Three kinetic electric / pneumatic screwdrivers

Abstract

The present application provides a three kinetic energy electric / pneumatic opener, which mainly comprises a high-speed motor device, a reduced reaction force hammer block device, a gear device, an asymmetric clutch device, a torsion spring device and a connecting shaft device; in particular, the three kinetic energy sources of the opener include the high-speed motor device, the reduced reaction force hammer block device and the asymmetric clutch device. The high-speed motor device provides a first kinetic energy with high rotation speed, the reduced reaction force hammer block device increases the rotor weight of the high-speed motor device and increases the rotation speed to obtain a second kinetic energy; the asymmetric clutch utilizes the compression torsion generated by the steel balls with different center distances and the cam track, and the third kinetic energy is obtained by the torsion spring being squeezed, rotated and deformed to form a spiral angle to obtain the energy storage recoil force; in addition, the present application further comprises a hydraulic shock absorbing device, which can reduce the noise amplification caused by the large increase of kinetic energy and achieve the buffering effect, so as to obtain a more accurate working torque value.

Description

Technical Field

[0001] This invention relates to a mechanism improvement of an electric / pneumatic screwdriver, and more particularly to a three-energy electric / pneumatic screwdriver. Background Technology

[0002] Note that the existing impact power wrench 2, such as Figure 1 As shown, the main components include: motor assembly 21, hammer block seat assembly 22, and connecting shaft 23. Figure 2 As shown, the impact principle is as follows: repeated rotational impact is called a rotary impact clutch. When the hammer 24 impacts the connecting shaft 23, it is in the engaged state, generating large torque; after the impact, it is in the disengaged state, and there is no torque. Therefore, the kinetic energy source is: motor assembly + hammer block assembly, totaling 2 kinetic energies. The relationship between the hammer block and the connecting shaft is like hammering a nail; the faster the hammering speed, the greater the force generated. Usually, this type of tool has a pressure regulating valve, which adjusts the motor speed. The faster the speed, the greater the torque; the slower the speed, the less the torque. The tool's final speed is generally between 6000 and 9000 rpm. The advantages of this impact wrench are: fast motor speed, large kinetic energy, small reaction force, and simple structure. The disadvantages are: when the torque reaches the set value, the hammer will produce a hammering sound, and the torque depends on the duration of the hand pressure. Since the kinetic energy generated is mainly derived from speed, the speed affects the torque, causing the screw to be sometimes too tight and stripped, and sometimes too loose and inaccurate. The torque accuracy is generally 50%, which is commonly used in tire repair shops.

[0003] Existing hydraulic pulse screwdrivers 3, such as Figure 3 As shown, the main components include: a motor assembly 31, a hydraulic pulse assembly 32, and a connecting shaft 33. Figure 4 As shown, the principle of this hydraulic pulse screwdriver is as follows: when the blade 34 on the connecting shaft 33 rotates to the high-pressure zone, it is engaged, generating high torque; when it is disengaged in the low-pressure zone, there is no torque. Oil 35 acts as a buffer medium. When the torque is adjusted to the set value, the motor assembly 31 will automatically stop driving, completing the locking. The kinetic energy source is the motor assembly + the hydraulic pulse assembly, totaling two kinetic energy sources. The basic kinetic energy principle of this hydraulic pulse screwdriver is similar to that of an impact wrench, but the hydraulic pulse improves upon the shortcomings of the impact type. It uses hydraulic oil as a buffer medium and utilizes blades to create high and low pressures in the oil. After the motor rotates at high speed, it generates an impact pulse, producing kinetic energy with relatively low noise. Because hydraulic oil does not produce the sound of hammers colliding with the connecting shaft, however, the viscosity changes due to the rise in oil temperature during use, resulting in inaccurate torque, typically within ±15%. The motor speed is approximately 3000–7000 rpm, and the kinetic energy source speed is slightly lower than that of the aforementioned impact wrench.

