Rotary impact tool

Abstract

The utility model discloses a rotary impact tool which comprises a shell, a rotary sleeve, a piston, a rotary transmission assembly, a hammering transmission assembly and a driving motor. The rotating sleeve is at least partially arranged in the shell, and one end of the rotating sleeve is connected with a working head; the piston is arranged in the rotating sleeve; the rotating transmission assembly is connected with the rotating sleeve; the hammering transmission assembly is connected with the piston and drives the piston to do linear reciprocating motion in the length direction of the rotating sleeve. The driving motor is provided with a driving gear, and the driving gear is meshed with the rotating transmission assembly and the hammering transmission assembly to drive the rotating transmission assembly and the hammering transmission assembly to move. The gear shifting assembly is used for selectively engaging and disengaging the rotating transmission assembly and the hammering transmission assembly with the rotating sleeve so that different working modes of the rotating impact tool can be achieved. The gear shifting assembly of the rotary impact tool is simple in structure and higher in reliability.

Description

Technical Field

[0001] The utility model belongs to the technical field of electric motors, in particular to a rotary impact tool. Background Art

[0002] Rotary impact tools usually have multiple working modes such as rotation and hammering. In order to integrate multiple working modes into the same power tool, it is necessary to set up a shift mechanism to switch the power tool so that it is in different working gears. Existing power tools are usually composed of multiple structures such as an eccentric knob, a spring, multiple paddles, a torsion spring, a torsion spring seat, a drill gear clutch, and a hammer gear clutch. There are many problems with this structure. For example, the paddles, the torsion springs that cooperate with the paddles, the torsion spring seat, etc. have complex structures, and the dimensions of each component are difficult to guarantee, which affects the function realization. Secondly, the torsion spring and the torsion spring seat are prone to heat up during operation or deform / fail after long-term work.

[0003] The information disclosed in this background technology section is only intended to increase the understanding of the overall background of the present invention, and should not be regarded as an admission or any form of suggestion that the information constitutes the prior art already known to those skilled in the art. Utility Model Content

[0004] The purpose of the utility model is to provide a rotary impact tool, the shift assembly of which has a simple structure and higher reliability.

[0005] To achieve the above objectives, a specific embodiment of the present invention provides the following technical solution: a rotary impact tool comprising: a housing, a sleeve, a piston, a rotary transmission assembly, a hammer transmission assembly, and a drive motor. The sleeve is at least partially disposed within the housing, one end of the sleeve being connected to a working head; the piston is disposed within the sleeve; the rotary transmission assembly is connected to the sleeve; the hammer transmission assembly is connected to the piston, driving the piston to perform linear reciprocating motion along the length of the sleeve; and the drive motor is provided with a drive gear that meshes with the rotary transmission assembly and the hammer transmission assembly to drive the rotary transmission assembly and the hammer transmission assembly to move.

[0006] The rotary impact tool also includes a shift assembly comprising a first clutch, a second clutch, a shift paddle, and a shift knob. The first clutch is mounted on the rotating sleeve and is linked to the rotary transmission assembly; the second clutch is mounted on the hammer transmission assembly and is linked to the hammer transmission assembly; the shift paddle is pivotally connected to the housing and is linked to the second clutch; and the shift knob is mounted on the housing and can be rotated to different angles to selectively connect to the first clutch and / or the shift paddle.

[0007] In one or more embodiments of the present invention, the shift assembly further includes a return torsion spring, which is pivotally connected to the housing, the shift paddle is pivotally connected to the housing, the return torsion spring is coaxially connected to the shift paddle, one end of the return torsion spring is against the shift paddle, and the other end is against the housing.

[0008] In one or more embodiments of the present invention, the housing is further configured with an abutting surface, the abutting surface abuts against the shift paddle, and the abutting surface limits the rotation of the shift paddle.

[0009] In one or more embodiments of the present invention, the hammer transmission assembly includes: a transmission gear and a crankshaft; the second clutch is slidably disposed on the crankshaft and is rotationally fixed relative to the crankshaft; a limiting protrusion is provided on the lower surface of the second clutch; a limiting groove is provided on the upper surface of the transmission gear; the limiting groove is configured to accommodate the limiting protrusion;

[0010] When the limiting protrusion is located in the limiting groove, the transmission gear and the second clutch are fixed relative to the crankshaft and rotate together with the crankshaft, driving the piston to perform linear reciprocating motion;

[0011] When the limiting protrusion is disengaged from the limiting groove, the transmission gear rotates relative to the crankshaft, and the piston stops the linear reciprocating motion.

