Driving device capable of directly converting rotary motion into linear reciprocating motion

Abstract

The invention relates to a driving device capable of directly converting rotary motion into linear reciprocating motion, in particular to a driving device capable of directly converting the rotary motion into the linear reciprocating motion by using three parts, namely two end cams capable of realizing complementation and mutual meshing, and a machine body. According to the technology, a pestle type washing machine with the washing effect closer to that achieved through hand rubbing or wooden stick beating can be simulated, and due to the fact that the path for doing work on clothes is shortened and power consumption is reduced, low abrasion, high cleanliness, water saving, electricity saving and time saving become possible. By means of the technology, a traditional piston type air compressor or an internal combustion engine can be slimmed, after a crankshaft and a connecting rod in the piston type air compressor or the internal combustion engine are removed, abrasion, vibration, noise and the size of the whole machine can be reduced, and efficiency and response speed are improved.

Description

TECHNICAL FIELD

[0001] The present invention relates to a kind of drive device that can directly convert rotary motion into linear reciprocating motion, belonging to the technical field of mechanical transmission. BACKGROUND

[0002] In traditional piston air compressor or internal combustion engine and other machinery, there is a mechanism called "crankshaft connecting rod", and it is this mechanism that enables the piston air compressor or internal combustion engine to convert rotary motion into linear reciprocating piston motion or convert linear reciprocating piston motion into rotary motion. For more than a hundred years, the crankshaft connecting rod mechanism has become an indispensable part of them. However, it is not difficult to find that it is this seemingly indispensable mechanism that makes these traditional piston air compressors or internal combustion engines look too bulky, makes their efficiency low, and thus brings unnecessary additional wear, vibration and noise. SUMMARY

[0003] The present invention uses two end face cams that can realize complementation and mutual engagement, with the top edge of the cylindrical edge distributed according to a specific contour curve, together with a body, a total of three parts, to make "a kind of drive device that can directly convert rotary motion into linear reciprocating motion". This technology can further optimize the existing traditional machinery that still uses the crankshaft connecting rod mechanism technology, eliminate the crankshaft connecting rod, make them slim, and further improve their efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0004] Figure 1 is a structural schematic diagram of end face cam 1 with the features of claims 1, 2 and 3 of the present invention.

[0005] Figure 2 is a structural schematic diagram of end face cam 2 with the features of claims 1, 2 and 3 of the present invention.

[0006] Figure 3 is a structural schematic diagram of body 3 with the features of claims 1, 2 and 3 of the present invention.

[0007] Figure 4 is a schematic diagram of "a kind of drive device that can directly convert rotary motion into linear reciprocating motion" composed of end face cam 1, end face cam 2 and body 3 with the features of claims 1, 2 and 3 of the present invention.

[0008] Figure 5 is a kind of "pestle" type washing machine that uses linear reciprocating "pestle" type pounding to replace the "pestle" type washing machine that uses wave wheel rotation to do work on clothes.

[0009] Figure 6 is a schematic diagram of the main drive part of a conventional piston air compressor.

[0010] Figure 7 is a schematic diagram of the main drive part of a new piston air compressor without a crankshaft and connecting rod obtained after the patented technology of the present application is implanted into Figure 6 a conventional piston air compressor.

[0011] Figure 8 is a schematic diagram of the main drive part of a new internal combustion engine without a crankshaft and connecting rod obtained after the patented technology of the present application is implanted into a conventional internal combustion engine using the crankshaft and connecting rod mechanism technology. DETAILED DESCRIPTION

[0013] A driving device capable of directly converting rotary motion into linear reciprocating motion, which is composed of two end face cams 1 and 2 that can realize complementary and mutual engagement, and a machine body 3, and a total of three parts:

[0014] The end face cam 1 and the end face cam 2 are both compound wheels, and the end face cam 1 is composed of an end face cam 101, an end face cam 102, a cam seat 103, and a rotating shaft 104. The end face cam 101 and the end face cam 102 are back-to-back and are a mirror-symmetrical whole assembly. The wave crest P1 of the cam surface of the end face cam 101 is upward, and the wave crest P2 of the cam surface of the end face cam 102 is downward. The overall height of the assembly is the distance P1-P2 between the wave crest P1 and the wave crest P2. A cylindrical deep hole 105 is opened through the end face cam 101 and the end face cam 102 from top to bottom along the axis of the assembly. The end face cam 1 has an upwardly open cylindrical cup-shaped cam seat 103. The inner wall of the upwardly open cylindrical cup-shaped cam seat 103 is tightly attached to and rigidly connected with the outer wall of the end face cam 101 and the end face cam 102 assembly. The rotating shaft 104 is integrally formed below the cam seat 103.