[0004] In addition, existing semi-automatic clutch screwdrivers 4, such as Figure 5As shown, the main components include: motor assembly 41, gear assembly 42, clutch assembly 43, torsion spring 44, and connecting shaft 45. The kinetic energy source is the motor assembly, totaling 1 unit of kinetic energy. Figure 6 As shown, the principle of this clutch assembly is as follows: In the symmetrically designed cam structure, the distance between the clutch center (C) and the center of the steel ball is the same (r1 = r2), which is called a "symmetrical clutch". Here, T = Fr (T = torque, F1 & F2 = force, r = radius, C = center point). According to the formula, T1 = F1r1, T2 = F2r2, and T1 + T2 is the total torque of the tool (T). T3 + T4 is the force exerted by the hand gripping (reaction force). Since the clutch radius is symmetrical (r1 = r2), the action force equals the reaction force. For example... Figure 7 The diagram shown is a side view of the torsion spring's operation. The clutch assembly 43 includes a steel ball 431, a cam 432 (i.e., the lower clutch and the upper clutch), and a torque washer seat 433. Figure 7 When (A) is in standby mode (no torque), the steel ball 431 of the clutch generates resistance (F) against the cam 432, causing the cam 432 to rise and generate a lifting force (F1 and F2) on the torsion spring 44, which in turn generates a compressive force (S1 and S2). During operation, if force is applied... Figure 7 In the middle (B), the height (L) of the torsion spring 44 gradually shortens, L1 = lower clutch height, L2 = cam rise height; when the cam 432 rises to the top dead center, as... Figure 7 At point C, when the torque reaches its maximum, due to the symmetrical cam design, the steel ball 431 rises and falls synchronously with the cam 432 as it rises and falls. However, the torsion spring 44 and the torsion washer seat 433 do not twist during the rise and fall. This action causes the clutch to rotate, generating kinetic energy in T1 and T2, which is the total torque (total resultant torque) of the tool = T1 + T2. Finally, the cam 432 disengages as... Figure 7 In the middle (D), the torsion spring 44 returns to its original length (L). To summarize the above explanation: because the clutch assembly contains a cam and steel balls, the torsion spring causes the cam to move up and down, thus adjusting the spring force. Most commercially available cordless screwdrivers use a semi-automatic clutch. When the expected torque value is reached, the clutch will slip (a clicking sound), at which point releasing the trigger button completes the operation. Accuracy is affected by human operation and the duration of the strike; the torque is less precise, with an error of approximately ±10% to 30%. Due to the large reaction force, they are generally designed as gun-shaped tools, while straight tools are used to tighten screws smaller than M4.

[0005] Furthermore, existing fully automatic clutch torque automatic stop starter 5, such as Figure 8As shown, the main components include: a valve plate and needle 51, a motor assembly 52, a gear assembly 53, a clutch assembly 54, a torsion spring 55, and a connecting shaft 56. The kinetic energy source is the motor assembly, which provides one unit of kinetic energy. The clutch assembly operates on a symmetrical cam principle, similar to the semi-automatic clutch described above. The difference lies in that when the torque set value is reached, the valve plate and needle 51 automatically stop the motor assembly 52, and the connecting shaft 56 stops rotating, completing the locking process. The automatic shut-off screwdriver is an evolution of the semi-automatic clutch screwdriver. Because the aforementioned semi-automatic clutch has a torque repeatability accuracy of ±10-30%, it cannot meet the international precision requirements of ISO 5393 in professional production lines. This generation of automatic shut-off clutch screwdriver, however, meets the requirements with an accuracy of ±3%. Similar to the semi-automatic clutch, the kinetic energy source is the motor assembly. The gear assembly is responsible for reducing speed. By changing the gear ratio, the speed or torque can be increased; higher torque results in slower speed, and lower torque results in faster speed. Once the torque reaches the preset value, the clutch assembly automatically shuts off the motor assembly and stops rotation, completing the screw tightening process, thus ensuring high torque accuracy. The torque spring adjusts the torque value. The reaction force is relatively large; when tightening large screws, a torque arm is required to prevent operator injury. In view of this, the inventors of this invention deeply felt that existing automated tools still had room for improvement and were not yet perfect. Therefore, relying on years of accumulated design experience and continuous experimentation, they finally developed this more practical invention. Summary of the Invention

[0006] The main objective of this invention is to provide a three-energy electro / pneumatic screwdriver. By superimposing the three energy devices designed by the inventor, the screwdriver has greater energy, lower working force, higher precision, and a buffer when the power stops. The clutch disengagement is smoother, noise is reduced, the operator's feel is more comfortable, and the energy and performance are better.

[0007] To achieve the above objectives, the present invention provides a three-energy electro / pneumatic screwdriver, comprising: a high-speed motor device, a reaction-reducing hammer device, a gear device, an asymmetric clutch device, a torsion spring device, and a connecting shaft device. Specifically, the screwdriver's kinetic energy sources include: the high-speed motor device, the reaction-reducing hammer device, and the asymmetric clutch device, totaling three kinetic energy sources. The high-speed motor device provides the first kinetic energy, enabling high-speed rotation. The reaction-reducing hammer device, attached to the high-speed motor device, increases the rotor weight, thereby increasing the rotational speed and torque, thus providing the second kinetic energy. The asymmetric clutch utilizes the compressive torque generated by two second steel balls with different center distances and the cam track, as well as the helix angle created by the compression and rotation of the torsion spring, to obtain the third kinetic energy, which stores torque (ejection force).