[0012] In one or more embodiments of the present invention, one of the second clutch and the crankshaft is configured with a guide portion, and the other of the second clutch and the crankshaft is configured with a guide groove, and the guide portion and the guide groove are matched to limit the rotation of the second clutch relative to the crankshaft.

[0013] In one or more embodiments of the present invention, a first return spring is provided between the second clutch and the crankshaft, and the first return spring has an elastic force that causes the second clutch to abut against the transmission gear.

[0014] In one or more embodiments of the present invention, the second clutch further comprises a circumferentially protruding annular ridge, and the shift paddle is provided with a push portion protruding toward the second clutch, and within the axial projection plane of the second clutch, the projection of the push portion at least partially overlaps with the projection of the annular ridge.

[0015] In one or more embodiments of the present invention, a plurality of the pushing portions are symmetrically arranged on the outer periphery of the second clutch.

[0016] In one or more embodiments of the present invention, the shift paddle includes a driving arm, a rotating arm and a connecting portion. The rotating arm is arranged on the left and right sides of the hammer transmission assembly, and the connecting portion connects the two rotating arms.

[0017] In one or more embodiments of the present invention, the shift paddle is a sheet metal component.

[0018] Compared to existing technologies, the rotary impact tool of the present invention utilizes the aforementioned shift assembly, requiring only a single shift knob, a single shift paddle, and two clutches to achieve multiple gear shifts, thereby simplifying the shift assembly structure. Furthermore, the shift paddle's simple structure simplifies its molding process and assembly structure, and also requires less complex and precise precision. Furthermore, this simplified structure reduces component wear and other issues. Compared to complex shift structures, this shift assembly is located farther away from the drive motor, making it less susceptible to problems such as thermal deformation caused by the heat generated by the drive motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments recorded in the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 A perspective view of a rotary impact tool according to an embodiment of the present invention;

[0021] Figure 2 This is a diagram showing the internal structure of a rotary impact tool in one embodiment of the present invention;

[0022] Figure 3 An exploded view of a rotary impact tool in one embodiment of the present invention;

[0023] Figure 4 This is an exploded view of the crankshaft portion in one embodiment of the present invention;

[0024] Figure 5 A top view of a crankshaft in one embodiment of the present invention;

[0025] Figure 6 for Figure 5 A cross-sectional view of the middle AA axis, where the rotary impact tool is in hammering gear;

[0026] Figure 7 for Figure 5 A cross-sectional view of the middle AA axis, when the rotating impact tool is out of the hammer stop;

[0027] Figure 8 This is a first schematic diagram of a rotary impact tool in an embodiment of the present invention in a hammering position;

[0028] Figure 9 This is a second schematic diagram of a rotary impact tool in an embodiment of the present invention in a hammering position;

[0029] Figure 10 This is a schematic diagram of a rotary impact tool in a drill stop according to an embodiment of the present invention;

[0030] Figure 11 This is a first schematic diagram of a rotary impact tool in an embodiment of the present invention in an angle adjustment position;

[0031] Figure 12 This is a second schematic diagram of the rotary impact tool in an embodiment of the present invention in the angle adjustment position;

[0032] Figure 13 This is a first schematic diagram of a rotary impact tool in a hammer drill gear according to an embodiment of the present invention;

[0033] Figure 14 This is a second schematic diagram of a rotary impact tool in an embodiment of the present invention in a hammer drill position;

[0034] Figure 15 Schematic diagram of the shift paddle and housing in one embodiment of the present invention.

[0035] Description of main reference numerals:

[0036] 1-housing, 11-abutting surface, 12-locking plate, 121-locking groove, 2-swivel sleeve, 21-piston, 22-limiting member, 3-rotation transmission assembly, 31-large bevel gear, 311-tooth groove, 4-hammer transmission assembly, 41-transmission gear, 411-limiting groove, 42-crankshaft, 421-accommodating groove, 422-eccentric shaft, 43-connecting rod, 5-drive motor, 51-drive gear, 6-shift assembly, 61-first clutch, 611-locking tooth, 612-matching tooth, 62-second clutch, 621-limiting protrusion, 622-guide part, 623-guide groove, 624-annular ridge, 63-shift paddle, 631-pivot, 632-return torsion spring, 633-pushing part, 634-driving arm, 635-rotating arm, 636-connecting part, 64-shift knob, 641-knob eccentric pin, 65-first return spring, 66-second return spring. DETAILED DESCRIPTION

[0037] In order to enable those skilled in the art to better understand the technical solutions of the present invention, the following will be combined with the drawings of the embodiments of the present invention to clearly and completely describe the technical solutions of the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present invention.