[0015] The end face cam 2 of the part-time piston is composed of an end face cam 201, an end face cam 202 and a shaft 203. The top end of the end face cam 2 is a circular plane 205 which is used as a linear reciprocating output end, the face of the circular plane 205 faces upward, a piston ring 206 is arranged on the cylindrical wall below the circular plane 205, a long hole 204 is opened along the axial direction below the piston ring 206 and through the cylindrical surface of the end face cam 2 in the radial direction, the effective length of the long hole 204 is slightly greater than the peak-to-peak value P-P of the specific profile curve of the cam curve edge on the radial outer cylindrical surface of the end face cam 1 or the end face cam 2, and the peak of the end face cam 201 facing downward is below the long hole 204, the end face cam 201 extends downward along the axial direction with a cylindrical shaft 203, the shaft 203 is inserted from the top of the end face cam 1 and passes through the cylindrical deep hole 105 of the end face cam 101 and the end face cam 102 assembly, so that the end face cam 201 facing downward is tightly engaged with the end face cam 101 facing upward and forms a complement, the end face cam 202 facing upward which is sleeved on the shaft 203 is moved downward from the position where it is tightly engaged with the end face cam 201 facing downward and forms a complement by a distance P1-P2 between the peak P1 and the peak P2 of the whole height of the end face cam 101 and the end face cam 102 assembly, and is rigidly connected with the lower bottom of the shaft 203 at the position below the end face cam 101 and the end face cam 102 assembly.

[0016] The lower bottom of the body 3 has an opening 301, the end face cam 1 passes through the opening 301 in the lower bottom of the body 3 through the rotating shaft 104 at the bottom thereof, and is installed in the opening 301 in the lower bottom of the body 3 so as to only rotate and cannot move up and down. The body 3 also has horizontally split holes 302, and the pin 303 passes through the split holes 302 in the body 3 and the long hole 204 in the cylindrical wall of the end face cam 2, so that the end face cam 2 is fixed in the radial direction with the body 3, and the end face cam 2 can only linearly reciprocate along the axis of the end face cam 1 and the end face cam 2 under the limitation of the pin 303 fixed with the body 3 and the cylindrical deep hole 105 of the end face cam 1, and the amplitude of the linear reciprocation does not exceed the peak-to-peak value P-P of the specific profile curve of the cam curve edge on the radial outer cylindrical surface of the end face cam 1 or the end face cam 2.

[0017] The specific profile curve of the edge of the cylindrical top end of the end face cam 1 and the end face cam 2 is taken as n, n≥1, n is an integer multiple of 1, and the specific profile curve of the edge of the cylindrical top end can be a triangular wave or a positive spin wave.

[0018] Since the peak-to-peak value P-P of the specific profile curve of the cam curve edge on the radial outer cylindrical surface of the end face cam 1 or the end face cam 2 is limited by the size of n and the size of the cylindrical diameter of the end face cam 1 or the end face cam 2, the value of n is preferably selected between 1, 2 or 3, and should not be too large.

[0019] Because the end face cam 2 is limited and positioned by the pin 303 fixed on the body 3 and the cylindrical deep hole 105 on the end face cam 1, the device can run in a relatively stable state even if the value of n is 1.

[0020] When the value of the specific profile curve of the cam surface edge on the radial outer cylindrical surface of the end face cam 1 and the end face cam 2 is n≥3, at each moment during the operation of the device, there are at least three engagement points between the end face cam 101 and the end face cam 201 in the end face cam 1 and the end face cam 2, which are evenly distributed around the cam axis and on a plane perpendicular to the axis; at the same time, at this moment, there are also at least three engagement points between the end face cam 102 and the end face cam 202 below the plane, which are also evenly distributed around the cam axis and on another plane perpendicular to the axis, and the distance between the two planes is always constant. It can be seen that these evenly distributed engagement points around the cam axis provide good support for the stable operation of the device.

[0021] Example 1

[0022] A "pestle" type washing machine using linear reciprocating pounding motion

[0023] The current pulsator type washing machine adopts a washing method of floating and rapidly rotating the laundry in the washing liquid. If there is not enough washing space and a large amount of washing liquid to float the laundry, the laundry will always sink to the bottom of the washing tub and cannot be normally washed, and finally may be abraded. Because the washing motor must drive the laundry and a large amount of washing liquid in the rotating washing tub at the same time, the washing motor must have a large power reserve and consume more electric energy. The pulsator type washing machine has high washing degree, saves time and effort, and the disadvantage is that the abrasion rate of the laundry is high.

