Three-kinetic-energy electric / pneumatic screwdriver

Abstract

The invention provides a three-kinetic-energy electric / pneumatic screw driver. The three-kinetic-energy electric / pneumatic screw driver mainly comprises a high-speed motor device, a counter-acting force reducing hammer block device, a gear device, an asymmetric clutch device, a torsion spring device and a connecting shaft device. Particularly, three kinetic energy sources of the screwdriver comprise a high-speed motor device, a counter-acting force reducing hammer block device and an asymmetric clutch device. The high-speed motor device provides first kinetic energy with high rotating speed, and the counter-acting force reducing hammer block device increases the weight of a rotor of the high-speed motor device and increases the rotating speed to obtain second kinetic energy; according to the asymmetric clutch, third kinetic energy of energy storage ejection force is obtained through compression torsion generated by two steel balls with different center distances and a cam track and a helical angle formed by extrusion, rotation and deformation of a torsion spring; in addition, the hydraulic anti-vibration device is further included, the noise amplification caused by the fact that the kinetic energy is greatly increased can be reduced, the buffering effect is achieved, and a more accurate working torsion value is obtained.

Description

Technical Field

[0001] The invention relates to a structural improvement of an electric / pneumatic screwdriver, in particular to a three-kinetic-energy electric / pneumatic screwdriver. Background Art

[0002] According to the prior art impact wrench 2, Figure 1 As shown, the main mechanism comprises: a motor group 21, a hammer block seat group 22, and a connecting shaft 23. Figure 2 As shown, the impact principle is: repeated rotation and striking is called a rotary impact clutch. When the hammer block 24 impacts the connecting shaft 23, it is in a closed state, generating a large torque; after the impact is completed, it is in an open state, and there is no torque. Therefore, the source of kinetic energy is: motor group + hammer block seat group, a total of 2 kinetic energies. The relationship between the hammer block seat and the connecting shaft is like hammering a nail with a hammer. The faster the hammering speed, the greater the force generated. Usually, there is a pressure regulating valve on this type of tool, which is used to adjust the motor speed. The faster the speed, the greater the torque, and the slower the speed, the smaller the torque. The final speed of the tool generally falls between 6000 and 9000 rpm. The advantages of this impact wrench: fast motor speed, large kinetic energy, small reaction force and simple structure. Disadvantages: When the torque reaches the set value, the hammer block will produce a hammering sound, and the torque depends on the time of hand pressing. Since the kinetic energy generated is mainly derived from the speed, the speed affects the torque, causing the locking screws to be too tight and slip, or too loose and inaccurate. The general torque accuracy is 50%, which is commonly used in tire repair shops.

[0003] The oil pressure pulse screwdriver 3 of the prior art, such as Figure 3 As shown, the main mechanism components include: motor group 31, oil pressure pulse group 32, and connecting shaft 33. Figure 4 As shown, the principle of the oil pulse is: when the blade 34 on the connecting shaft 33 rotates to the high pressure area, it is closed and generates a large torque; when it is in the low pressure area, it is separated and there is no torque. Oil 35 is a buffering medium. When the torque is adjusted to the set value, the motor group 31 will automatically stop driving and complete the locking. Kinetic energy source: motor group + oil pulse group, a total of 2 kinetic energies. The basic kinetic energy principle of the oil pulse screwdriver is similar to that of the impact wrench, but the oil pulse improves the shortcomings of the impact type. It uses hydraulic oil as a buffering medium and uses blades to make the oil produce high and low pressures. After the motor rotates at high speed, an impact pulse is generated, which generates kinetic energy and has a relatively low noise value. Because the hydraulic oil does not have the sound of the hammer hitting the connecting shaft, but when used, the viscosity will change due to the increase in oil temperature, and the torque is inaccurate. The accuracy is generally about ±15%, and the motor speed is about 3000~7000rpm. The kinetic energy source speed is slightly lower than the aforementioned impact wrench.