[0038] like Figure 1-15 As shown, a rotary impact tool in one embodiment of the utility model includes a housing 1, a rotating sleeve 2, a piston 21, a rotary transmission assembly 3, a hammer transmission assembly 4, a drive motor 5 and a shift assembly 6. The rotating sleeve 2 is arranged in the housing 1, and one end of the rotating sleeve 2 is connected to a working head. The rotary transmission assembly 3 is connected to the rotating sleeve 2 and is used to drive the rotating sleeve 2 to rotate. The hammer transmission assembly 4 is connected to one end of the piston 21 and is used to drive the piston 21 to perform linear reciprocating motion along the length direction of the rotating sleeve 2. The drive motor 5 is provided with a driving gear 51, and the driving gear 51 is engaged with the rotary transmission assembly 3 and the hammer transmission assembly 4 to drive the rotary transmission assembly 3 and the hammer transmission assembly 4 to move. The shift assembly 6 is used to selectively clutch the rotary transmission assembly 3 and the hammer transmission assembly 4 with the rotating sleeve 2 to achieve different working modes of the rotary impact tool.

[0039] Specifically, if Figure 2 and Figure 3 As shown, the shift assembly 6 includes a first clutch 61, a second clutch 62, a shift paddle 63, and a shift knob 64. The first clutch 61 is mounted on the rotating sleeve 2 and is linked to the rotary transmission assembly 3. The second clutch 62 is mounted on the hammer transmission assembly 4 and is linked to the hammer transmission assembly 4. The shift paddle 63 is pivotally connected to the housing 1 and is linked to the second clutch 62 to control the engagement and disengagement of the second clutch 62 and the hammer transmission assembly 4. The shift knob 64 is provided on the housing 1 and can be rotated to different angles to selectively connect with the first clutch 61 and / or the shift paddle 63.

[0040] The working principle of the shift assembly 6 is as follows: in the initial state, the first clutch 61 is linked to the rotary transmission assembly 3, and the second clutch 62 is linked to the hammer transmission assembly 4. When the drive motor 5 is started, the rotating sleeve 2 rotates, driving the working head to rotate, and the working head can hammer under the action of the piston 21.

[0041] To change the operating mode of the rotary impact tool, the operator rotates the shift knob 64 to one position, disengaging the first clutch 61 from the rotary transmission assembly 3 and connecting the second clutch 62 to the hammer transmission assembly 4. The piston 21 then performs linear reciprocating motion, driving the work head to hammer, while the swivel sleeve 2 does not rotate. When the shift knob 64 is moved to another position, the second clutch 62 disengages the hammer transmission assembly 4, connecting the first clutch 61 to the rotary transmission assembly 3, rotating the swivel sleeve 2, and deactivating the piston 21. Thus, the shift assembly 6 changes the operating mode of the rotary impact tool.

[0042] In the above embodiment, the rotary impact tool of the present invention can reduce the number of shift paddles by adopting the above shift assembly, simplify the shift structure of the rotary impact tool, make the shift structure more reliable and reduce assembly and maintenance costs.

[0043] Specifically, if Figure 1 As shown, the housing 1 of the rotary impact tool can be assembled from multiple parts. For example, the housing 1 is divided into two parts, a front housing and a rear housing, which are connected to form a complete housing 1. The interior of the housing 1 forms an accommodating space.

[0044] The rotating sleeve 2 is at least partially disposed in the housing 1 and can realize switching between different gears under the action of the gear shift assembly 6 .

[0045] In one embodiment, the piston 21 can perform linear reciprocating motion under the drive of the hammer transmission assembly 4. The rotary sleeve 2 can rotate under the drive of the rotary transmission assembly 3. The rotary sleeve 2 can also rotate while the piston 21 performs linear reciprocating motion. Among them, the linear reciprocating motion of the piston 21 can be defined as the hammer stop of the rotary impact tool. The rotation of the rotary sleeve 2 can be defined as the drill stop. The linear reciprocating motion of the piston 21 and the rotation of the rotary sleeve 2 can be defined as the hammer drill stop. The rotary sleeve 2 can also rotate freely under certain conditions to adjust the angle of the working head connected to the rotary sleeve 2. This mode can be defined as the angle adjustment stop of the rotary impact tool.