[0008] In a preferred embodiment, the high-speed motor device has a rotor and an outer seat. A needle is inserted through the shaft of the rotor. One end of the rotor is provided with a valve plate and a spring for support. A main gear is connected to the other end of the rotor relative to the valve plate.

[0009] In a preferred embodiment, the reaction force reducing hammer device includes: one or more fixed screw hammers, a reaction force hammer, a hammer fixing seat, a C-ring, and a plurality of first steel balls. The hammer fixing seat is fixed by the C-ring in combination with the reaction force hammer. The reaction force hammer has a recessed groove on its circumference, and a receiving groove is formed on one side of the groove. The fixed screw hammer is placed in the receiving groove and one end passes through the circumference of the hammer fixing seat and is fixed by the first steel balls.

[0010] In a preferred embodiment, the asymmetric clutch device consists of an upper clutch, a second steel ball, and a lower clutch. The surface of the upper clutch has two inner and outer cam tracks with different center distances. A second steel ball is disposed on each of the two cam tracks and supported by the lower clutch.

[0011] In a preferred embodiment, the torsion spring device includes a torsion cylinder covering the torsion spring, a torsion cylinder washer seat, and a torsion adjusting ring. One end of the torsion spring abuts against the lower clutch, and the other end abuts against the torsion cylinder washer seat. The torsion adjusting ring provides the torsion spring with a tight or loose state.

[0012] In a preferred embodiment, one end of the connecting shaft device is provided with a striker and a striker ball, which are connected to the shaft of the rotor, and the other end is provided with a tool head.

[0013] In a preferred embodiment, the hydraulic shock absorber includes a hydraulic outer seat and a lower clutch piston that is coupled to the lower clutch. The space between the lower clutch piston and the hydraulic outer seat has an upper liquid groove, a lower liquid groove, and a hydraulic hole connecting the upper and lower liquid grooves. The upper liquid groove has an oil injection hole and an oil injection screw. The lower liquid groove has an oil leak-proof seal that abuts against the hydraulic hole and an oil leak-proof washer that abuts against a return spring.

[0014] The expected benefits achieved by this invention include: 1. Two additional buffer cams on the asymmetrical clutch device release the kinetic energy of the later part of the pulse, providing a buffer after the motor stops, resulting in a smoother pulse and a more comfortable operating experience. 2. An additional reaction force reducing hammer device is added to the asymmetrical clutch device to reduce the reaction force while maintaining the high precision of the clutch. 3. When the torque of the fully automatic clutch reaches the set value, the clutch automatically disengages, and the air valve plate automatically shuts off the air, resulting in more precise torque (±3%), meeting the precision requirements of ISO5393. 4. The asymmetrical clutch is positioned in the torque cylinder, ensuring that the torque washer seat remains fixed and clamps the torque spring and lower clutch, allowing the torque spring to twist and generate new kinetic energy. 5. Without reducing resistance, the spring force accelerates the connecting shaft device to generate rotational kinetic energy. This process adds an extra torque for storing kinetic energy, increasing the total torque. Simultaneously, the reaction force decreases when locking the same torque; actual tests show a reduction of 25% to 50% in reaction force. Attached Figure Description

[0015] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0016] Figure 1 This is an exploded view of the mechanism of a conventional impact power wrench;

[0017] Figure 2 yes Figure 1 A schematic diagram illustrating the principle and operation of an impact power wrench;

[0018] Figure 3 This is an exploded view of the mechanism of a conventional hydraulic pulse screwdriver;

[0019] Figure 4 yes Figure 3 Schematic diagram of the principle and operation of a hydraulic pulse screwdriver;

[0020] Figure 5 This is an exploded view of the mechanism of a conventional semi-automatic clutch screwdriver;

[0021] Figure 6 yes Figure 5 A schematic diagram of the principle of a semi-automatic clutch screwdriver;

[0022] Figure 7 yes Figure 5 A schematic diagram of the operation of a semi-automatic clutch screwdriver;

[0023] Figure 8 This is an exploded view of the mechanism of a conventional fully automatic clutch screwdriver;

[0024] Figure 9 This is an exploded view of the screwdriver composition according to a preferred embodiment of the present invention;

[0025] Figure 10 This is a cross-sectional view of the overall structure of a screwdriver according to a preferred embodiment of the present invention;

[0026] Figure 11(A) is a schematic diagram of a device for increasing the kinetic energy of a screwdriver according to a preferred embodiment of the present invention;

[0027] Figure 11(B) is a perspective view of a device for increasing the kinetic energy of a screwdriver according to a preferred embodiment of the present invention;

[0028] Figure 11(C) is a schematic diagram of the screwdriver operation according to a preferred embodiment of the present invention;

[0029] Figure 12(A) shows the cam structure of a prior art symmetrical clutch;

[0030] Figure 12(B) shows the cam structure of an asymmetric clutch device according to another preferred embodiment of the present invention;

[0031] Figure 13 This is a schematic diagram showing an additional new displacement energy in the asymmetric clutch device of another preferred embodiment of the present invention;

[0032] Figure 14 This is a side view of the torsion spring in Figure 12.