[0024] The drum type washing machine simulates the principle of a stick hitting the laundry, and uses the rotation of the drum to repeatedly lift and drop the laundry in the drum, which has the advantages of less abrasion of the laundry and higher washing degree. The machine uses less water than the pulsator type, but because it uses the way of rotating and hitting the laundry with the drum, the washing efficiency is relatively low and the washing cycle is long. In addition to consuming a large amount of electric energy each time, it is also testing whether we have enough time and enough patience.

[0025] In real life, we can often see that many families choose to wash clothes by hand instead of using washing machines when washing a small amount of clothes. This problem is worth our deep thinking. Obviously, although the current washing machine has partially replaced the heavy labor of manual work, it seems to be labor-saving but does not let people save effort at all. The current washing machine is water-consuming, power-consuming, time-consuming and detergent-consuming, which is a common understanding that many relevant people are concerned about but feel helpless, and it is not suitable for the green low-carbon and modern fast-paced social life we advocate at present.

[0026] Mortar and pestle is a pair of labor tools that our ancestors have been widely used in ancient times. The jade rabbit that crushes medicine in the ancient Chinese myth of Toad Palace and the "Wu Song" poem by the great poet Li Bai in the Tang Dynasty "A piece of moonlight in Chang'an, ten thousand households are making clothes" witness the widespread application of this simple tool for thousands of years. Until the late 1970s, before the washing machine began to be popular in China, many remote areas in the folk still used this ancient and simple way of beating with a club when washing clothes. The vitality of mortar and pestle is so strong that it is simple and effective, which is worth our reference.

[0027] If the technology of the present application is introduced into the current washing equipment, the clothes soaked in the washing liquid are confined in a small and relatively closed "mortar", and the "pestle" type pounding is applied to the clothes. In this way, not only can the path of work on the clothes be shortened, but also the power consumption of the motor can be greatly reduced because a large amount of washing liquid does not need to be driven to force the clothes to rotate, and the use of a small and relatively closed "mortar" is also conducive to the substantial reduction of the amount of washing liquid and the time of each water inlet and drainage.

[0028] Figure 5 This is a structural diagram of the new "pestle" type washing machine

[0029] Figure 5 The "pestle" type washing machine of the present application is composed of two Figure 4 The "pestle" type washing machine of the present application is composed of two

[0030] The "pestle" type washing machine of the present application is composed of two Figure 5 The "pestle" type washing machine of the present application is composed of two Figure 5 The "pestle" type washing machine of the present application is composed of two

[0031] Figure 5The "pestle" type washing machine is based on the current full-automatic impeller washing machine and is slightly modified.

[0032] The inner barrel 3 in a current full-automatic impeller washing machine is equivalent to Figure 4 The inner barrel 3 in a current full-automatic impeller washing machine is equivalent to Figure 4 The end face cam 1 and the end face cam 2 with the features of claims 1, 2 and 3 of the present application replace the impeller in the full-automatic impeller washing machine. The pin 303 is passed through the opening 302 on the wall of the inner barrel 3 and the long hole 204 on the cylindrical wall of the end face cam 2, and the end face cam 2 is fixed in the radial direction with the inner barrel 3. The rotation shaft 104 of the newly placed end face cam 1 in the end face cam 1 is rigidly connected with the impeller shaft of the clutch assembly 6 of the washing machine. When the end face cam 1 is driven to rotate as the main rotation by the impeller shaft of the clutch assembly 6, the end face cam 2 without the piston ring 206 is an inverted "pestle" driven by the end face cam 1 to only make linear reciprocating percussion movement. Above the end face cam 1 and the end face cam 2 in the inner barrel 3 is the draining tray 11, which is provided with draining holes 1101 and damping buffer springs 1102. Above the draining tray 11 is the upper cover 12, which is also provided with draining holes 1201 and damping buffer springs 1202, and has at least three manually or electrically controlled positioning pins 1203 horizontally and symmetrically extending from the side wall, which are inserted into the draining holes 304 on the inner barrel 3 to position the upper cover 12. The top of the upper cover 12 is further provided with a flexible and retractable water storage bag 13, which can be drained downward through the draining holes 1201 of the upper cover 12 through the water drainage valve 1301 arranged at the lower bottom. The space 15 for placing the laundry is left between the draining tray 11 and the upper cover 12. The space 15 between the inner barrel 3, the draining tray 11 and the upper cover 12 forms a relatively closed inverted "mortar", the draining tray 11 is the movable seal of the relatively closed inverted "mortar", and the upper cover 12 is the bottom of the inverted relatively closed "mortar".