[0046] In one embodiment, if Figure 3 and Figure 4 As shown, the hammer transmission assembly 4 includes a transmission gear 41 and a crankshaft 42 from bottom to top.

[0047] The transmission gear 41 meshes with the drive gear 51. The driving force of the drive motor 5 is transmitted to the crankshaft 42 through the transmission gear 41. One end of the crankshaft 42 is connected to the transmission gear 41, and the transmission gear 41 can rotate relative to the crankshaft 42. The crankshaft 42 is connected to the piston 21 via a connecting rod 43.

[0048] like Figure 6As shown, the cooperation relationship between the second clutch 62 and the transmission gear 41 can be, for example, as follows: when the second clutch 62 is in contact with the transmission gear 41, the transmission gear 41 is fixed relative to the crankshaft 42 and drives the crankshaft 42 to rotate together, thereby driving the connecting rod 43 to drive the piston 21 to perform linear reciprocating motion. The air pressure in the rotating sleeve 2 changes periodically, driving the working head to hammer, thereby achieving hammering on the object to be constructed or operated. When the second clutch 62 is disengaged from the transmission gear 41, the transmission gear 41 can rotate relative to the crankshaft 42, and the crankshaft 42 cannot rotate with the transmission gear 41, so that the connecting rod 43 cannot drive the piston 21 to perform linear reciprocating motion.

[0049] One end of the connecting rod 43 is mounted on the crankshaft 42, and the other end is connected to the piston 21. Rotation of the crankshaft 42 drives the connecting rod 43 in linear reciprocating motion, thereby driving the piston 21 in linear reciprocating motion. The specific arrangement of the connecting rod 43 and the crankshaft 42 can be implemented in a variety of ways. For example, an eccentric shaft 422 may be provided at the top of the crankshaft 42. One end of the connecting rod 43 is mounted on the eccentric shaft 422. As the crankshaft 42 rotates, the eccentric shaft 422 drives the connecting rod 43, thereby driving the piston 21 in linear reciprocating motion.

[0050] In one embodiment, the second clutch 62 is slidably mounted on the crankshaft 42 and is rotatably fixed relative to the crankshaft 42. Specifically, a limiting protrusion 621 is provided on the lower surface of the second clutch 62. A limiting groove 411 is defined on the upper surface of the transmission gear 41. The limiting groove 411 is configured to accommodate the limiting protrusion 621.

[0051] Meanwhile, a guide portion 622 is configured on one of the second clutch 62 and the crankshaft 42. A guide groove 623 is configured on the other of the second clutch 62 and the crankshaft 42. The guide portion 622 and the guide groove 623 are mated to restrict the second clutch 62 from moving axially along the crankshaft 42 and from rotating relative to the crankshaft 42.

[0052] In one embodiment, for example, the guide groove 623 may be provided on the second clutch 6. The guide portion 622 may be provided on the crankshaft 42. Figure 5 As shown, the surface of the crankshaft 42 is provided with an accommodating groove 421 for accommodating the guide portion 622. For example, multiple accommodating grooves 421 can be evenly spaced along the circumference of the crankshaft 2 on the outer surface of the crankshaft 2. A guide groove 623 can be provided on the inner wall of the second clutch 62 along the axial direction of the second clutch 62 at a position corresponding to the accommodating groove 421. The guide groove 623 can connect the upper and lower surfaces of the second clutch 62. The accommodating groove 421 and the guide groove 623 can jointly accommodate the guide portion 622.

[0053] The specific setting method of the guide part 622 can be as follows: the guide part 622 is a spherical guide part 622. The size and shape of the accommodating groove 421 match the spherical guide part 622. Part of the spherical guide part 622 is accommodated in the accommodating groove 421 and can be fixed relative to the accommodating groove 421. The width of the guide groove 623 is roughly equal to the diameter of the spherical guide part 622. With this setting, since the guide groove 623 is arranged along the axial direction of the second clutch 62, the second clutch 62 can only move along the axial direction of the crankshaft 42 and cannot rotate relative to the crankshaft 42. Therefore, when the second clutch 62 abuts against the transmission gear 41, the transmission gear 41 can be fixed relative to the crankshaft 42 and drive the crankshaft 42 to rotate together.

