-05-08|Pneumatic tool|
    CN201810431869.X|2018-05-08|
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