[0033] Figure 15 It is a table of kinetic energy changes when the screwdriver is tightened and the screw is fastened in an asymmetrical clutch, using a screw dynamic simulator.

[0034] Figure 16 It is a table of kinetic energy changes of a screwdriver with a symmetrical clutch when tightening a screw, using a screw dynamic simulator;

[0035] Figure 17(A) is a reverse view of the operation of a hydraulic shock absorber according to a preferred embodiment of the present invention (a).

[0036] Figure 17(B) is a reverse view of the operation of a hydraulic shock absorber device according to a preferred embodiment of the present invention (II);

[0037] Figure 17(C) is a reverse view of the operation of a hydraulic shock absorber device according to a preferred embodiment of the present invention (III);

[0038] Figure 17(D) is a reverse view of the operation of a hydraulic shock absorber device according to a preferred embodiment of the present invention (IV);

[0039] Figure 17(E) is a reverse view of the operation of a hydraulic shock absorber device according to a preferred embodiment of the present invention (V);

[0040] Figure 17(F) is an enlarged view of point A in Figure 17(B);

[0041] Figure 17(G) is an enlarged view of point A in Figure 17(C);

[0042] Figure 17(H) is an enlarged view of point A in Figure 17(D);

[0043] Figure 18 This is a schematic diagram of the external adjustment control of a hydraulic pulse device according to a preferred embodiment of the present invention;

[0044] Figure 19 This is a graph (a) showing the change in screwdriver torque over time according to a preferred embodiment of the present invention;

[0045] Figure 20 This is a graph (II) showing the change in screwdriver torque over time according to a preferred embodiment of the present invention;

[0046] Figure 21 This is a graph (III) showing the change in screwdriver torque over time according to a preferred embodiment of the present invention.

[0047] Explanation of reference numerals in the attached figures

[0048] 2. Impact power wrench; 21-motor set;

[0049] 22. Hammer block seat assembly; 23. Connecting shaft;

[0050] 24. Hammer block;

[0051] 3. Hydraulic pulse screwdriver; 31. Motor assembly;

[0052] 32. Hydraulic pulse assembly; 33. Connecting shaft;

[0053] 34. Leaf blade; 35. Oil;

[0054] H, high-pressure zone; L, low-pressure zone;

[0055] 4. Semi-automatic clutch screwdriver; 41. Motor assembly;

[0056] 42. Gear set; 43. Clutch set;

[0057] 431. Steel ball; 432. Cam;

[0058] 433. Torque washer seat; 44. Torque spring;

[0059] 45. Connecting shaft;

[0060] 5. Fully automatic clutch torque-stop screwdriver;

[0061] 51. Valve plate and needle; 52. Motor assembly;

[0062] 53. Gear set; 54. Clutch set;

[0063] 55. Torsion spring; 56. Connecting shaft;

[0064] This invention:

[0065] 1. Three kinetic energy electric / pneumatic screwdrivers; 11. High-speed motor device;

[0066] 111. Rotor; 112. Inner and outer bearings;

[0067] 113. Needle; 114. Valve plate;

[0068] 115. Single-slot spring; 116. Main gear;

[0069] 12. Reaction force reducing hammer block device; 121. Fixed screw hammer;

[0070] 122. Reaction hammer; 123. Hammer fixing seat;

[0071] 124. Ring C; 125. First steel ball;

[0072] 126. Planetary gear; 13. Gear assembly;

[0073] 14. Asymmetrical clutch device; 141. Upper clutch;

[0074] 142. Second steel ball; 143. Lower clutch;

[0075] 144. Cam track; 15. Torsion spring device;

[0076] 151. Torsion spring; 152. Torsion cylinder;

[0077] 153. Torque cylinder washer seat; 154. Torque adjusting ring;

[0078] 16. Connecting shaft assembly; 161. Strike pin;

[0079] 162. Firing pin and steel ball; 163. Tool head;

[0080] 17. Hydraulic shock absorber; 171. Hydraulic outer seat;