[0004] In addition, the semi-automatic clutch screwdriver 4 of the prior art, such as Figure 5As shown, the main mechanism components include: motor group 41, gear group 42, clutch group 43, torsion spring 44, connecting shaft 45. Kinetic energy source: motor group, totaling 1 kinetic energy. Figure 6 As shown, the principle of the clutch group is: the cam structure with a symmetrical design has the same distance between the clutch center (C) and the steel ball center (r1=r2), which is called a "symmetrical clutch", where T=Fr (T=torque, F1&F2=force, r=radius, C=center point). According to the formula, T1=F1r1, T2=F2r2, T1+T2 is the total torque of the tool (T), and T3+T4 is the hand grip force (reaction force). Since the clutch radius is symmetrical (r1=r2), the action force=reaction force. For example Figure 7 The torsion spring side view action diagram shown in the figure, the clutch group 43 includes a steel ball 431, a cam 432 (ie, a lower clutch, an upper clutch), and a torsion washer seat 433, wherein Figure 7 When (A) is in standby mode (no torque value), the steel ball 431 of the clutch generates resistance (F) on the cam 432, and the cam 432 rises, generating an upward force (F1 and F2) on the torsion spring 44, and the torsion spring 44 generates a compression force (S1 and S2); when the force is applied during operation, Figure 7 In (B), the height (L) of the torsion spring 44 gradually becomes shorter, L1 = lower clutch height, L2 = cam rise height; when the cam 432 rises to the top dead center, as shown in FIG. Figure 7 In (C), when the torque reaches the maximum value, due to the symmetrical cam design, when the cam 432 rises and falls, the steel ball 431 also rises and falls synchronously, but the torsion spring 44 and the torsion washer seat 433 do not twist when rising and falling. The above action causes the clutch to rotate, so that T1 and T2 generate kinetic energy, which is the total torque (total torque) of the tool = T1 + T2; finally, the cam 432 jumps out of the way. Figure 7 In (D), the length (L) of the torsion spring 44 returns to its original state. Summarizing the above description, it can be seen that since the clutch group is provided with a cam and a steel ball, the torsion spring causes the cam to bounce up and down to adjust the elastic force. Generally, commercially available rechargeable screwdrivers all use a semi-automatic clutch. When the screw locking reaches the expected torque value, the clutch will slip (a clacking sound), and the hand releases the trigger button to complete the task. The accuracy will be affected by manual operation and the length of the striking time, and the torque is less accurate, with an error of about ±10 to 30%. Due to the large reaction force, they are generally designed as gun-type tools, and straight tools are used to lock screws below M4.

[0005] Furthermore, the fully automatic clutch torque automatic stopper 5 of the prior art, such as Figure 8As shown, the main mechanism components include: valve plate and needle 51, motor group 52, gear group 53, clutch group 54, torsion spring 55, and connecting shaft 56. Kinetic energy source: The motor group has a total of 1 kinetic energy. The principle of the clutch group is: symmetrical cam principle, just like the symmetrical principle of the aforementioned semi-automatic clutch, the only difference is: when the torque setting value is reached, the valve plate and needle 51 will automatically stop the motor group 52, and the connecting shaft 56 will no longer rotate, and the lock is completed. The torque automatic stop screwdriver (Auto shut-off Screwdriver) is an evolved version of the semi-automatic clutch screwdriver. Since the aforementioned semi-automatic torque repeatability accuracy reaches ±10~30%, it cannot pass the international accuracy requirement standard of ISO5393 in professional production lines, but this generation of clutch torque automatic stop screwdriver can meet it, with an accuracy of up to ±3%. Like the semi-automatic torque, the kinetic energy source is the motor group. The gear group is responsible for reducing the speed. The speed or torque can be increased by changing the speed ratio. The torque is large and the speed is slow; the torque is small and the speed is fast. When the torque reaches the expected set value, the clutch group will automatically shut down the motor group (Auto Shut-off) and stop rotating to complete the screw locking, so the torque accuracy is high. The torsion spring is responsible for adjusting the torque value. The reaction force is large, and a robot arm (Torque Arm) must be used when locking large screws to prevent the operator from being injured. In view of this, the inventor of the present invention deeply felt that the existing automatic tools are still not perfect and there is room for improvement. Therefore, relying on the design experience accumulated over many years, after continuous experiments, a more practical present invention was finally produced. Summary of the invention

[0006] The main purpose of the present invention is to provide a three-kinetic-energy electric / pneumatic screwdriver. By superimposing the three kinetic energy devices designed by the inventor, the screwdriver has greater kinetic energy, lower back force, higher precision in operation, and there is buffering when the power stops, the clutch jumps out more smoothly, the noise can be reduced, the operator feels more comfortable, and better kinetic energy and performance are obtained.

