A penetrated tool system

The present invention is related to the penetrating tool system. In such a tool system, the penetrating tool is designed to penetrate a workpiece, for example, by drilling, perforating, drilling, cutting, sawing, shearing, polishing, etc. or similar tools.

Examples of this type of through tool system are different types of cutting machines such as sawing. Drilling, sewing, planing, cutting or similar machines. These systems can be used with hand tools or portable tools or fixed mechanical tools. In these known systems, the penetrating tool or the workpiece has a linear or rotational displacement relative to the tool, and it can be in a single direction or reciprocating back and forth. So for example: a hand-held sawing machine has a reciprocating linear displacement, and a needle-shaped stitching machine is the same.

However, in the known penetration tool system, in most cases, the tool will consume energy (and inevitably generate heat) when the tool penetrates into the workpiece, and in many cases there are waste (maybe slag) materials like sawdust or the like Something produced.

So for example, many hand-held power drills used to drill hard objects will use a hammer mechanism and consume high energy, and expensive components must be replaced frequently.

The purpose of the present invention is to provide a new and improved penetrating tool system that can reduce and overcome the above-mentioned inconveniences and shortcomings.

According to the present invention, a penetrating tool system is provided for penetrating the workpiece, wherein there is a relative displacement between the workpiece and the system. The system is composed of the following elements: a penetrating element; In terms of displacement components, this basic displacement has frequency and vibration cap, and its effect relative to the workpiece does not change with time.

The second way is to generate the opposite force on the system and the auxiliary moving back, so at least the inertial load and the effect of the auxiliary moving back on the system can be balanced.

In order to ensure that the auxiliary displacement transfer to the penetrating element does not change with time, the so-called "rigid fixed kinematics" is used when the auxiliary displacement is transferred to the penetrating element. Different, each of these systems transmitted to the penetrating element's back and forth movement (for example, using electromagnetic, hydraulic or pneumatic means or by means of traditional elements such as elastic elements, springs or similar vibrating on deformation) will vibrate to The effect on the workpiece will change over time. At the same time, the new system has some improvements in general technical operations and special penetrating surface quality. Therefore, through this invention, to achieve a new type of technical operation, such as cutting a whole piece of material without generating scraps or waste, and drilling on a solid object no longer requires hammer drilling. It's all possible.

According to the tool system of the present invention, the transfer function of assisting the transfer of the return movement to the penetrating element becomes quite easy, and the power consumption is also significantly reduced.

However, such tools, especially hand-held tools, will generate inertial force in the tool. The direction of this force is opposite to the force generated by the auxiliary displacement. Therefore, these forces will at least partially balance. Unwanted vibration is reduced to a minimum.

If it is a hand-held tool, the above-mentioned balance force is almost continuously provided. If it is a tool with a fixed base, the balance force is only required to be provided when the transfer aid is greater than 0.5 mm in the reset movement.

As mentioned above, the penetrating tool system must be established when the penetrating element and the workpiece have a basic relative displacement. For example, if the penetrating element is a knife, a pin, or a drill, the relative displacement can be a single-direction linear displacement and pass through the workpiece, and if it is a drilling, the relative displacement is a single-direction rotational displacement. Such a single-direction linear basic displacement can of course be transmitted to the penetrating element by the user applying pressure on the workpiece.

In addition, the basic displacement can be reciprocated, such as the displacement of a sewing machine or a saw. The frequency of the basic displacement is small, but the amplitude of this transfer assists the return movement to be large. The transfer of the auxiliary back-to-return movement can be simple, linear reciprocating motion, such as a penetrating element transferred to the shaft, or reciprocating rotational motion. If it is a rotationally symmetric element, such as a drill bit, the auxiliary displacement can be reciprocating linear movement or reciprocating rotational movement or a combination of the two.

The reasonable frequency range for transmitting auxiliary displacement is about 50-500HZ, and the better frequency is 100HZ. The reasonable range of the amplitude is about 0.1-10 mm. The preferred amplitude is 1-2 mm for the cutting element and 0.5 mm for the drilling tool. The frequency and amplitude are usually determined by the material of the workpiece. For example, the lower the elasticity, the higher the frequency selected. And the more brittle the material, the larger the selected amplitude.

In order to better understand the present invention and the actual implementation status, refer to the following

The graphics will help you understand: Figure 1 is an explanation of the displacement symbols used in the following graphics.

Figures 2 to 13 illustrate many different types of displacements transmitted to the penetrating element.

Figure 14 is a pictorial illustration of a hand-held penetration tool with linear displacement in accordance with the present invention.

Figure 15 is a further illustration of a hand-held penetration tool with linear displacement according to the present invention.

Fig. 16 is an illustration of the cutting tool mechanism shown in Fig. 14 in accordance with the present invention.

Figure 17 is a pictorial illustration of a rotary handheld drill bit according to the present invention.