[0054] like Figure 6 As shown, when the second clutch 62 slides along the crankshaft 42 and abuts the transmission gear 41, the limiting protrusion 621 can be inserted into the limiting groove 411. The transmission gear 41 and the second clutch 62 are fixed relative to the crankshaft 42. Under the action of the drive motor 5, the crankshaft 42 rotates together, driving the connecting rod 43 to move, thereby driving the piston 21 to perform linear reciprocating motion. At this time, the rotary impact tool is in the hammering gear.

[0055] like Figure 7 As shown, when the second clutch 62 slides along the crankshaft 42 and disengages the transmission gear 41, the limiting protrusion 621 disengages from the limiting groove 411. The transmission gear 41, freed from the restraint of the second clutch 62, can rotate relative to the crankshaft 42. The driving force of the drive motor 5 cannot be transmitted to the crankshaft 42 via the transmission gear 41, the connecting rod 43 does not move, and the piston 21 does not reciprocate linearly. At this point, the rotary impact tool disengages the hammering block.

[0056] In one embodiment, if Figure 3 and Figure 8 As shown, the movement of the second clutch 62 on the crankshaft 42 is controlled by the shift paddle 63. Figure 15 Specifically, the shift paddle 63 and the housing 1 can be connected via a pivot 631, allowing the shift paddle 63 to rotate about the pivot 631. The second clutch 62 also includes a circumferentially protruding annular ridge 624. The shift paddle 63 is provided with a push portion 633 that protrudes toward the second clutch 62. Within the axial projection plane of the second clutch 62, the projection of the push portion 633 at least partially overlaps with the projection of the annular ridge 624.

[0057] During the rotation of the paddle shifter 63, the abutting portion 633 abuts against the second clutch 62, thereby driving the second clutch 62 to slide on the crankshaft 42. In one embodiment, multiple abutting portions 633 are symmetrically arranged around the outer periphery of the second clutch 62, thereby ensuring stable abutment between the paddle shifter 63 and the second clutch 62.

[0058] Furthermore, the shift paddle 63 may include a driving arm 634, a rotating arm 635, and a connecting portion 636. The connecting portion 636 is connected to the housing 1 via a pivot 631. The rotating arms 625 are disposed on the left and right sides of the hammer transmission assembly 4. The connecting portion 636 connects the two rotating arms 635. In one embodiment, the push portion 633 may be disposed at one end of the rotating arm 635. The shift paddle 63 may be formed of sheet metal to reduce manufacturing cost and difficulty.

[0059] A return torsion spring 632 is provided on the shift paddle 63. The return torsion spring 632 is pivotally connected to the housing 1. In one embodiment, the return torsion spring 632 is coaxially connected to the shift paddle 63, for example, they can be connected to the same pivot 631. One end of the return torsion spring 632 is abutted against the shift paddle 63. The return torsion spring 632 has an elastic force that causes the shift paddle 63 to rotate clockwise / counterclockwise around the pivot 631. In one embodiment, the housing 1 is further provided with an abutment surface 11. The abutment surface 11 abuts against the shift paddle 63, and the abutment surface 11 limits the rotation of the shift paddle 63. Therefore, the elastic force of the return torsion spring 632 will not cause the shift paddle 63 to rotate excessively.

[0060] When the rotary impact tool needs to be switched to the hammer gear, the shift knob 64 can be rotated clockwise or counterclockwise relative to the housing 1 and abuts against the driving arm 634 of the shift paddle 63, causing the rotating arm 635 to rotate relative to the housing 1. The abutting portion 633 of the shift paddle 63 abuts against the second clutch 62, causing the second clutch 62 to disengage from the transmission gear 41, and the piston 21 stops its linear reciprocating motion.

[0061] When it is necessary to shift back to the hammer shift gear, the shift knob 64 rotates counterclockwise / clockwise relative to the housing 1 to disengage the driving arm 634 of the shift paddle 63. The return torsion spring 632 causes the rotating arm 635 of the shift paddle 63 to rotate, thereby disengaging the push portion 633 from the second clutch 62. A first return spring 65 is provided between the second clutch 62 and the crankshaft 42. The elastic force of the first return spring 65 causes the second clutch 62 to abut against the transmission gear 41, causing the piston 21 to perform linear reciprocating motion.

[0062] The rotation of the shift paddle 63 is controlled by the shift knob 64. In one embodiment, the shift knob 64 is provided with a knob eccentric pin 641.