[0033] Operation principle

[0034] The end face cam 1 and the end face cam 2 with the features of claims 1, 2 and 3 of the present application replace the impeller in the full-automatic impeller washing machine. The pin 303 is passed through the opening 302 on the wall of the inner barrel 3 and the long hole 204 on the cylindrical wall of the end face cam 2, and the end face cam 2 is fixed in the radial direction with the inner barrel 3. The rotation shaft 104 of the newly placed end face cam 1 in the end face cam 1 is rigidly connected with the impeller shaft of the clutch assembly 6 of the washing machine. When the end face cam 1 is driven to rotate as the main rotation by the impeller shaft of the clutch assembly 6, the end face cam 2 without the piston ring 206 is an inverted "pestle" driven by the end face cam 1 to only make linear reciprocating percussion movement. Above the end face cam 1 and the end face cam 2 in the inner barrel 3 is the draining tray 11, which is provided with draining holes 1101 and damping buffer springs 1102. Above the draining tray 11 is the upper cover 12, which is also provided with draining holes 1201 and damping buffer springs 1202, and has at least three manually or electrically controlled positioning pins 1203 horizontally and symmetrically extending from the side wall, which are inserted into the draining holes 304 on the inner barrel 3 to position the upper cover 12. The top of the upper cover 12 is further provided with a flexible and retractable water storage bag 13, which can be drained downward through the draining holes 1201 of the upper cover 12 through the water drainage valve 1301 arranged at the lower bottom. The space 15 for placing the laundry is left between the draining tray 11 and the upper cover 12. The space 15 between the inner barrel 3, the draining tray 11 and the upper cover 12 forms a relatively closed inverted "mortar", the draining tray 11 is the movable seal of the relatively closed inverted "mortar", and the upper cover 12 is the bottom of the inverted relatively closed "mortar". Figure 5The "pestle" type washing machine is powered on, the upper cover 12 is opened, the laundry to be washed is placed in the draining tray 11 above the end face cam 2 with "pestle" function, the washing liquid is added and the washing liquid is allowed to cover the laundry to be washed, the upper cover 12 is covered after the upper cover 12 is added above the laundry to be washed, the positioning pin 1203 in the upper cover 12 is extended and inserted into the draining hole 304 on the barrel wall of the inner barrel 3, and the upper cover 12 is locked.

[0035] When the washing machine is in the "washing" mode, the controller 14 issues an instruction to command the motor 7 to drive the impeller shaft of the clutch 6 through the belt 8 to rotate the end face cam 1 at a low speed; at the same time, the clutch spring in the clutch 6 is released, the clutch sleeve is separated from the dehydration shaft, the brake band holds the brake disc, and the dehydration shaft and the inner barrel 3 cannot rotate. Because the inner barrel 3 cannot rotate, the end face cam 2 attached to the inner barrel 3 also cannot rotate; finally, under the clamping of the end face cam 1 and the inner barrel 3, the end face cam 2 radially locked by the pin 303 on the barrel wall of the inner barrel 3 can only be driven by the actively rotating end face cam 1 and passively perform a linear reciprocating "pestle" pounding movement along the axis of the end face cam 1 and the end face cam 2.

[0036] The inverted "pestle" type pounding has an advantage: during each return stroke of the "pestle", the gravity of the laundry can be fully utilized to allow the laundry to naturally rebound, stretch and become fluffy again, making it easier to wash.

[0037] Considering that the "pestle" will generate relatively large vibration and noise during pounding, a permanent water injection or sand injection counterweight can be added to the bottom of the washing machine; when the washing machine is in the "washing" program mode, water must also be injected into the flexible water storage bag 13 on the top of the upper cover 12, and this temporary water storage pool is used for noise reduction and shock absorption; when the "washing" program is about to end, it is slowly released as a water source for "spray rinsing".