Figure 18 is an illustration of a hand-held tool that can be used as a linear displacement penetrating tool or a rotary drill bit according to the present invention.

Figure 19 is a pictorial illustration of a first type of drilling/milling machine fixed in accordance with the present invention.

Fig. 19a is a side view of Fig. 19.

Figure 20 is a pictorial illustration of a second type of drilling/milling machine fixed in accordance with the present invention.

Fig. 20a is a side view of Fig. 20.

Fig. 21 is an illustration of a further version of the rotary drilling machine according to the present invention.

Fig. 22 is a side view of the fixed skeleton of the sawing mechanism according to the present invention.

FIG. 23 is a top view of the fixed structure of the sawing mechanism in FIG. 22.

Figure 24 is a detailed end view of the mechanism shown in Figure 22.

Circle 25 is a front detailed view of the mechanism shown in FIG. 22.

Fig. 26 is a detailed cross-sectional view of the mechanism shown in Fig. 22.

Fig. 27 is a front view of a fixed penetrating mechanism with a cut-off type blade with linear displacement according to the present invention.

Fig. 28 is a side view of the mechanism shown in Fig. 27.

Figure 29 is a pictorial illustration of a shear type mechanism according to the present invention.

Fig. 30 is a detailed cross-sectional view of Fig. 29 taken along the line XXX-XXX.

Detailed description of the invention

As shown in Figure 1, the basic displacement is represented by a single-line arrow, and the auxiliary displacement toward the reset is represented by a double-line arrow. Therefore, Fig. 1a illustrates the linear basic displacement, Fig. 1b illustrates the basic displacement of the rotation, Fig. 1c illustrates the linear assisted movement toward the reset, and Fig. 1d illustrates the angular assisted movement toward the reset.

As shown in Figure 2, a cutting tool (indicated by T). There is a linear basic displacement and a linear auxiliary to the reset transfer to itself.

As shown in Figure 3, this tool adds a combination of linear and rotational basic displacements on top of the linear assisted reset movement.

As shown in Figure 4, this tool has a linear basic displacement and an angle is added to assist in the reset movement.

As shown in Figure 5, this tool has a linear basic displacement and an angle is added to assist in the reset movement.

As shown in Figure 6, this tool has a combination of linear and rotational basic displacements and then adds linear and angular assistance to the reset movement.

As shown in Figure 7, this tool has a basic linear reciprocating motion and then adds a linear auxiliary to the reset movement.

Therefore, Figures 2 to 7 can be representative of various tool systems, in which the penetrating element is composed of pins, needles, blades, drills, saws or similar tools.

The tool T as shown in FIG. 8 may have irregular cutting boundaries. The tool T has a basic linear displacement relative to the X and Y axes, and/or a basic rotational displacement around the axis 0. On top of these basic displacements, an auxiliary reciprocating displacement relative to the X and Y axes and/or an auxiliary reciprocating angular displacement relative to the axis 0 or another axis 0'is added.

The penetrating element is composed of a tool symmetrical to the longitudinal axis, such as a drill or an auger bit, and the tool system can have any type of displacement in FIGS. 2-7. However, if this tool system is equipped with a drill, for example, as shown in Figures 9a and 9b, it is not symmetrical with the longitudinal axis. As shown in Figure 9a, it has a closed type of cutting boundary, as shown in Figure 9b. An open type cutting boundary, and only the displacement of Figure 2 can be used. In a similar situation, this tool system is designed to penetrate the workpiece with non-circular or symmetrical holes (such as square holes). Drilling machines with square cutting boundaries can be used in this example, and only the displacement shown in Figure 2 Can pass.

As shown in Figure 10, a cutting and penetrating element with a curved boundary is fixed on axis 0 and has a linear basic displacement in the X direction. On the basic displacement, an angle is added around the same axis to assist the reset movement and/or at the same X Add a linear assist in the direction to move towards the reset.

Figure 11 illustrates the use of a planar cutting element to transfer the basic displacement of linear translation and the linear auxiliary to the return movement, one is in the direction of the basic movement, and the other is in the direction of 90 degrees.

Figure 12 illustrates the use of all elements T. This cutting element has a pair of cutting surfaces that are at an angle to each other, and has a linear basic displacement in the X direction and a linear auxiliary return movement in the same direction. Such a cutting element can be used as a workpiece Shape cutting.

Figure 13 illustrates a truncated cutting element with linear basic displacement in the X and Y directions. This element can also transmit linear and/or angular assisted return movement, where the angle is 90 degrees.

Hereinafter, various examples of penetrating tool systems will be described with reference to FIGS. 14 to 30, as well as the method of transferring the auxiliary movement to the penetrating element and the appropriate basic displacement.