[0007] In order to achieve the above-mentioned purpose, the present invention provides a three-kinetic-energy electric / pneumatic screwdriver, including: a high-speed motor device, a reaction-force-reducing hammer device, a gear device, an asymmetric clutch device, a torsion spring device and a connecting shaft device. In particular, the kinetic energy sources of the screwdriver include: a high-speed motor device, a reaction-force-reducing hammer device and an asymmetric clutch device, which together have three kinetic energies. The high-speed motor device is the first kinetic energy for providing high-speed rotational power; the reaction-force-reducing hammer device is attached to the high-speed motor device to increase the rotor weight of the high-speed motor device and to increase the rotation speed and torque to obtain the second kinetic energy; the asymmetric clutch utilizes the compression torsion generated by the second steel balls at two different center distances and the cam track and the helical angle caused by the extrusion and rotation deformation of the torsion spring to obtain the third kinetic energy of energy storage torque (ejection force).

[0008] In a preferred embodiment, the high-speed motor device has a rotor and an inner and outer seat, a needle is passed through the axis of the rotor, a valve plate is provided at one end of the rotor and a straight spring is provided to support it, and a main gear is combined with 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 fixing 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 combining the C ring with the reaction force hammer. A concave notch is formed on the circumference of the reaction force hammer, and a receiving groove is formed on one side of the notch. The fixing screw hammer is placed in the receiving groove and one end thereof passes through the circumference of the hammer fixing seat and is connected and 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 upper clutch surface has inner and outer cam tracks with two different center distances. A second steel ball is respectively arranged on the two cam tracks and supported by the lower clutch.

[0011] In a preferred embodiment, the torsion spring device includes a torsion cylinder, a torsion cylinder washer seat and a torsion adjustment ring covered on the torsion spring. One end of the torsion spring is supported by the lower clutch, and the other end is pressed against the torsion cylinder washer seat. The torsion adjustment ring provides the torsion spring with a tight and loose state change.

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

[0013] In a preferred embodiment, the hydraulic shock absorber includes a hydraulic outer seat, a lower clutch piston linked to the lower clutch, an upper liquid tank, a lower liquid tank and a hydraulic hole connecting the upper and lower liquid tanks in the space sandwiched by the lower clutch piston and the hydraulic outer seat, an oil filling hole on the upper liquid tank, an oil filling screw is arranged inside, and a leak-proof oil seal is arranged in the lower liquid tank to resist the hydraulic hole and a leak-proof washer is arranged to resist a return spring.

[0014] The expected effects achieved by the present invention include: 1. Two buffer cams are newly added to the asymmetric clutch device, which are used to release the kinetic energy of the latter part of the pulse, so that there is a buffer after the motor stops, the pulse is smoother, and the operator feels more comfortable. 2. The asymmetric clutch device is added with a hammer block device to reduce the reaction force, while retaining the high precision of the clutch. 3. When the torque of the fully automatic clutch reaches the set value, the clutch automatically jumps out, the air valve plate automatically shuts off the air, and the torque is more accurate (±3%), which meets the ISO5393 precision requirement specification. 4. The asymmetric clutch is set in the torque cylinder, so that the torque washer seat will be fixed and not rotated, and the torsion spring and the lower clutch will be clamped and fixed, so that the torsion spring can be twisted to generate new kinetic energy. 5. Under the condition of not reducing resistance, the elastic force accelerates the connecting shaft device to generate rotational kinetic energy. In the process, a torque of energy storage kinetic energy is added, which increases the total torque. At the same time, when the same torque is locked, the reaction force will become smaller. The actual drop test can reduce the reaction force by 25% to 50%. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0016] Figure 1 It is a schematic diagram of the mechanism decomposition of an impact power wrench in the prior art;

[0017] Figure 2 yes Figure 1 Principle and operation diagram of impact power wrench;

[0018] Figure 3 This is a schematic diagram of the mechanism decomposition of a prior art oil pressure pulse screwdriver;