[0081] 172. Lower clutch piston; 173. Upper fluid tank;

[0082] 174. Lower liquid tank; 175. Hydraulic port;

[0083] 176. Oil filling hole; 177. Oil filling screw;

[0084] 178A, Leak-proof washer; 178B, Leak-proof oil seal;

[0085] 179. Returning spring; Opening A;

[0086] Opening B; Opening C. Detailed Implementation

[0087] Please cooperate as follows Figure 9 , Figure 10As shown, the present invention proposes a three-energy electro / pneumatic screwdriver 1, comprising: a high-speed motor device 11, a reaction force reducing hammer device 12, a gear device 13, an asymmetric clutch device 14, a torsion spring device 15, and a connecting shaft device 16. The high-speed motor device 11 has a rotor 111 and a middle and outer seat 112, and a needle 113 is provided on the shaft of the rotor 111. One end of the needle 113 is provided with a valve plate 114 and a spool spring 115 for controlling the opening and closing of the high-speed motor device 11. The other end of the rotor 111 relative to the valve plate 114 has a main gear 116. The reaction force reducing hammer block device 12 features low after-effect force and high torque, including one or more fixed screw hammers 121, a reaction force hammer 122, a hammer fixing seat 123, a C-ring 124, and multiple first steel balls 125. The main gear 116 of the rotor 111 is pressed into the hammer fixing seat 123, and then the reaction force hammer 122 is placed inside. The hammer fixing seat 123 is fixed to the reaction force hammer 122 by the combination of the C-ring 124 and the reaction force hammer 122. The circumferential surface of the reaction force hammer 122 forms a... The device features a recessed slot with a receiving groove on one side. A fixing hammer 121 is placed within this groove, with one end passing through the circumference of a hammer fixing seat 123 and secured by a first steel ball 125. A planetary gear 126 engages below it for transmission. When the high-speed motor 11 starts, the fixing hammer 121 is driven upwards and strikes a reaction hammer 122. As the speed decreases, the fixing hammer 121 moves downwards and strikes the hammer fixing seat 123. The gear device 13 engages upwards with the planetary gear 126 to connect and transmit power to the high-speed motor 11. The asymmetrical clutch device 14 consists of an upper clutch 141, a second steel ball 142, and a lower clutch 143. The lower surface of the upper clutch 141 has two inner and outer cam tracks 144 with different diameters. A second steel ball 142 is disposed within each of the two cam tracks 144, and the lower clutch 143 provides support, thus forming an asymmetrical clutch mechanism. The torsion spring device 15 includes a torsion cylinder 152 covering the torsion spring 151, a torsion cylinder washer seat 153, and a torsion adjusting ring 154. One end of the torsion spring 151 abuts against the lower clutch 143, and the other end abuts against the torsion cylinder washer seat 153. When the torsion spring 151 is tightened by the torsion adjusting ring 154, the torque increases; when it is loosened, the torque decreases. One end of the connecting shaft device 16 is provided with a striker 161 and a striker ball 162 for connecting and moving with the shaft of the rotor 111, and the other end is provided with tool heads 163 that fit into various functions and shapes.

[0088] The present invention provides three devices for increasing kinetic energy in a three-phase electric / pneumatic screwdriver: a high-speed motor device 11, a reaction force reducing hammer device 12, and an asymmetric clutch device 14. The high-speed motor device 11 provides the first kinetic energy for basic rotational power; in this example, its rotational speed is between 20,000 and 40,000 rpm. The function of the reaction force reducing hammer device 12 is to increase the rotational mass of the high-speed motor device 11, thereby increasing the kinetic energy to a second kinetic energy, and enabling the screwdriver to achieve low reaction force and high precision, with repeatability meeting the precision requirements of ISO 5393 for screw fastening. Its principle is as follows:

[0089]

[0090] From the above kinetic energy formula, we know that: mass m and velocity V 2 The magnitude of kinetic energy is determined by, in particular, velocity V. 2 Therefore, a different concept was designed using the formula, increasing the rotational speed of the high-speed motor device, but ultimately reducing the speed to the connecting shaft device, to achieve maximum kinetic energy, most precise torque, light weight, and low reaction force. Furthermore, the kinetic energy formula proves that V is the square of the velocity; the higher the rotational speed, the greater the kinetic energy and the smaller the reaction force. Based on the hammer principle of existing impact wrenches, this invention adds a reaction force-reducing hammer device to the rotor of the high-speed motor device. Because the overall mass (m) is increased and the rotational speed is increased, the kinetic energy is increased, thus achieving the highest efficiency for the high-speed motor.