[0038] In the dehydration mode, the controller 14 issues an instruction to command the electromagnetic iron to pull the clutch sleeve in the clutch 6 upward and engage and lock the clutch sleeve with the belt pulley shaft through the helical spline, the clutch spring holds the clutch sleeve and the dehydration shaft engaged and locked by the belt pulley shaft, and the dehydration shaft is mechanically locked. At the same time, the impeller shaft is rigidly connected to the dehydration shaft through the gear locking mechanism inside the clutch. Finally, the belt pulley shaft, the impeller shaft, and the dehydration shaft and the inner barrel 3 are connected together and directly driven to rotate synchronously by the motor 7. At the same time, the end face cam 1 rigidly connected to the impeller shaft and the end face cam 2 radially locked together with the inner barrel 3 will also rotate synchronously with the inner barrel 3. Obviously, the end face cam 2 in the dehydration mode will not perform a linear reciprocating "pestle" pounding movement.

[0039] In the minds of many particularly fastidious housewives, the laundry that is "washed" by hand is the cleanest. The frequency of "hand washing" is at most 2-3 times per second, and the amplitude of "hand washing" is only 5-10 cm. Thus, to simulate the effect of "hand washing" or "stick beating", the "pestle" of the "pestle" washing machine in Figure 5 may have a beating frequency of 3 times per second, and a beating amplitude of about 10 cm.

[0040] To enable the "pestle" washing machine in Figure 5 to operate more smoothly, Figure 5 the specific profile of the end face edge of the end face cam 1 and the end face cam 2 in the "pestle" washing machine in is a rectified cycloid, and the number n of the rectified cycloid is recommended to be 3.

[0041] Figure 5 If the number n of the rectified cycloid of the specific profile of the end face edge of the end face cam 1 and the end face cam 2 in the "pestle" washing machine in is set to 3, and the beating frequency of the "pestle" is set to 3 times per second, then when the washing machine is placed in the "washing" program, the rotational speed of the motor 7 on the pulley shaft of the clutch 6 via the belt 8 should be 60 rpm.

[0042] Figure 5 In the "pestle" washing machine in , the peak-to-peak value P-P of the profile of the rectified cycloid of the end face edge of the end face cam 1 and the end face cam 2 is the beating amplitude of the "pestle".

[0043] In order to enable the "pestle" to have a larger beating amplitude and reduce the dead space in the inner drum 3 during washing, the diameters of the end face cam 2 used as the "pestle" and the end face cam 1 matched therewith should be as close as possible to the inner diameter of the inner drum 3.

[0044] Figure 5 Since the end face cam 1 and the end face cam 2 occupy a considerable space height in the inner drum 3, the depth of the inner drum 3, the outer drum 4, and the casing 5 in the "pestle" washing machine in should be deeper than the inner drum, the outer drum, and the casing of the current full-automatic pulsator washing machine.

[0045] The clutch assembly of the current full-automatic pulsator washing machine generally includes a planetary gear reduction mechanism, which has a slightly complex structure and often causes a high failure rate of the washing machine. Therefore, the clutch assembly of the "pestle" washing machine in Figure 5In the "pestle" type washing machine, the clutch 6 can also be slightly simplified: the planetary gear reduction mechanism is abandoned, and the pulley shaft of the clutch 6 assembly input end and the impeller shaft of the output end are directly replaced with a rigid straight shaft. As for the "reduction" function of the impeller shaft lost after the clutch 6 is simplified, it can be compensated by selecting a motor 7 with variable frequency speed regulation function. In addition to allowing the clutch 6 to be simplified, the main advantage of selecting a motor 7 with variable frequency speed regulation function is that when the washing machine is in the "washing" program, it is necessary to select different pestle beating frequencies according to the material and cleanliness of the clothes to be washed. The motor 7 with variable frequency speed regulation function can greatly facilitate this.

[0046] When the "pestle" beating mode replaces the rotation of the impeller, with the change of the washing mechanism, the "forward" and "reverse" rotation and the "stop-start" function of the original fully automatic impeller type washing machine in the "washing" mode are too time-consuming and no longer applicable. Figure 6 The working program of the "pestle" type washing machine cannot follow the original washing machine and needs to be rewritten.

[0047] At this point, the entire working process of the "pestle" type washing machine is like a scene in the early years at the small river in the village, where the village girls are using a club to beat the clothes in the bamboo basket immersed in the flowing water.