Figure 14 is a pictorial illustration of a hand-held penetration tool according to the present invention. This tool is composed of a frame 11 with a handle 12 and a starter motor 13 fixed on the frame. The motor 13 has a starter shaft 14 to start the crankshaft 15, where the crankshaft 15 is a rotating shaft located in the frame 11 neck. The crankshaft 15 is composed of an outer crank 15a and an inner crank 15b. The inner crank 15b is connected to the linear starting shaft 17 via the motion conversion mechanism 16, wherein the linear starting shaft 17 extends outside the frame 11 and is connected to the penetrating tool element 18. Such a motion conversion mechanism (hereinafter referred to as "motion conversion mechanism") is designed to convert the rotary motion of the first axis into linear reciprocating motion on the second axis perpendicular to the first axis. Such a mechanism can be constituted by the so-called "Scotch Yoke" mechanism.

The outer crank 15a is transferred to a counterweight 19 through the motion conversion mechanism 16, and the counterweight passes through the starting shaft 17.

When in use, the motor 13 rotates and starts, causing the crankshaft 15 to rotate, and then the rotational displacement of the intermediate crank 15b is transmitted to the starting shaft 17 in the form of a linear movement to the reset. The motion conversion mechanism 16 determines that only the linear displacement in the axial direction of the activation shaft 17 is transmitted.

At the same time, the rotational displacement of the outer crank 15a causes the counterweight 19 to move back and forth linearly, wherein the displacement is 180 degrees relative to the displacement of the crankshaft 15 and the penetrating tool element 18. Here, as above, the crank 15a is connected to the counterweight 19 via a motion conversion mechanism to ensure that the rotational displacement of the crank 15 is transmitted to the counterweight 19 only in the form of reciprocating linear displacement, and the direction opposite to the tool element 18.

During operation, since the user applies force to the workpiece, the penetrating element 18 will transmit a substantially linear displacement, and the rotation of the crank 15 causes the linear auxiliary displacement to be transmitted to the penetrating element 18. Therefore, the penetrating element 18 can penetrate the workpiece. The transmission from the motor 13 through the rotating machine shaft to the return movement to the penetrating element 18 includes rigid motion transmission. Therefore, the frequency and amplitude of the auxiliary return movement of the penetrating element 18 relative to the penetration of the workpiece does not change with time.

The back-to-return movement of the counterweight 19 is 180 degrees out of phase with respect to the auxiliary back-to-return movement of the penetrating element 18, so it can be ensured that the inertial force generated by the tool will be balanced with the inertial load generated by the auxiliary back-to-return movement of the penetrating element. In this way, the vibration caused by the user can be reduced to a minimum.

The magnitude of the balance force generated by the counterweight 19 moving toward the reset is a function of the mass of the counterweight 19 and the amplitude of the counterweight 19 moving toward the reset. These parameters can be selected appropriately to ensure that the balance can be effectively achieved.

The penetrating element 18 itself can be composed of a knife or a blade or any cutting and flattening form, or it can be composed of a needle-shaped penetrating element used to make an aperture. In addition, the penetrating element can also be composed of one or a pin-like element for the preparation of a flat plate or other materials such as a circuit board to form a set of apertures.

A further penetrating tool is shown in Figure 15. The penetrating tool system is composed of an outer frame 21, in which the inner frame 22 is fixed by the guide rod 23 inside the frame 21, so that the inner frame 22 will not affect the outer frame The longitudinal axis direction is limited to the return movement. The rotating starter motor 24 has a rotating shaft 25 extending to the outer frame 21 and starts a helical wheel 26, and then is connected to the rotating worm wheel 27, which is fixed to the frame with respect to the outer frame 21. The crankshaft 28 is located within the inner frame 22, and the crankshaft 28 is connected to the starting shaft 25 with a coupling 29. The first crank 28 a of the crankshaft 28 is connected to the angled vibrating rod 31 by a connector 30, and the vibrating rod is pivotally supported at the middle corner and fixed to the inner frame 22 by a bracket 32. The end of the vibrating rod away from the connector 30 is connected to the main shaft 34 by the connector 33, and a through tool is fixed under the shaft. The second crank 28b of the crankshaft 28 is connected to an angular vibrating rod 37 by a connecting rod 35 and a connector 36, and the vibrating rod is pivotally supported at the middle corner and fixed to the inner frame 22 by a bracket 38. The end of the vibrating rod away from the connector 36 is connected to the counterweight 40 via the connector 39, and the main shaft 34 surrounds it.

The crank rod 41 is pivotally connected to the upper end of the eccentric portion of the worm wheel 27 and connected to the lowest end of the inner frame 22 by a connector 42.

In operation, the motor 24 rotates the starter shaft 28 and vibrates the vibrating rods 31 and 37 in mutually opposite directions. These pivot-guided vibrations are transmitted to the main shaft 34 in one direction and to the counterweight 40 on the other hand. Because the main shaft 34 and the penetrating element are connected together, the linear auxiliary displacement can be transmitted, and the counterweight 40 will be The linear auxiliary displacement is transmitted in the opposite direction of the penetrating element.