[0091] Please Figure 11(A) , 11(B) Figure 11(C) shows a preferred embodiment of the device for increasing the kinetic energy of a screwdriver and its operation schematic diagram. The reaction force reducing hammer block device 12 is attached to the rotor 111 of the high-speed motor device 11 in the power output direction and includes: one or more fixing screw hammers 121, a reaction force hammer 122, a hammer fixing seat 123, a C-ring 124, and a plurality of first steel balls 125. As can be seen from the kinetic energy formula, mass (m) affects kinetic energy. In the design, a lighter material such as aluminum is used for the inner ring of the hammer fixing seat 123, so that the high-speed motor device 11 saves more power when starting. After starting, the fixing screw hammer 121 will hammer the reaction force hammer 122. Therefore, the outer ring of the reaction force hammer 122 is made of a heavier material such as steel, so that the high-speed motor device 11 has lighter and better kinetic energy and performance.

[0092] Please Figure 12(A) and 12(B)As shown, another preferred embodiment of the present invention discloses a device for increasing the kinetic energy of a screwdriver and a schematic diagram of its operation; wherein Figure 12(A) shows the cam structure of a prior art symmetrical clutch, including a cam (c1) and a cam (c2) with a track (t) at a relative position; Figure 12(B) shows the cam structure of an asymmetrical clutch device, including two non-interfering inner and outer tracks (t1, t2) and cams (c3), cam (c4) and two buffer cams (c5). Furthermore, the distance between the cam and the center (r1≠r2) is different from the distance between the cam and the center of a prior art symmetrical clutch (r1=r2). Please refer to... Figure 13 As shown, the asymmetric clutch device 14 adds a new displacement kinetic energy, where the torque formula is T = Fr (T = torque, F1 & F2 = force, r = radius), and C = center point. The principle is as follows: In the asymmetric cam design, r1 and r2 have different radii. According to the above formula, T1 = F1r1, T2 = F2r2, and T3 = F3r3. The sum of these is the total torque of the tool (T1 + T2 + T3). Compared with the symmetrical cam, a new kinetic energy T3 is added. Furthermore, since the radii of the two cams in the asymmetric clutch device 14 are (r1 ≠ r2), the action force ≠ reaction force; the larger the action force, the smaller the reaction force.

[0093] Please repeat Figure 14 As shown, a side view of the torsion spring 151 is disclosed. The following is an explanation of the operation diagram: Figure 14 In the standby (no torque) state (A), the second steel ball 142 of the asymmetric clutch device 14 generates resistance (F) against the cam 144. Simultaneously, the rising cam 144 generates a lifting force (F1 and F2) on the torsion spring 151, which in turn generates a compressive force (S1 and S2). L1 = lower clutch height, L2 = cam rise height. For example... Figure 14 When force is applied during operation (B), the high-speed motor is forced to rotate with the bearing as the center point (C). However, due to the asymmetrical cam structure (r1≠r2), the radius of r1 is smaller than that of r2. According to the above formula, F1 is greater than F2. The second steel ball 142, like a car wheel, obliquely pushes the clutch 143. With a smaller radius of r1, the second steel ball 142 rotates relatively faster. Conversely, with a larger radius of r2, the second steel ball 142 rotates slower. The two rolling second steel balls 142 will generate an inner wheel difference due to the asymmetrical track. The second steel ball 142 begins to rotate and drives the clutch 143 to rotate, generating an inner wheel difference and speed difference similar to that when a car rotates. This causes the torsion spring 151 to gradually twist, generating a helix angle (α3) and beginning to store energy. Figure 14In the middle (C), when cam 144 rises to the top dead center (i.e., the highest point), it reaches its maximum torque. At the maximum of T1 and T2, kinetic energy is released simultaneously, generating the maximum torsional thrust (T3), which is displacement energy. Therefore, the total torque (total resultant torque) of the screwdriver = T1 + T2 + T3, resulting in greater force. For example... Figure 14 In the middle (D), the cam 144 of the asymmetric clutch device 14 has disengaged. At this time, the resistance of the rolling second steel ball 142 and the cam 144 immediately becomes zero. The asymmetric track generates an inner wheel difference and slips, like a pull-back toy car. When the hand is about to release the pull-back car, the spring releases the previously stored kinetic energy, causing the wheels to start rotating and moving forward. Therefore, there are two different types of forces driving the action, namely, an additional elastic potential energy is added to launch F3. Figure 14 When the operation stops (E), the locking is completed, and the torsion spring 151 returns to its original state.