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

[0020] Figure 5 It is a schematic diagram of the mechanism decomposition of a prior art semi-automatic clutch screwdriver;

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

[0022] Figure 7 yes Figure 5 Schematic diagram of the action of the semi-automatic clutch screwdriver;

[0023] Figure 8 This is a schematic diagram of the mechanism decomposition of a fully automatic clutch screwdriver in the prior art;

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

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

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

[0027] FIG11(B) is a perspective view of a device for increasing kinetic energy of a screwdriver according to a preferred embodiment of the present invention;

[0028] Fig. 11 (C) is a schematic diagram of the screwdriver action of a preferred embodiment of the present invention;

[0029] FIG. 12 (A) is a cam structure of a symmetrical clutch in the prior art;

[0030] FIG12 (B) is another preferred embodiment of the present invention showing the cam structure of the asymmetric clutch device;

[0031] Fig.13 It is a schematic diagram of an asymmetric clutch device according to another preferred embodiment of the present invention that has a new displacement energy added;

[0032] Fig.14 is a side view of the torsion spring of FIG12;

[0033] Fig.15 It is a table showing the kinetic energy change of a screwdriver of an asymmetric clutch when tightening screws using a screw dynamic simulator.

[0034] Fig.16 It is a table of kinetic energy changes of a screwdriver with a symmetrical clutch when tightening a screw using a screw dynamic simulation machine;

[0035] FIG. 17 (A) is a schematic diagram of the hydraulic shock absorbing device of a preferred embodiment of the present invention in reverse view (I);

[0036] FIG. 17(B) is a schematic diagram (II) of the hydraulic shock absorbing device in reverse view according to a preferred embodiment of the present invention;

[0037] FIG. 17(C) is a schematic diagram of the hydraulic shock absorbing device of a preferred embodiment of the present invention in reverse view (III);

[0038] FIG. 17 (D) is a schematic diagram of the hydraulic shock absorbing device of a preferred embodiment of the present invention in reverse view (IV);

[0039] FIG17(E) is a schematic diagram of the hydraulic shock absorbing device of a preferred embodiment of the present invention in reverse view (V);

[0040] FIG17(F) is an enlarged schematic diagram of point A in FIG17(B);

[0041] FIG17(G) is an enlarged schematic diagram of point A in FIG17(C);

[0042] FIG17(H) is an enlarged schematic diagram of point A in FIG17(D);

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

[0044] Fig.19 This is a diagram of the torque and time variation of a screwdriver of a preferred embodiment of the present invention (I);

[0045] Fig. 20 This is a diagram of the torque and time variation of a screwdriver of a preferred embodiment of the present invention (II);

[0046] Fig.21 1 is a diagram (3) showing the variation of the screwdriver torque and time according to a preferred embodiment of the present invention.

[0047] Description of Reference Numerals

[0048] 2. Impact power wrench; 21 motor group;

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

[0050] 24. Hammer block;

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

[0052] 32. Oil pressure pulse group; 33. Connecting shaft;

[0053] 34. Blade; 35. Oil;

[0054] H, high pressure area; L, low pressure area;

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

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

[0057] 431, steel ball; 432, cam;

[0058] 433, torsion washer seat; 44, torsion spring;

[0059] 45. Connecting shaft;

[0060] 5. Fully automatic clutch torque automatic stop starter;

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

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

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

[0064] The present invention:

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

[0066] 111. rotor; 112. middle and outer seats;

[0067] 113, needle; 114, valve plate;

[0068] 115. Slotted spring; 116. Main gear;

[0069] 12. Reaction force reduction hammer block device; 121. Fixing screw hammer;

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

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

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

[0073] 14. Asymmetric 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 adjustment ring;

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

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

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

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

[0082] 174, lower liquid tank; 175, hydraulic hole;

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

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

[0085] 179, return spring; opening A;