[0063] In one specific embodiment of the shift knob 64, in its initial state, the driving arm 634 of the shift paddle 63 is not in contact with the knob eccentric pin 641 of the shift knob 64. The push portion 633 of the shift paddle 63 abuts the second clutch 62. At this point, if the drive motor 5 is operating, the piston 21 performs linear reciprocating motion; if the drive motor 5 is not operating, the piston 21 is stationary.

[0064] To disengage the rotary impact tool from the hammering mode, the shift knob 64 is rotated clockwise. During this rotation, the knob's eccentric pin 641 contacts and presses the shift paddle 63's drive arm 634 downward. The shift paddle 63 rotates counterclockwise, causing the rotary arm 635 to pivot upward. The push portion 633 of the second clutch 62 disengages from the transmission gear 41, halting the piston 21's linear reciprocating motion.

[0065] When the rotary impact tool needs to be switched back to the hammer gear, the shift knob 64 can be rotated in the opposite direction. The eccentric pin 641 of the shift knob 64 is disengaged from the drive arm 634 of the shift paddle 63. The elastic force of the return torsion spring 632 causes the shift paddle 63 to rotate clockwise, and the push portion 633 is disengaged from the second clutch 62. The second clutch 62 loses the restriction of the shift paddle 63 and can slide along the crankshaft 42. The elastic force of the first return spring 65 causes the second clutch 62 to slide toward the transmission gear 41 and abut against the transmission gear 41. The transmission gear 41 and the second clutch 62 are fixed relative to the crankshaft 42, and the driving force of the drive motor 5 can be transmitted to the crankshaft 42, and the piston 21 performs linear reciprocating motion.

[0066] In addition to the shift paddle 63 being controlled by the shift knob 62, the first clutch 61 is also controlled by the shift knob 62. In one embodiment, the rotary transmission assembly 3 includes a large bevel gear 31 and a connecting component (not shown in the figure). The large bevel gear 31 is sleeved on one end of the rotating sleeve 2 and can rotate along the circumference of the rotating sleeve 2. The large bevel gear 31 can engage with the first clutch 61. When the large bevel gear 31 is not engaged with the first clutch 61, it can rotate relative to the rotating sleeve 2, but cannot drive the rotating sleeve 2 to rotate together.

[0067] The connecting component cooperates with the large bevel gear 31 and the drive gear 51, thereby transmitting the driving force of the drive motor 5 to the large bevel gear 5 through the drive gear 51 and the connecting component to drive the large bevel gear 31 to rotate. The connecting component here can be a device capable of power transmission, such as a gear or a belt. The connecting component is prior art and will not be described in detail here.

[0068] In one embodiment, a locking plate 12 is fixedly disposed within the housing 1. The first clutch 61 is operatively connected to the locking plate 12 and can be fixed relative to the locking plate 12. A limit member 22 is disposed between the first clutch 61 and the rotating sleeve 2. The limit member 22 is configured to guide the first clutch 61 in axial movement along the rotating sleeve 2 and limit rotation of the first clutch 61 relative to the rotating sleeve 2.

[0069] To switch the drill gear of the rotary impact tool, the shift knob 64 can be rotated counterclockwise or clockwise to engage the first clutch 61 and drive the first clutch 61 away from the large bevel gear 31. The large bevel gear 31 disengages from the first clutch 61, and the first clutch 61 engages the locking plate 12. The large bevel gear 31 is unable to drive the rotating sleeve 2 to rotate, and the rotating sleeve 2 stops rotating.

[0070] When the rotary impact tool needs to be switched back to the drilling gear, the shift knob 64 can be rotated clockwise / counterclockwise to disengage the first clutch 61. A second return spring 66 is provided between the first clutch 61 and the housing 1. The elastic force of the second return spring 66 causes the first clutch 61 to disengage from the locking plate 12 and causes the first clutch 61 to engage with the large bevel gear 31. The large bevel gear 31 can drive the first clutch 61 and the rotating sleeve 2 to rotate together.

[0071] In one embodiment, the specific working method of the drill gear switching of the rotary impact tool is as follows:

[0072] In the initial state, when the drive motor 5 is started, the first clutch 61 is engaged with the large bevel gear 31, driving the large bevel gear 31 to rotate. The first clutch 61 cannot rotate relative to the rotating sleeve 2 and can only drive the rotating sleeve 2 to rotate together under the drive of the large bevel gear 31. At this time, the rotary impact tool is in the drilling gear.