At the same time, the motor 24 is transferred to the worm gear 27 by the rotational movement of the spiral wheel 26, and then a linear basic vibration displacement is transmitted to the inner frame 22 by the crank rod 41 via the connector 42, wherein the displacement has a vibration frequency less than that transmitted to the penetrating element and The frequency of the reciprocating movement of the counterweight 40. The vibration movement of the inner frame 22 is transmitted to the main shaft 34 and the penetrating element.

What is transmitted to the main shaft 34 and the penetrating element is a linear reciprocating basic displacement, and a linear auxiliary reciprocating movement is added at the same time, wherein this displacement has a frequency greater than the reciprocating basic displacement. At the same time, a similar displacement in the opposite direction is also transmitted to the counterweight 40. Since it is transferred in the opposite direction to the reset and moved to the counterweight 40, and then transferred to the penetrating element with a relatively high frequency, the vibration transmitted to the user will be reduced. Obviously, this penetrating element can be formed by a saw blade, and this tool will be an efficient hand-held saw.

Referring to the graph in FIG. 16, the hand-held tool shown is a cutting tool that can transmit arc-shaped reciprocating basic displacement and linear auxiliary reciprocating movement. It can be seen from the figure that this tool is composed of a main frame 51 and a frame 52 fixed on it, wherein the frame 52 can move back and forth along with the arc-shaped guide rod 53 located on the main frame 51. The frame 52 has a first starting motor, which constitutes a mechanism identical to that of FIG.

In addition, this tool has a second starter motor on the frame 51, this motor has a starter shaft connected to the worm gear 58 via a protruding gear and a connecting shaft 57, and then connected to the worm gear 59. The worm gear 59 is connected to the frame 52 by a connecting rod 60 on its circumference.

After the starter motor 56 is started, the power is transmitted to the frame 52 via the gear 57, the worm gear 58, the worm gear 59 and the connecting rod 60, and the frame 52 reciprocates in an arc path formed by the arc guide rod 53. Therefore, what is transmitted to the cutting element 55 is a substantially reciprocating arc-shaped displacement. At the same time, the starting of the motor 54 is transmitted to the cutting element by a linear assisted return movement with a higher frequency and lower amplitude than the basic reciprocating movement.

Refer to Figure 17, which shows a hand-held rotary drill bit according to the present invention. As shown in the figure, the rotary drill bit is composed of a frame 65 fixed with a starter motor 66. The motor has a starter shaft 67, which can rotate and start the protruding gear 68 and start a pair of protruding gears 69, 70 through the protruding gear 68. The protruding gear 69 is connected to the protruding gear 72 via the connecting shaft 71 and thus drives the protruding gear 73 to be connected to the shaft 74. At the free end of the shaft 74, there is a chuck 75 that can clamp the drill element 76. In this way, the starter motor 66 can transfer the basic return movement to the shaft 74 and the drill element 76.

The protruding gear 70 is connected to a pair of helical gears 78, 79 via a connecting shaft 77, and the helical gear 79 is connected to a rotating machine shaft 80 fixed in the frame 65 via a shaft head. The central crank 80a of the rotating machine shaft 80 is connected to a linear displacement shaft 81 via a suitable motion conversion mechanism. The crankshaft 81 is connected to the starting shaft 74 via a connection mechanism 82, which allows the rotational movement of the shaft 74 to be linearly displaced relative to the shaft 81, but does not affect the linear displacement from the shaft 81 to the linear movement between the shaft 74It Transmission.

The outer cranks 80b of the pair of crankshafts 80 are connected to the counterweight 83 via a motion conversion mechanism.

Therefore, the start of the motor 66 is transmitted to the crankshaft 80 via the helical gears 78 and 79, and the rotation of the latter is converted into a linear assisted return movement of the shaft 74, and of course it continues to be transmitted to the drill element 76. At the same time, the counterweight 83 relative to the auxiliary reset movement of the drill element 76 transfers toward the reset movement in an inverse phase of 180°. Therefore, a counterbalance force is generated in the tool to balance the vibration generated by the auxiliary displacement of the drill element 76.

The hand-held drill shown in Figure 17 has a traditional basic rotational displacement, and then adds a linear auxiliary reciprocating movement. Furthermore, due to the counterweight, the user of the drill bit can effectively protect and avoid the vibration caused by the auxiliary reciprocating movement of the drill bit element.