[0048] Example 2

[0049] A piston air compressor without crankshaft and connecting rod

[0050] Figure 6 It is a schematic diagram of the main transmission structure of a traditional piston air compressor. This type of piston air compressor adopts a method of converting the rotary motion of the motor into linear reciprocating piston motion to compress air, and the main transmission part is composed of a cylinder body 3 with its attached configuration, a motor 7, a piston 16, a crankshaft 17 and a connecting rod 18. In the process of converting the rotation of the motor 7 into the linear reciprocating motion of the piston 16, the crankshaft 17 and the connecting rod 18 are usually used to realize the linkage between the motor shaft 701 and the piston 16. From Figure 7 It can be seen from the above that the crankshaft 17 and the connecting rod 18 in the traditional piston air compressor not only occupy limited space in the device, making the device bulky, but also bring many disadvantages.

[0051] If the present technology is implanted in such devices, the redundant crankshaft 17 and connecting rod 18 can be eliminated, the overall structure of the device is more simple, the volume, vibration, noise and wear of the device are reduced, and the overall efficiency and response speed of the device are further improved.

[0052] Figure 6 is implanted into Figure 4 The schematic diagram of the main transmission part of the new piston air compressor without crankshaft and connecting rod generated after the traditional piston air compressor in

[0053] In fact, Figure 6 The "a driving device capable of directly converting rotary motion into linear reciprocating motion" shown in the figure has the rudiment of the main transmission part of the new piston air compressor without crankshaft and connecting rod. To eliminate Figure 6 the crankshaft 17 and connecting rod 18 in Figure 4 the traditional piston air compressor, only need to replace Figure 7 the traditional piston air compressor with the "a driving device capable of directly converting rotary motion into linear reciprocating motion" with the features of claims 1, 2, 3 in Figure 6 , make the indicators of the end face cam 2 with piston function and the body 3 with cylinder and its attached configuration meet the adaptation of the piston air compressor, and finally rigidly connect the rotating shaft 104 of the end face cam 1 passing through the lower bottom opening 301 of the body 3 with the rotating shaft 701 of an additional motor 7 through the shaft coupling 19. In this way, a new piston air compressor without crankshaft and connecting rod capable of replacing Figure 7 the traditional piston air compressor is generated.

[0054] Operating principle

[0055] In Figure 6 , the rotating shaft 701 of the motor 7 is linked with the rotating shaft 104 of the end face cam 1 through the shaft coupling 19 to drive the rotation of the end face cam 1. Since the end face cam 2 with piston function is simultaneously restricted and positioned by the cylindrical deep hole 105 on the end face cam 1 and the pin 303 fixed on the body 3, when the motor 7 drives the end face cam 1 to rotate actively, the end face cam 2 at this time will not rotate with the end face cam 1, but can only be forced to make linear reciprocating piston motion along the axis of the end face cam 1 and the end face cam 2 under the clamping of the end face cam 1 and the body 3.

[0056] Figure 7 The path experienced by the piston of the traditional piston air compressor in its working cycle from top dead center to bottom dead center is the piston stroke, the length of which is marked as S, which directly depends on the rotating diameter of the crankshaft connecting rod shaft part. The crankshaft will rotate 180 degrees for each complete piston stroke. In such a piston air compressor, excessive piston stroke will lead to the increase of engine size, and higher engine height may hinder the improvement of its lightweight and high speed performance.

[0057] In Figure 6 which: when the end face cam 1 and the end face cam 2 with the features of the patent claims 1, 2, 3 of the invention are substituted for Figure 7 the piston 16, the crankshaft 17 and the connecting rod 18 in the piston air compressor, a new mode of the piston air compressor is established, at this time Figure 1 the stroke S of the end face cam 2 with the piston function in the Figure 2 , Figure 7 and Figure 7 the peak-peak value P-P of the specific profile normal involute curve on the radial outer cylindrical surface of the end face cam 1 or the end face cam 2 in the

[0058] To ensure that Figure 7 the new piston air compressor can run more smoothly, Figure 8a the specific profile curve of the end face edge of the end face cam 1 and the end face cam 2 in the

[0059] Example 3

[0060] A crankshaft and connecting rod-free internal combustion engine

[0061] If the "driving device capable of directly converting rotary motion into linear reciprocating motion" technology of the invention is implanted into the current traditional internal combustion engine still using the crankshaft and connecting rod mechanism technology, the crankshaft and connecting rod mechanism therein can be eliminated to make a new crankshaft and connecting rod-free internal combustion engine.

[0062] Figure 8 is a schematic diagram of the main transmission part structure of the crankshaft and connecting rod-free internal combustion engine obtained after the technology of the invention is implanted into the current traditional internal combustion engine still using the crankshaft and connecting rod mechanism technology and the crankshaft and connecting rod mechanism therein is eliminated. This main transmission part is composed of the end face cam 1, the end face cam 2 with the features of the patent claims 1, 2, 3 of the invention, and the internal combustion engine body 3 with the cylinder and its attached configuration, plus the flywheel 20, etc.