[0086] Opening B; Opening C. DETAILED DESCRIPTION

[0087] Please cooperate with Fig. 9 , Fig.10As shown, the present invention provides a three-kinetic-energy electric / pneumatic screwdriver 1, comprising: a high-speed motor device 11, a reaction force reducing hammer block 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 outer seat 112, and a needle 113 is provided at the axis of the rotor 111, and a valve plate 114 and a straight spring 115 are provided at one end of the needle 113 to control the opening and closing operation of the high-speed motor device 11, and a main gear 116 is provided at the other end of the rotor 111 relative to the valve plate 114. The reaction force reducing hammer block device 12 has the characteristics of low back force and high torque, and includes more than one fixing screw hammer 121, a reaction force hammer 122, a hammer fixing seat 123, a C ring 124 and a plurality of 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, the hammer fixing seat 123 is fixed by combining with the C ring 124 and the reaction force hammer 122, and the circumference of the reaction force hammer 122 forms a The fixing screw hammer 121 is placed in the containing groove and one end of the fixing screw hammer 121 penetrates the circumference of the hammer fixing seat 123 and is connected and fixed by the first steel ball 125. The lower part is meshed with a planetary gear plate 126. When the high-speed motor device 11 is started, the fixing screw hammer 121 is driven to move upward and hammer the reaction force hammer 122. When the speed decreases, the fixing screw hammer 121 moves downward and hammers the hammer fixing seat 123. The gear device 13 meshes with the planetary gear plate 126 upward to connect and transmit the power of the high-speed motor device 11. The asymmetric clutch device 14 is composed 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 respectively arranged in the two cam tracks 144, and the lower clutch 143 is used as a support to form an asymmetric clutch mechanism. The torsion spring device 15 includes a torsion cylinder 152 covered with a torsion spring 151, a torsion cylinder washer seat 153 and a torsion adjustment ring 154. One end of the torsion spring 151 is supported by the lower clutch 143, and the other end is pressed against the torsion cylinder washer seat 153. When the torsion adjustment ring 154 tightens the torsion spring 151, the torsion becomes larger, and when it is loosened, the torsion becomes smaller. One end of the connecting shaft device 16 is provided with a striker 161 and a striker steel ball 162 for connecting with the axis of the rotor 111, and the other end is provided with a tool head 163 with various functions and shapes.

[0088] The three kinetic energy increasing devices of the three kinetic energy electric / pneumatic screwdrivers of the present invention are: 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 is the first kinetic energy that provides the basic rotational power. In this example, the rotation 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, so that the kinetic energy is further increased to become the second kinetic energy, and the screwdriver obtains low reaction force and has high precision, and the repeatability can meet the ISO5393 screw locking specification for precision requirements. The principle is as follows:

[0089]

[0090] From the above kinetic energy formula, we know that mass m and speed V 2 Determines the kinetic energy, especially the velocity V 2 Therefore, a different concept is designed using the formula to increase the speed of the high-speed motor device, but the final speed is reduced to the connecting shaft device, so as to have the functions of maximum kinetic energy, most accurate torque, light weight and small reaction force. It is also proved from the kinetic energy formula that V is the square ratio of speed. The higher the speed, the greater the kinetic energy and the smaller the reaction force. According to the hammer block principle of the impact wrench in the prior art, it is applied to the present invention, and a reaction force reduction hammer device is added to the rotor of the high-speed motor device. Because the overall mass (m) is increased and the speed is increased, the kinetic energy is increased, so the efficiency of the high-speed motor is the highest.

[0091] Please Figure 11(A) , 11(B) 11(C) shows a device and an action diagram of increasing the kinetic energy of a screwdriver according to a preferred embodiment of the present invention; the reaction force reducing hammer block device 12 is attached to the power output direction of the rotor 111 of the high-speed motor device 11, 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. It is known from the kinetic energy formula that mass (m) affects kinetic energy. When designing, the inner ring of the hammer fixing seat 123 is made of a lighter material such as aluminum, so that the high-speed motor device 11 is more energy-saving when starting. After starting, the fixing screw hammer 121 will hammer the reaction force hammer 122, so the reaction force hammer 122 is made of a heavier material such as steel on the outer ring, so that the high-speed motor device 11 can obtain lighter, 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 FIG12 (A) shows the cam structure of a symmetrical clutch in the prior art, including a cam (c1) and a cam (c2) in relative positions of a track (t); FIG (B) shows the cam structure of an asymmetrical clutch device, including two inner and outer tracks (t1, t2) that do not interfere with each other and a cam (c3), a cam (c4) and two buffer cams (c5). Moreover, the distance between the cam and the center (r1≠r2) is also different from the distance between the cam and the center of the symmetrical clutch in the prior art (r1=r2). Please refer to FIG. Fig.13 As shown, the asymmetric clutch device 14 adds a new position kinetic energy, wherein the torque formula T = Fr (T = torque, F1 & F2 = force, r = radius), C = center point, the principle is as follows: in the asymmetric cam design, the radii r1 and r2 are different, according to the above formula, we know that T1 = F1r1, T2 = F2r2 and T3 = F3r3, the sum of which is the total torque of the tool (T1 + T2 + T3), compared with the symmetric cam, a new T3 kinetic energy is added. In addition, due to the two cam radii of the asymmetric clutch device 14 (r1 ≠ r2), it is obtained that the action force ≠ the reaction force, the action force is large, and the reaction force is small.