Referring to Fig. 18, the figure illustrates a hand-held tool that can be converted into a linearly movable through tool or a rotary drill bit. This tool is composed of an outer frame 91 and a starting motor 92. The motor has a starting shaft 93 connected to a starting shaft 95 via a coupling 94. This activated shaft is connected to the first protruding wheel 96 and then to the second protruding wheel 97. The second protruding wheel 97 is connected to the third protruding wheel 99 via the crankshaft 98, and then to the fourth protruding wheel 101. The protruding wheel 101 is connected to a first helical gear 103 via a connecting shaft 102, and then to a second helical gear 104 placed vertically, and then rigidly connected to an extended hollow shaft 105.

The pair of cranks 98a of the crankshaft 98 are connected to the counterweight 106, and the crank 98b located in the middle is connected to one end of the longitudinally extending shaft 107 via a motion conversion mechanism. The other end of the shaft 107 is connected to a tool fixing element 108. As shown in the figure, the connecting cover 109 is fixed to one end of the shaft 105. The chuck 110 is connected to the connecting cover 109 and can hold a penetrating element (such as a drill). Therefore the drill element can be connected to the chuck 110, in this case the tool should be a rotary drill. In addition, the chuck 110 and the connecting cover 109 can be removed, and the penetrating tool element (such as a blade) can be directly connected to the tool fixing element 108. In this example, according to the present invention, the tool is a vibration penetrating tool.

During operation, if it is desired to use a tool element such as a blade as a penetrating tool, according to the present invention, the connecting cover 109 is removed, and then the tool element is directly connected to the tool fixing element 108. The motor 92 rotates to drive the rotation of the motor shaft 98, and then the crank 98b transmits a linear aid to the return movement to the connecting shaft 107, and then connects to the tool fixing element 108 connected to the tool. At the same time, the reciprocating linear displacement of the counterweight 106 is derived, and this displacement is 180° out of phase with the shaft 107 and the tool fixing element 108.

Since the counterweight 106 provides an anti-return movement of 180° to the tool fixing element, the user of the tool can avoid unnecessary vibration when using the tool.

If you want to use this tool as a rotary drill, the cover 109 is fixed to the end of the shaft 105, and the drilling element is fixed to the chuck 110. The rotational tendency generated by the motor 92 is transmitted to the extended shaft 105 via the starting shaft 93, the driven shaft 95, the gears 96, 97, the crankshaft 98, the gear transmission 99, 101, the helical gear 103, 104, and the connecting cover 109 to the clamp Head 110 and drill element.

In this example, since the connecting cover 109 makes the drill element not connected with the fixed element 108, it does not directly transfer the linear return movement to the drill element, so the tool can be effectively operated as a traditional rotary drill.

However, it is worth noting that when the linear return movement is not directly transmitted to the drill element, the counterweight 106 continues to undergo reciprocating movement. This reciprocating movement will generate auxiliary vibration in the tool, which is transmitted to the drill element and can significantly improve the drilling process.

When the auxiliary vibration is transmitted to the drill element instead of rigid motion transmission, it can be found that such auxiliary vibration is still effective in improving the drilling operation. The amplitude of the auxiliary vibration cannot exceed 0.5 mm and the diameter of the drill element cannot exceed 12 mm.

The tool described above transmits a substantially linear displacement to the workpiece as a result of the force or pressure exerted by the user.

Refer to the figures in Figures 19 and 19a. These two figures illustrate a fixed drilling/milling machine. Figure 19a is a partial side view of the mechanism in Figure 19. This machine consists of a rigid frame with a tool receiving plate 122. The starting motor 123 is fixed on the frame and has a starting shaft 124 connected by a starting pulley 125 and a starting belt with a starting pulley 127. The rack-shaped rotating shaft 128 is connected to the activated pulley 127, so that it can follow the rotation, but is axially linearly displaced relative to the pulley 127. The rack-shaped 128 is connected to a sleeve 129 that can move axially in the frame, so the shaft 128 can move axially in the sleeve and rotate independently of the sleeve 129. The rotation of the rack-shaped shaft 128 is transmitted to the chuck 130 which holds a drill element 131. Such a connection makes the chuck 130 and the drill element 131, the sleeve 129 and the rack-shaped shaft 128 move axially together, but the rotation and the sleeve 129 are independent of each other.

Working together with the rotating gear 132 is an axial rack 133 fixed on the sleeve 129.

Another starter motor 134 is fixed on the frame 121 to start a rotating crank 135 (see Figure 19a) in which the crank 135 is connected to the surrounding part of the input helical gear 137 by the connecting shaft 136, plus the output helical gear 139 and the side bevel The gears 140 and 141 constitute a set of differential helical gear mechanism 138. The output helical gear 139 is fixed to the shaft 142, and the shaft 142 is fixed to the pinion 133.

The rotary displacement handle 143 of the drill bit is connected to the shaft 144 and then to the helical gears 140,141.