[0063] Operating principle

[0064] The traditional internal combustion engine should have sufficient fuel, sufficient battery power, sufficient lubricating oil and coolant, and intact mechanical parts before starting. In addition, the traditional internal combustion engine usually needs to rotate the flywheel and the crankshaft by external power before ignition to reach the minimum starting speed necessary for starting, to ensure that the oil lubrication system establishes oil pressure, the combustible mixture is formed in the cylinder, and the mechanical resistance during starting is reduced. At the same time, the engine must have a certain starting torque to overcome the various resistances when the crankshaft transitions from a static state to a minimum starting speed.

[0065] Consistent with the starting of the traditional internal combustion engine, the main body of the crankshaft-free and connecting rod-free internal combustion engine of Figure 8 should also follow the above principles before starting, and its starting process can refer to the standard operation of the traditional internal combustion engine. The difference is that the return stroke of the piston of the traditional internal combustion engine is completed by the flywheel with rotational inertia driving the crankshaft and connecting rod. The return stroke of the piston of the crankshaft-free and connecting rod-free internal combustion engine of the present embodiment is completed by the flywheel with rotational inertia driving the end face cam 1 with the features of the present patent, which in turn drives the end face cam 2 to move as a piston.

[0066] Whether it is a traditional internal combustion engine or the crankshaft-free and connecting rod-free internal combustion engine of the present embodiment, when the piston reaches the top and bottom dead centers, the driving member is just collinear with the driven member. At this time, if the driving force cannot generate effective rotational torque, both internal combustion engines may encounter the problem of dead center.

[0067] Figure 8b Figure 8 is a schematic diagram of the main drive site structure when the piston of the crankshaft-free and connecting rod-free internal combustion engine of the present embodiment reaches the bottom dead center. As can be seen from the figure, at this moment, between the end face cam 1 that can only rotate and the end face cam 2 that can only move as a piston, the end face cam 101 is just fully engaged with the end face cam 201, and at the same time, the peak of the end face cam 102 just reaches above the peak of the end face cam 202.

[0068] Figure 8a Figure 8 is a schematic diagram of the main drive site structure when the piston of the crankshaft-free and connecting rod-free internal combustion engine of the present embodiment reaches the top dead center. As can be seen from the figure, at this moment, between the end face cam 1 that can only rotate and the end face cam 2 that can only move as a piston, the peak of the end face cam 101 just reaches below the peak of the end face cam 201, and at the same time, the end face cam 102 is just fully engaged with the end face cam 202.

[0069] From Figure 8b and Figure 8bAs can be seen, in this embodiment of the internal combustion engine without a crankshaft and connecting rod, the driving and driven components are collinear at the critical moments when the piston reaches the top and bottom dead centers. To avoid dead points between the end face cam 1, which can only rotate, and the end face cam 2, which can only move the piston, this embodiment can be operated according to the operating specifications of a traditional internal combustion engine.

[0070] The conventional solution for avoiding dead spots in internal combustion engines is to first rotate the flywheel using external power, causing the flywheel to drive the crankshaft and connecting rod to rotate. Ignition can only begin after the flywheel, crankshaft, and connecting rod reach the minimum speed necessary for starting and have sufficient starting torque to overcome dead spots. In this embodiment, the internal combustion engine has no crankshaft and no connecting rods. Instead, the flywheel 20 is first rotated using external power, causing the flywheel 20 to drive the end face cam 1 to rotate. Ignition can only begin after the flywheel 20 and end face cam 1 reach the minimum speed necessary for starting and have sufficient starting torque to overcome dead spots.

[0071] Similarly, both traditional internal combustion engines and the crankshaft-less, connecting rod-less internal combustion engine of this embodiment face the issue of ignition timing. Ideally, the spark generated by the spark plug ignites the air-fuel mixture, the flame propagates smoothly within the cylinder, and the point of maximum pressure should occur just after the piston has passed top dead center and begun its downward movement. Similar to the need for an ignition advance angle in traditional internal combustion engines, controlling the ignition timing of this device is also crucial, considering the time required for combustion when the spark ignites the mixture.