[0093] Please Fig.14 As shown, a side view of the torsion spring 151 is disclosed, and the following is an explanation of the action diagram: Fig.14 In the middle (A), when in standby mode (no torque value), the second steel ball 142 of the asymmetric clutch device 14 generates resistance (F) on the cam 144. At the same time, the cam 144 rises to generate an upward force (F1 and F2) on the torsion spring 151. The torsion spring 151 generates a compression force (S1 and S2). L1 = lower clutch height, L2 = cam rise height. Fig.14 (B) is when the force is applied during operation, with the bearing as the center point (C), the high-speed motor device is forced to rotate. However, due to the asymmetric cam structure (r1≠r2), the radius r1 is smaller than r2. According to the above formula, F1 is greater than F2. The second steel ball 142 pushes the lower clutch 143 obliquely like the wheel of a car. The radius r1 is smaller, and the speed of the second steel ball 142 rotating is relatively faster. On the contrary, the radius r2 is larger, and the second steel ball 142 rotates slower. The two rolling second steel balls 142 will produce an inner wheel difference due to the asymmetric track. The second steel ball 142 starts to rotate and drives the lower clutch 143 to rotate, generating an inner wheel difference and speed difference similar to the rotation of a car, and gradually twisting the torsion spring 151, generating a helical angle (α3) and starting to store energy. Fig.14 In the middle (C), when the cam 144 rises to the top dead center (i.e. the highest point), it runs to the maximum torque. When T1 and T2 are at their maximum, the kinetic energy is released at the same time, generating the maximum internal thrust (T3), which is the kinetic energy. Therefore, the total torque (total torque) of the screwdriver = T1 + T2 + T3, which is more powerful. Fig.14 In the middle (D), the cam 144 of the asymmetric clutch device 14 has been tripped. At this time, the resistance of the rolling second steel ball 142 and the cam 144 immediately becomes zero resistance, and the asymmetric track produces an inner wheel difference and slips, just like a pull-back toy car. When the hand is ready to let go of the pull-back toy car, the spring releases the kinetic energy stored before, causing the wheels to start rotating and moving forward. Therefore, there are two different types of forces driving the action, that is, a new elastic potential energy is emitted F3. Fig.14 The middle (E) indicates that the operation is stopped, the locking is completed, and the torsion spring 151 returns to its original state.

[0094] Please Fig.15 , Fig.16 As shown in the figure, it is a table of kinetic energy changes of screwdrivers with symmetrical clutches and screwdrivers with asymmetrical clutches when tightening screws using a screw dynamic simulator, to prove that the asymmetrical clutch device has an additional kinetic energy of ejection force. Fig.15 As shown in the figure, the speed of the thick black line suddenly dropped by 30rpm at 0.13 seconds, proving that there was slippage. Generally, a clutch with proportional linearity cannot have slippage. At 0.14 seconds, the speed of the thick black line and the torque value of the thin gray line both rose to the maximum value. This phenomenon means that after slippage, the stored elastic potential energy will be ejected at the same time, generating the speed and maximum torque value (the total force of T1+T2+T3), and then the motor stops, and the speed and torque return to zero. Fig.16 The figure shows the kinetic energy change table of the prior art symmetrical clutch, where the thick black line is the speed line. When the motor is loaded, the speed slowly drops to 450rpm and then stops rotating at 0.7 seconds. The thin gray line is the torque line. The clutch increases linearly and proportionally. The maximum torque value is around 6N.m. There is no slippage and no ejection force, which is different from the asymmetrical clutch.