During operation, the rotational displacement of the handle 143 causes the rotational displacement of the gear 133, so the sleeve 129 generates a linear displacement, and then the drill element 131 also generates a linear basic displacement. When the drill element 131 is lowered to the workpiece contact, the rotational movement provided by the motor 123 is transmitted to the rack-shaped shaft 128, and then a basic rotational displacement is transmitted to the drill element 131. In addition, the rotation activation provided by the motor 134, through the adjustment of the differential mechanism, transmits a rotation to the reset to the gear 133 and then transmits the auxiliary reciprocating linear displacement with a frequency higher than the basic rotational displacement of the drill element 131 To the rack 132, sleeve 129 and drill element 131.

The drill element 131 can be easily replaced with a grinding element. The tools described above provide an effective method to drill or grind workpieces, and make drilling or grind relatively easy by transferring the assisted return movement . Judging from the fact that these tools are fixed tools, it is not necessary to provide a balance force due to the vibration caused by the auxiliary displacement of the tool element. However, if the amplitude of the assisted return movement exceeds a certain maximum value, such a balance force must be provided to protect the tool from wear and this function can also be easily achieved.

Refer to Figures 20 and 20a, where the illustration is a fixed drilling/milling machine in which the drill/grinding workpiece transmits a basic rotational displacement and adds rotation or angular assistance to the return movement.

This machine is composed of a rigid frame 135 with a workpiece receiving substrate 135a. The frame 136 is vertically fixed on the frame 135, and by turning on the handle 136b, the frame 136 is axially displaced relative to the rack and pinion device. The starter motor 137 is fixed on the frame 136, and a starter shaft is connected to the helical gear 139, which constitutes the first input gear of a differential gear set 140. The differential gear set 140 is composed of first and second helical gears 141 and 142, and the latter (142) can also be regarded as the second input gear of the differential gear set 140. The differential gear 140 finally provides an output helical gear 143 connected to the chuck 145 via a shaft 144, wherein the chuck fixes a drill element 146.

The second starter motor 147 is fixed on the frame 136, and has a power output through a power conversion mechanism to start a crankshaft 148 connected to one end of a reciprocating shaft 149, and the other end of the shaft 149 is connected to the eccentric position 150 of the helical gear 142.

During operation, the frame 136 and the drill element or grinding element 146 are lowered in position by the rack or pinion device 136, wherein the gear device is attached to a workpiece receiving substrate 135a, so that it can transmit substantially linear displacement to the element 146. After the motor 137 is started, it is transmitted to the output helical gear 143 via the input helical gear 139 and the side helical gears 141 and 142, and the basic rotational displacement is transmitted from the output helical gear to the chuck 145 and the drill/grinding element 146.

In addition, after the motor 147 is started, the crankshaft 148 generates a rotational displacement, and the rotational displacement is converted by the motion conversion mechanism into a linear return movement of the shaft 149. Since the lower end of the shaft 149 is connected to the eccentric position 150 of the second input helical gear 142, it will transmit auxiliary rotation or angular return to the helical gear 142, where this displacement will be transmitted to the chuck 145 and drill/grinding through the output helical gear 143 Component 146. It can be determined that the frequency of the auxiliary reciprocating angular displacement transmitted to the drill/grinding element 146 will be much greater than the frequency of the basic rotational displacement of the drill/grinding element 146 activated by the motor 147. Therefore, the auxiliary rotary reciprocating action of the drill bit is added to the basic rotary action, which will make drilling or grinding more convenient in operation.

Refer to the graph in Figure 21, which is a representation of a tool such as a drill bit. The tool transmits a basic rotational displacement and a linear basic displacement, the latter being caused by the user's pressure on the tool. Added to it is the combination of linear assisted shift to reset and rotary assisted shift to reset. As shown in the figure, this device is composed of an outer frame 171 and an inner frame 172, wherein the inner frame is fixed on the outer frame and can rotate. The first starter motor 173 is fixed on the outer frame 171. The motor has a starter shaft 174 extending to the outer frame 171 and is rigidly fixed on the inner frame 172. The penetrating element 175 is connected to an activation shaft extending through the frames 171 and 172, and is connected to the inner frame in an articulated manner so as to rotate together with the inner frame 172 and have relative axial movement relative to the frame 172.

The second starter motor 177 is fixed on the outer wall of the inner frame 172 and starts a crankshaft 178 connected to the central crank 178a of the shaft 176. Therefore, when the motor is started, the crankshaft 178 is started to rotate, and the rotation of the crank 178a will cause the penetrating element 175 The linear axis assists the reset movement.

The third motor is fixed on the inner frame 172 and activates the crankshaft 181 with a crank 181a, wherein the free end of the crank 181a protrudes to a U-shaped connecting element 183, which is fixedly connected to the starting shaft 176.