[0094] Please Figure 15 , Figure 16 The table shown illustrates the kinetic energy changes of screwdrivers with symmetrical and asymmetrical clutches when tightening screws, using a screw dynamics simulator. This demonstrates that the asymmetrical clutch mechanism generates additional kinetic energy from the ejection force. Figure 15 As shown, the thick black line indicates a sudden drop of 30 rpm in speed at 0.13 seconds, proving slippage. Generally, a proportional linear clutch wouldn't slip. At 0.14 seconds, both the thick black line (speed) and the thin gray line (torque) simultaneously reach their maximum values. This phenomenon indicates that after slippage, the stored spring potential energy is released simultaneously, generating both speed and maximum torque (the sum of T1+T2+T3). Then the motor stops, and both speed and torque return to zero. Figure 16 The table shown illustrates the kinetic energy change of a conventional symmetrical clutch. The thick black line represents the rotational speed; under motor load, the speed slowly decreases to 450 rpm and then stops rotating after 0.7 seconds. The thin gray line represents the torque; the clutch increases linearly proportionally, with maximum torque at approximately 6 N·m. Unlike asymmetrical clutches, there is no slippage or ejection force.

[0095] Please Figures 17(A)-17(H)The diagram shows the structure and operation of the hydraulic shock absorber. The hydraulic shock absorber 17 is located above the torque cylinder 152 to reduce the rebound force of the torsion spring 151. It includes: a hydraulic outer seat 171 and a lower clutch piston 172 connected to the lower clutch 143. The space between the lower clutch piston 172 and the hydraulic outer seat 171 has an upper liquid groove 173, a lower liquid groove 174 and a hydraulic hole 175 connecting the upper liquid groove 173 and the lower liquid groove 174. There is an oil injection hole 176 on the upper liquid groove 173 and an oil injection screw 177 inside. There is a leak-proof oil seal 178B in the lower liquid groove 174 that abuts against the hydraulic hole 175 and a leak-proof washer 178A that abuts against the return spring 179. The leak-proof oil seal 178B is made of a soft material, such as rubber, to block the hydraulic hole 175 and achieve a good sealing effect. The leak-proof washer 178A is made of a hard material, such as metal, to support the soft material leak-proof oil seal 178B and is supported by the return spring 179 below. The leak-proof oil seal 178B and leak-proof washer 178A are controlled by the displacement of the lower clutch piston 172 to control the flow rate of the liquid and the speed of the up and down movement of the lower clutch piston 172. Figure 17(A) shows the screwdriver in standby mode; Figures 17(B) and 17(F) show the screwdriver after startup. When the lower clutch rises, the cam and the lower clutch piston 172 rise, and the liquid in the upper liquid tank 173 pushes the leak-proof oil seal 178B and leak-proof washer 178A downward through the hydraulic hole 175 to form an opening A, allowing the liquid to flow from the opening A to the lower liquid tank 174, and causing the return spring 179 to descend; Figures 17(C) and 17(G) show that when the cam rises to its highest point (top dead center), the opening B of the leak-proof oil seal 178B forms the maximum liquid flow. Excessive torque is the maximum torque of the screwdriver's locking screw. As shown in Figures 17(D) and 17(H), when the cam disengages, the oil filler screw 177 will block the leak-proof oil seal 178B, preventing the lower clutch piston 172 from moving. At this time, the gap of opening C is smaller than that of opening B, and the liquid flows back from the lower liquid groove 174 to the upper liquid groove 173. The return spring 179 resets, and the lower clutch piston 172 also slowly descends to its original position. At this time, the screwdriver is about to complete the screw fastening. As shown in Figure 17(E), the screwdriver has completed the screw fastening and returned to the standby state, and can be used to fasten the screw again.

[0096] As mentioned above, because the lower clutch piston 172 reduces the downward pushing force of the torsion spring 151 and the lower clutch 143, the torsion spring 151 will not cause noise from the continuous impact between the second steel ball 142 and the lower clutch 143, thus reducing the noise level. In particular, when the screwdriver tightens each screw, the lower clutch only disengages once (One Pulse), without any continuous jumping, and automatically stops when the torque value is reached (Auto Shut-Off), resulting in high torque accuracy, unlike the continuous pulse (jumping phenomenon) of general hydraulic pulse-type tools.

[0097] Furthermore, regarding the screwdriver structure of this invention, the torsion spring pressure varies between high and low torque, and the rotation speed varies between fast and slow. Therefore, two mechanical structures are designed: one for faster rotation speed and higher torque, requiring an internal adjustment tool; and one for slower rotation speed and lower torque, requiring an external adjustment tool. Please see below. Figure 18 As shown, the screwdriver of this invention uses an external torque adjustment structure. The torque can be easily adjusted by simply rotating the control torque adjustment ring. Because it uses a compression torque spring, the compression force can be linearly proportional, and the target torque value can be obtained very accurately, which meets the ISO5393 accuracy requirements.