[0095] Please Figure 17(A)-17(H)The structure and operation diagram of the hydraulic shock absorber shown in the figure; the hydraulic shock absorber 17 is arranged above the torsion cylinder 152 to reduce the rebound force of the torsion spring 151, including: a hydraulic outer seat 171, a lower clutch piston 172 linked to the lower clutch 143, the space between the lower clutch piston 172 and the hydraulic outer seat 171 has an upper liquid tank 173, a lower liquid tank 174 and a hydraulic hole 175 connecting the upper liquid tank 173 and the lower liquid tank 174, an oil filling hole 176 is provided on the upper liquid tank 173, and an oil filling screw 177 is provided therein, and a leak-proof oil seal 178B is provided in the lower liquid tank 174 to abut against the hydraulic hole 175 and a leak-proof washer 178A is provided to abut against the return spring 179. The leak-proof oil seal 178B is made of soft material such as rubber to block the hydraulic hole 175 to achieve a good sealing effect. The leak-proof washer 178A is made of hard material such as metal to support the soft leak-proof oil seal 178B and be resisted by the return spring 179 below. The set of leak-proof oil seal 178B and leak-proof washer 178A are affected 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. As shown in FIG17(A), the screwdriver is in the standby state; as shown in FIG17(B) and FIG17(F), after the screwdriver is started, the lower clutch rises, causing the cam and the lower clutch piston 172 to rise, and the liquid in the upper liquid tank 173 will push the leak-proof oil seal 178B and the leak-proof washer 178A to shift downward from the hydraulic hole 175 to form an opening A, so that the liquid flows from the opening A to the lower liquid tank 174, and the return spring 179 is lowered; as shown in FIG17(C) and FIG17(G), when the cam rises to the highest point (top dead center), the opening B of the leak-proof oil seal 178B forms the maximum liquid passage. Excessive, this state is the maximum torque of the screwdriver locking the screw; as shown in Figure 17 (D) and Figure 17 (H), when the cam jumps out, the oil filling screw 177 will block the leak-proof oil seal 178B, so that the lower clutch piston 172 is immobile. At this time, the gap of opening C is smaller than that of opening B, and the liquid flows back from the lower liquid tank 174 to the upper liquid tank 173. The return spring 179 is reset, and the lower clutch piston 172 also slowly descends to return to its original position. At this time, the state is that the screwdriver is about to complete the screw locking; as shown in Figure 17 (E), the screwdriver has completed the screw locking and returned to the standby state, and the screw can be locked again.

[0096] As mentioned above, since the lower clutch piston 172 will reduce the downward force of the torsion spring 151 and the lower clutch 143, the torsion spring 151 will not cause the noise of continuous collision between the second steel ball 142 and the lower clutch 143, thereby reducing the noise value. In particular, when the screwdriver locks each screw, the lower clutch only jumps once (One Pulse), without continuous jumping, and automatically stops when the torque value is reached (Auto Shut-Off), with high torque accuracy, which is different from the continuous pulse (continuous jumping phenomenon) of general hydraulic pulse tools.

[0097] In addition, for the screwdriver structure of the present invention, the torsion spring pressure is divided into large and small torques, and the speed is fast and slow, so two mechanical structures are designed. The faster speed and large torque require the use of internal adjustment tools; the slower speed and small torque require the use of external adjustment tools. Fig.18 As shown, the screwdriver of the present invention uses an external torque adjustment structure. The torque can be easily adjusted by rotating the torque adjustment ring. Since a compression torsion spring is used, the compression force can be linearly proportional, and the target torque value can be obtained very accurately, which can meet the ISO5393 precision requirement specification.