When in use, the rotation generated by the motor 173 causes the rotation of the inner frame 172 and therefore the rotation of the penetrating element 175. In other words, the motor 173 transmits a basic rotational displacement to the penetrating element 175a. On the other hand, as mentioned above, the starter motor 177 transmits a linear assist to the return movement to the penetrating element 175. Finally, the third motor 180 rotates the starter shaft 181, and transmits an auxiliary rotation displacement to the shaft 176 via the U-shaped connecting element 183. In this manner, there are three types of displacements transmitted to the penetrating element 175, namely, the basic rotational displacement, and the combination of linear assisted return movement and rotation assisted return movement. In addition, the force exerted by the user on the tool along the direction of the workpiece, coupled with the weight of the tool, causes the linear basic displacement of the penetrating element toward the workpiece. In addition, the tool can provide a counterweight so that the reverse direction can be used to transfer the return movement to the auxiliary displacement of the penetrating element. In this way, the vibration felt by the user of the tool can be greatly reduced.

Referring to Figures 22 to 26, these figures illustrate the sawing mechanism of the fixed skeleton made according to the present invention. Especially in Figures 22, 23 and 24, it can be seen that the sawing mechanism is supported by a rigid support "support platform 92". A skeleton 191 is formed, and a timber route device 193 is fixed on the supporting platform. There is a rotating friction feeding cylinder 194a in front of the routing device 193, and this cylinder is connected to the rotating displacement handle 195. The rotational displacement of the handle 195 can rotate the friction cylinder 194a. The second rotating friction cylinder 194b is fixed on a pair of cylindrical sliding wooden blocks 196 to rotate, and then slides on a pair of vertical support injections 197. A piece of wood block 198 slides toward the separated cylinders 194a and 194b by the routing device 193 of this sawing mechanism, and the cylinders 194b are divided in the direction of the wood 198 by the partition spring 199. The rotation of the handle 195 rotates the friction cylinder 194a and causes the wood 198 to advance in the direction of the saw.

Referring to FIG. 25, the saw is extended vertically upward from the platform 192 by an outer rectangular frame 201. The second rectangular frame is located in the first frame 201 and moves linearly relative to this frame. The frame 202 is fixed on the rail 203, which makes the displacement easier to control. The third rectangular frame 204 is located in the second frame 202 and is fixed on the frame 202 by a bracket 205. The three vertical sawing elements 206 are vertically fixed on the frame 204 and are fixed by screws 207 and rubber compression bolts 208, so that the sawing element 206 has a relative linear displacement with respect to the frame 204.

It can be seen from FIGS. 22 and 26 that the first motor 211 has a starting shaft 212 connected to the pulley 214 via a starting belt 213. The latter is fixed on the shaft 215, which activates a machine shaft 216 connected to the reciprocating rod 217 by a suitable motion conversion mechanism, as shown in FIG. 25, the check rod 207 is connected to the frame 202. Therefore, the motor 211 activates the belt 213, the pulley 214, the shaft 215, the crankshaft 216, and the reciprocating rod 217 to transfer a substantially linear back-to-return movement to the skeleton 202, and then to the sawing element 206 via the skeleton 202 and the inner skeleton 204.

It can be seen from FIG. 25 that the second starting motor 221 is connected to the crankshaft 223 via an elastically driven shaft 222, and then the sawing element 206 is connected via a linear reciprocating rod 224. Therefore, the second motor 221 transmits an auxiliary forward-return movement to the sawing element 206. The frequency of this displacement is greater than the basic forward-return movement transmitted through the skeleton 202, and the amplitude is smaller than the basic forward-return movement transmitted through the skeleton 202.

The wood placed on the platform 192 is fixed by the route device 192, and then the wood block is advanced to the innermost skeleton 204 by the rotation of the handle 195, and the wood block can be effectively slid by the vibration of the sawing element 206 in the skeleton 204 . The movement of the wood block towards the reciprocating sawing element can be controlled mechanically as shown in the figure or controlled by a suitable mechanical advancement device. Such a design is commendable.

Referring to Figures 27 and 28, shown in the figure is a fixed, cut-off cutting mechanism. As shown in the figure, this mechanism is composed of a horizontally placed rectangular frame 231, in which the frame 231 slides on the vertical support pillars 232, these support pillars are rigidly fixed on the support base plate 233, the frame is in the upward direction by a compression spring 234 separate. A suitable rotatable handle fixed in a pivoting manner can control the movement of the skeleton to the base plate 233. The starter motor 236 has a starter shaft 237, which is connected to the gear set 240a, 240b, 240c, 240d through gears 238, 239, and the gears 240a, 240d are respectively combined with the discs 241a, 241d fixed at the centrifugal position. The disks are respectively located in the motion conversion mechanisms 242a, 242d. When the discs 241a, 241d fixed at the centrifugal position rotate, they will produce a linear auxiliary output. These motion conversion mechanisms 242a, 242d are composed of Scotch Yoke mechanisms.