[0073] like Figure 10 As shown, when the rotary impact tool needs to disengage from the drill stop, the shift knob 64 is rotated counterclockwise. The eccentric pin 641 on the shift knob 64 contacts the first clutch 61, driving the first clutch 61 away from the large bevel gear 31. The first clutch 61 and the large bevel gear 31 are disengaged, so that the large bevel gear 31 cannot drive the rotating sleeve 2 to rotate. The first clutch 61 also contacts the locking plate 12, securing the first clutch 61 thereto, and the rotary impact tool disengages from the drill stop.

[0074] like Figure 14 As shown, Figure 14 The second schematic diagram shows the rotary impact tool in the hammer drill gear. At this point, the mating relationship between the first clutch 61 and the large bevel gear 31 is the same as in the hammer drill gear. To switch the rotary impact tool back to the drill gear, rotate the shift knob 64 clockwise. The eccentric pin of the shift knob 61 disengages from the first clutch 61. The elastic force of the second return spring 66 is released, causing the first clutch 61 to approach the large bevel gear 31 and engage with it. The large bevel gear 31 can drive the first clutch 61 and the rotating sleeve 2 to rotate together. The rotary impact tool switches back to the drill gear.

[0075] In one embodiment, one end of the first clutch 61 is provided with a plurality of locking teeth 611 along the axial direction, and the locking plate 12 is provided with a plurality of locking grooves 121. The locking teeth 611 can be inserted into the locking grooves 121, thereby securing the first clutch 61 to the locking plate 12. The other end of the first clutch 61 is provided with a plurality of mating teeth 612 along the axial direction, and the large bevel gear 31 is provided with a plurality of tooth grooves 311. The mating teeth 612 can be inserted into the tooth grooves 311, thereby meshing the first clutch 61 with the large bevel gear 31, causing the rotating sleeve 2 to rotate.

[0076] As previously mentioned, the rotary impact tool features an angle adjustment range in addition to the hammer and drill ranges. When the rotary impact tool is in the angle adjustment range, the drive motor 5 is deactivated, and the swivel sleeve 2 can be manually rotated. The piston 21 does not reciprocate linearly. At this point, the working head connected to the swivel sleeve 2 can be adjusted to the appropriate working position, and then the hammer or drill range can be selected to activate the drive motor 5.

[0077] like Figure 11 and 12 As shown, to switch the rotary impact tool to the angle adjustment gear, rotate the shift knob 64 counterclockwise. The eccentric pin 641 on the shift knob 64 abuts the first clutch 61, driving the first clutch 61 away from the large bevel gear 31. Here, the rotation angle of the shift knob 64 is less than the rotation angle of the rotating sleeve 2 when it disengages the drill gear, and the first clutch 61 is no longer in contact with the locking plate 12. Therefore, the rotating sleeve 2 can be rotated freely manually.

[0078] The rotary impact tool can be in either hammer mode or drill mode. When the rotary impact tool is in hammer mode, the first clutch 61 and the rotary transmission assembly 3 are disengaged. Similarly, when the rotary impact tool is in drill mode, the second clutch 62 and the hammer transmission assembly 4 are disengaged.

[0079] The rotary impact tool can also be in hammer drill mode, meaning that while the sleeve 2 rotates, the piston 21 performs linear reciprocating motion. In this mode, the shift knob 64 is not in contact with either the first clutch 61 or the shift paddle 63, resulting in the first clutch 61 engaging the large bevel gear 31 and the second clutch 62 engaging the transmission gear 41. The drive motor 5 can then drive the sleeve 2 to rotate and the piston 21 to perform linear reciprocating motion.

[0080] In summary, the rotary impact tool of the present invention, by providing the aforementioned shift assembly 6, only requires a single shift knob 64, a single shift paddle 63, and two clutches to achieve multiple gear shifts, thereby simplifying the structure of the shift assembly 6. Furthermore, the simple structure of the shift paddle 63 simplifies its molding process and assembly structure, and also requires simpler and lower precision. Furthermore, this simplified structure can also reduce problems such as component wear. Compared to complex shift structures, this shift structure is located farther away from the drive motor 5, making it less susceptible to problems such as thermal deformation of components caused by the heat generated by the drive motor 5.

[0081] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the present invention. Therefore, the embodiments should be considered in all respects as illustrative and non-restrictive, and the scope of the present invention is defined by the appended claims, not the foregoing description, and all variations within the meaning and range of equivalents of the claims are intended to be encompassed within the present invention. Any reference sign in a claim should not be construed as limiting the claim to which it relates.