[0098] Please Figures 19-21 The figures shown are graphs displaying the torque versus time changes of the screwdriver using the present invention. The biggest difference between the hydraulic shock absorber of the present invention and existing technologies is that it only disengages once when the same tool is subjected to high torque. Figure 19 When adjusted to low torque, a pulse (jumping) phenomenon may occur, and in all these situations, the reaction force is small. For example... Figure 20 As observed in the diagram, the torque initially at its maximum gradually decreases over time until the motor automatically stops, completing the locking process. Furthermore, commercially available rotary hydraulic pulse or impact tools typically exhibit a gradual increase in torque over time, starting with a lower initial torque. Figure 21 Due to variations in oil temperature and viscosity, or differences in the number and duration of impacts, the stopping time for each tightening operation can be inconsistent. Therefore, this invention overcomes the shortcomings of traditional designs (such as hydraulic pulse, mechanical impact, and semi-automatic clutch types) by innovating with a hydraulic shock absorber (continuous jump). Even with varying durations, the torque remains precise, making this an innovative structure for achieving accurate torque tightening of screws.

[0099] In summary, the present invention employs a combination of a high-speed motor, a reaction force reducing hammer, and an asymmetric clutch to form a design with three kinetic energies added together. This design surpasses existing technologies in terms of speed and torque output. Furthermore, the use of a hydraulic shock absorber further reduces the noise generated by the significant increase in speed and torque, effectively reducing the number of clutch disengagements during screw fastening to once, while simultaneously improving the torque accuracy when fastening screws.

[0100] However, the above description is only a preferred embodiment of the present invention. Therefore, any equivalent structural changes made by applying the present invention specification and claims should be included within the patent scope of the present invention.

Claims

1. A three-energy electro / pneumatic screwdriver, characterized in that, include: A high-speed motor device provides a first kinetic energy, having a rotor and an outer seat, a needle passing through the rotor shaft, and a valve plate at one end of the needle, with a spring abutting above the valve plate, and a main gear connected to the other end of the rotor. A reaction force reducing hammer block device provides a second kinetic energy, which is added to the power output direction of the rotor of the high-speed motor device and is penetrated by the rotor. It includes a fixing screw hammer, a reaction force hammer, a hammer fixing seat, a C-ring and a plurality of first steel balls. The hammer fixing seat is fixed by the C-ring and the reaction force hammer. The reaction force hammer has a recessed groove on its circumference. A receiving groove is formed on one side of the groove. The fixing screw hammer is placed in the receiving groove. One end of the fixing screw hammer passes through the hammer fixing seat and is connected and fixed by the first steel balls. It passes through the rotor end edge of the reaction force reducing hammer block device and then meshes with a planetary gear disk. A gear mechanism for connecting the combined output of the first kinetic energy and the second kinetic energy, including one or more gears meshing with the planetary gear disk to connect the power output of the high-speed motor device; An asymmetric clutch device provides a third kinetic energy, which is superimposed on the first kinetic energy and the second kinetic energy. It includes an upper clutch, a second steel ball, and a lower clutch. The surface of the upper clutch has two inner and outer cam tracks with different center distances. The second steel ball is respectively arranged on the inner and outer cam tracks and is clamped and positioned by the lower clutch. A torsion spring device includes a torsion spring, one end of which abuts against the lower clutch, and the other end abuts against a torsion cylinder washer seat, and is covered by a torsion cylinder and a torsion adjusting ring to control the tension of the torsion spring; and A connecting shaft device has a striker at one end that abuts against the striker and is connected to the lower clutch. The striker is coupled with two striker balls to limit displacement. A tool head is provided at the other end of the connecting shaft device.

2. The three kinetic energy electro / pneumatic screwdrivers as described in claim 1, characterized in that, It also includes a hydraulic shock absorber, comprising a hydraulic outer seat, a lower clutch piston connected to the lower clutch, and an upper liquid groove, a lower liquid groove, and a hydraulic hole connecting the upper liquid groove and the lower liquid groove within the space between the lower clutch piston and the hydraulic outer seat. An oil injection hole is provided on the upper liquid groove, and an oil injection screw is provided inside. An oil leakage seal is provided in the lower liquid groove to abut against the hydraulic hole, and an oil leakage washer is provided to abut against a return spring.

3. The three kinetic energy electro / pneumatic screwdrivers as described in claim 1, characterized in that, The reaction force reducing hammer block device includes one or more fixed screw hammers, which are evenly distributed around the periphery of the hammer fixing seat.

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