The motion conversion mechanisms 242a, 242d are respectively connected to the upper and lower linear auxiliary displacement rods 243a, 244a, 243d, 244d.

The lower displacement rods 244a, 244d are respectively connected to the tool fixing rods 245a, 245d. A cut-off tool 246 is fixed between the two rods. Such a fixing method can be clamped at any desired angle between the tool 246 and the base plate 233. control.

The upper reciprocating rods 243a, 243d are connected to the counterweights 2488, 248d via appropriate movement reversal couplings 243a, 243d.

When in use, when you want to use a cutting tool to cut the material placed on the substrate 233, the skeleton 231 uses the rotational displacement of the handle 235 to lower the material to the substrate 233, and in this way, a linear displacement is transmitted to the tool 246 . At the same time, the motor 236 transmits the auxiliary linear return movement of the cutter 246 through the displacement rods 244a, 224d and the supports 245a, 245d, so that the cutter can easily penetrate the material and cut it. At the same time, a back-to-return movement is transferred to the counterweights 248a, 248d in the opposite direction so that the vibration of the system can be balanced.

As mentioned above, the angle of the cut-off tool 246 can be easily adjusted by suitable fixing supports 245a, 245d.

Another way to transfer the auxiliary reset and move to the 2 ends of the tool in the same direction is to reverse the eccentricity of the eccentric fixed disc 241a relative to the other eccentric fixed disc 241d to ensure that the support rods 245a and 245d reciprocate in opposite directions. Moving, in this way, effective vibration displacement can be transmitted to the cutter 246, making it easier to penetrate or cut hard or thick materials. This vibration displacement can also reduce the instantaneous contact area between the tool and the material.

For the cutting tool mechanism described above, the tool can be replaced by a set of piercing pins, so when the set of piercing pins descends to an object, such as a circuit board, the pierceable and transfer required auxiliary will be moved to the reset pin, It can effectively make any type of perforation on the board.

Refer to Figure 29, which illustrates the cutting device used for cutting, such as paper, metal, or carpet.

This equipment consists of a fixed cutting tool 251 and a rotating disk cutting tool 252 parallel to it. The contact surface between the tool 251 and the disk 252 is quite sharp, as shown in the cross-sectional view of FIG. 30. The further structure of this equipment is as follows. The frame 253 has a starter motor 254 fixed on it. The motor has a starter shaft 255 connected by gear sets 256 and 257, and then a crankshaft with the innermost crank 258a and the outer crank 258b is connected. 258. The innermost crank 258a is connected to a linear reciprocating rod 259 via a suitable motion conversion mechanism, and this rod is pivotally connected to the circumferential portion 260 of the disc 252 with its other end. The disc 252 is pivotally connected to the frame 253 with its other circumferential portion 261.

The outer crank 258b is connected to the counterweight 262 by means of an appropriate motion conversion mechanism and a return-to-return rod 263.

During operation, the motor 254 is activated and then transmitted to the crankshaft 258, so that the shearing disc 252 has an angular auxiliary displacement relative to the cutter 251. If the material is put between the cutter and the cutting disc at this time, the auxiliary moving to the reset will help to cut this material. In this case, it is better to use the transmission of basic linear motion to cut the material.

When the angle assisted reset movement is transferred to the shearing disc, a relative resetting movement is transferred to the counterweight 262. This displacement and the displacement of the shearing disc are in antiphase, so the vibration generated by the tool will be cancelled out, greatly Reduce the vibration of the entire tool.

The cutting tool as described above is composed of the same type of hand-held penetrating tool as described in FIG. 14 and connected cutting parts 251 and 252.

Among the various combinations of auxiliary displacement and basic displacement just described, the present invention can be applied to various combinations. However, in all cases, the displacement is along a one-dimensional longitudinal axis (ie, a pin), either a cylindrical penetrating element or a planar penetrating element on a plane.

The tool according to the present invention can be used to penetrate (drill, cut, plan, etc.) workpieces of different materials and shapes. However, in very brittle materials, the method used for penetrating elements is to remove particles accumulated in the path that the penetrating elements pass. Such methods have been used in through elements such as sawing or drilling.

In particular, when the workpiece to be worn is a highly elastic material, such as rubber or similar materials, the workpiece must be compressed before penetration. In the same situation, if the tool is used to penetrate uneven or defective materials, lateral force must be applied to the workpiece to prevent unnecessary cracks on the workpiece as the tool advances.

Using the mechanisms shown in Figures 14, 17 and 18, in the actual type of penetration tool system used for cutting/drilling, the frequency range of the auxiliary displacement transmitted by the penetration element is 30-300Hz (preferably 50-100Hz), and the amplitude range is It is 0.02-3.5 mm (preferably 0.1-1.5 mm), and the horsepower range used by the tool is 200-1000 watts (preferably 500-600 watts).

Through tool system