[0082] In addition, it should be understood that although this specification is described in terms of implementation methods, not every implementation method contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

Claims

1. A rotary impact tool comprising: Housing (1); A rotating sleeve (2) is at least partially disposed in the housing (1), and one end of the rotating sleeve (2) is connected to a working head; A piston (21) is disposed in the rotating sleeve (2); A rotary transmission assembly (3) connected to the rotary sleeve (2); A hammer transmission assembly (4) is connected to the piston (21) and drives the piston (21) to perform linear reciprocating motion along the length direction of the rotating sleeve (2); and A driving motor (5) is provided with a driving gear (51), wherein the driving gear (51) is engaged with the rotating transmission assembly (3) and the hammering transmission assembly (4) to drive the rotating transmission assembly (3) and the hammering transmission assembly (4) to move; Characterized in that the rotary impact tool further comprises a shift assembly (6), which comprises: A first clutch (61) is sleeved on the rotating sleeve (2) and is linked to the rotating transmission assembly (3); A second clutch (62) is sleeved on the hammer transmission assembly (4) and is linked to the hammer transmission assembly (4); A shift paddle (63) pivotally connected to the housing (1), the shift paddle (63) being linked to the second clutch (62); and A shift knob (64) is provided on the housing (1) and can be rotated at different angles to selectively connect with the first clutch (61) and / or the shift paddle (63).

2. The rotary impact tool according to claim 1, wherein The shift assembly (6) further comprises a return torsion spring (632), wherein the return torsion spring (632) is pivotally connected to the housing (1), the shift paddle (63) is pivotally connected to the housing (1), the return torsion spring (632) is coaxially connected to the shift paddle (63), one end of the return torsion spring (632) is abutted against the shift paddle (63), and the other end is abutted against the housing (1).

3. The rotary impact tool according to claim 2, wherein The housing (1) is further provided with an abutting surface (11), the abutting surface (11) abuts against the shift paddle (63), and the abutting surface (11) limits the rotation of the shift paddle (63).

4. The rotary impact tool according to claim 1, wherein The hammer transmission assembly (4) comprises: a transmission gear (41) and a crankshaft (42); the second clutch (62) is slidably arranged on the crankshaft (42) and is rotationally fixed relative to the crankshaft (42); a limiting protrusion (621) is provided on the lower surface of the second clutch (62); a limiting groove (411) is provided on the upper surface of the transmission gear (41); the limiting groove (411) is configured to accommodate the limiting protrusion (621); When the limiting protrusion (621) is located in the limiting groove (411), the transmission gear (41) and the second clutch (62) are fixed relative to the crankshaft (42) and rotate together with the crankshaft (42), driving the piston (21) to perform linear reciprocating motion; When the limiting protrusion (621) is disengaged from the limiting groove (411), the transmission gear (41) rotates relative to the crankshaft (42), and the piston (21) stops linear reciprocating motion.

5. The rotary impact tool according to claim 4, wherein One of the second clutch (62) and the crankshaft (42) is provided with a guide portion (622), and the other of the second clutch (62) and the crankshaft (42) is provided with a guide groove (623). The guide portion (622) and the guide groove (623) are coupled to limit the rotation of the second clutch (62) relative to the crankshaft (42).

6. The rotary impact tool according to claim 4, wherein A first return spring (65) is provided between the second clutch (62) and the crankshaft (42), and the first return spring (65) has an elastic force that causes the second clutch (62) to abut against the transmission gear (41).

7. The rotary impact tool according to claim 4, wherein The second clutch (62) further comprises a circumferentially protruding annular ridge (624), and the shift paddle (63) is provided with a push portion (633) protruding toward the second clutch (62), wherein within the axial projection plane of the second clutch (62), the projection of the push portion (633) at least partially overlaps with the projection of the annular ridge (624).

8. The rotary impact tool according to claim 7, wherein The plurality of push portions (633) are symmetrically arranged on the outer periphery of the second clutch (62).

9. The rotary impact tool according to claim 1, wherein The shift paddle (63) comprises a driving arm (634), a rotating arm (635) and a connecting portion (636), wherein the rotating arm (635) is arranged on the left and right sides of the hammer transmission assembly (4), and the connecting portion (636) connects the two rotating arms (635).

10. The rotary impact tool according to claim 1, wherein The shift paddle (63) is a sheet metal part.

Images