[0098] Please Figure 19 to Figure 21 As shown, the torque and time variation diagrams of the screwdriver of the present invention are respectively shown; the biggest difference between the hydraulic shock-absorbing device of the present invention and the prior art is that the same tool only trips once when a large torque is used, such as Fig.19 When the torque is adjusted to a small value, pulses (continuous jumps) will occur. In the above cases, the reaction force is small. Fig. 20 From the graph, it can be seen that when the torque is the largest for the first time, as time goes by, the torque will become smaller and smaller until the motor automatically stops and completes the locking. Furthermore, for general rotary hydraulic pulse or impact tools on the market, the torque will become larger and larger as time goes by when the torque is small for the first time, such as Fig.21 , due to the change of oil temperature, viscosity or the difference of impact times, the time of each locking stop is inconsistent. Therefore, it can be seen that the present invention subverts the disadvantage of difficult time control in traditional designs (traditional designs such as oil pressure pulse, mechanical impact, semi-automatic clutch) and the innovatively designed hydraulic shock absorber (continuous jump) will not make the torque inaccurate even if the time is different, so it is an innovative structure for obtaining accurate torque locking screws.

[0099] From the above description, it can be seen that the present invention adopts a high-speed motor device, a reaction force reduction hammer device and an asymmetric clutch device to form a design with three kinetic energy addition, which is superior to the prior art in terms of speed and torque output. At the same time, the use of a hydraulic shock absorber device can further reduce the noise generated by the above-mentioned significant increase in speed and torque, effectively reducing the number of clutch tripping times when locking the screwdriver to once, and simultaneously improving the torque accuracy when locking the screw.

[0100] However, what is described above is only a preferred feasible embodiment of the present invention. Therefore, all equivalent structural changes made by applying the specification and claims of the present invention should be included in the patent scope of the present invention.

Claims

1. A three-kinetic-energy electric / pneumatic screwdriver, characterized in that: include: A high-speed motor device provides a first kinetic energy, and has a rotor and a middle and outer seat. A needle is passed through the axis of the rotor, and a valve plate is provided at one end of the needle. A straight spring is provided above the valve plate to resist, and a main gear is combined with the other end of the rotor; A reaction force reduction hammer block device provides a second kinetic energy, is attached to the power output direction of the rotor of the high-speed motor device and is penetrated by the rotor, and 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 combining the C ring with the reaction force hammer. A concave notch is formed on the circumference of the reaction force hammer. A receiving groove is formed on one side of the notch. 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 ball, passes through the rotor end edge of the reaction force reduction hammer block device and then meshes with a planetary gear plate for transmission; a gear device for connecting the combined output of the first kinetic energy and the second kinetic energy, comprising one or more gears meshing with the planetary gear plate to connect the power output of the high-speed motor device; An asymmetric clutch device provides a third kinetic energy, superimposing the first kinetic energy and the second kinetic energy, comprising an upper clutch, a second steel ball, and a lower clutch, wherein the upper clutch surface has two inner and outer cam tracks with different center distances, the inner and outer cam tracks are respectively provided with the second steel ball, and the lower clutch is used as a support to form a clamping position; A torsion spring device, comprising a torsion spring, one end of which is supported by the lower clutch, and the other end of which is pressed against a torsion cylinder washer seat, and is covered with a torsion cylinder and a torsion adjustment ring to control the tightness and looseness of the torsion spring; and A connecting shaft device is provided with a striker at one end thereof to abut against the needle and to move in conjunction with the lower clutch. The striker is combined with two striker steel balls to limit displacement. A tool head is provided at the other end thereof to be embedded therein.

2. The three kinetic energy electric / pneumatic screwdrivers as claimed in claim 1, characterized in that: It also includes a hydraulic shock absorber, including a hydraulic outer seat, a lower clutch piston linked to the lower clutch, an upper liquid tank, a lower liquid tank and a hydraulic hole connecting the upper liquid tank and the lower liquid tank in the space sandwiched by the lower clutch piston and the hydraulic outer seat, an oil filling hole on the upper liquid tank, an oil filling screw is arranged inside, and a leak-proof oil seal is arranged in the lower liquid tank to resist the hydraulic hole and a leak-proof washer is arranged to resist a return spring.

3. The three kinetic energy electric / pneumatic screwdrivers as claimed in claim 1, characterized in that: The reaction force reducing hammer block device comprises more than one fixing screw hammers, and the fixing screw hammers are equally arranged on the peripheral surface of the hammer fixing seat.

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