[0072] from Figure 1 As can be seen, if the advance angle is too small and the ignition is too late, the piston has already moved downwards before ignition. The consequence is that the combustion process occurs while the cylinder volume is constantly increasing, resulting in a decrease in maximum pressure. This leads to engine weakness, overheating, and increased fuel consumption. When the exhaust valve opens, combustion may not be finished, causing backfiring in the exhaust pipe. Similarly, if the advance angle is too large and the ignition is too early, the air-fuel mixture is ignited prematurely while the piston is still in the upward compression stroke. The consequence is that the enormous pressure generated by combustion will collide head-on with the still-moving piston, causing the end face cam 1, which is rotating due to the flywheel's inertia, to be suddenly deflected and forcibly blocked by the end face cam 2, which also acts as the piston. This severely damages the meshing surfaces between end face cam 1 and end face cam 2, as well as the bearings, causing the piston to lose its function and resulting in a decrease in power. This is a harmful phenomenon that must be avoided.

[0073] In Figure 8, the stroke S of the end face cam 2, which has a piston function, corresponds numerically to... Figure 2 , ​The peak-to-peak value P-P of the specific profiled normal helix curve of the cam surface edge of the radially outer cylindrical surface of the end cam 1 or the end cam 2 in Fig. 8 is subject to the size of the diameter of the end cam 1 or the end cam 2, and the maximum value of the diameter of the end cam 1 or the end cam 2 is limited by the diameter of the engine block 3.

[0074] To ensure that the internal combustion engine in Fig. 8 can run more smoothly, the specific profiled curve of the end surface edge of the end cam 1 and the end cam 2 in Fig. 8 adopts a normal helix curve. When the normal helix curve of the end surface edge of the end cam 1 and the end cam 2 takes n = 1, the end cam 2 that makes piston movement rotates 180 degrees for each stroke of the end cam 1. If calculated according to four strokes to complete a working cycle, the end cam 1 rotates 720 degrees in total. This parameter is equivalent to the crankshaft rotating 720 degrees to complete a working cycle of a traditional four-stroke engine. However, to make the operation of the device more stable, it is recommended that the normal helix curve takes n = 3, at which time the end cam 2 that makes piston movement rotates 60 degrees for each stroke of the end cam 1. According to four strokes to complete a working cycle, the end cam 1 rotates 240 degrees in total.

Claims

1. A drive device capable of directly converting rotary motion into linear reciprocating motion, comprising three parts: two end-face cams 1 and 2, whose top edges of cylindrical surfaces are distributed along a specific contour curve and can complement and mesh with each other, and a body 3; characterized in that: Both end face cam 1 and end face cam 2 are composite wheels. End face cam 1 is composed of end face cam 101, end face cam 102, cam seat 103, and rotating shaft 104. End face cam 101 and end face cam 102 are back-to-back and form a mirror-symmetrical integral component. The peak P1 of the cam surface of end face cam 101 faces upward, and the peak P2 of the cam surface of end face cam 102 faces downward. The overall height of the component is the distance P1-P2 between peak P1 and peak P2. The component has a cylindrical deep hole 105 that extends downward through end face cam 101 and end face cam 102 along the axis. End face cam 1 has an upward-opening... A cylindrical cup-shaped cam seat 103 has an upwardly opening inner wall that is rigidly connected to and closely adheres to the outer wall of the end face cam 101 and end face cam 102 assembly. Below the cam seat 103 is an integrally formed rotating shaft 104. The end face cam 2 consists of an end face cam 201, an end face cam 202, a shaft 203, and a piston ring 206. The top of the end face cam 2 is a circular plane 205 serving as the output end for linear reciprocating motion. The surface of the circular plane 205 faces upward. A piston ring 206 is located on the cylindrical wall below the circular plane 205. Below the piston ring 206, a piston ring 206 is located radially through the end face cam 2. A short elongated hole 204 is formed along the axial direction on the cylindrical surface. The effective length of the elongated hole 204 is slightly greater than the peak-to-peak value PP of the specific profile curve of the cam surface edge on the radially outer cylindrical surface of the end face cam 1 or end face cam 2. Below the elongated hole 204 is the end face cam 201 with its crest facing downwards. A cylindrical shaft 203 extends downwards from the axial direction of the end face cam 201. The shaft 203 is inserted from the top of the end face cam 101 and passes through the cylindrical deep hole 105 of the end face cam 101 and end face cam 102 assembly, so that the end face cam 201 with its crest facing downwards and the end face cam 101 with its crest facing upwards are closely attached and meshed, forming a complementary relationship. The shaft will be fitted with... The upward-facing end face cam 202 of 203 moves down a distance P1-P2 between the peaks P1 and P2 of the overall height of the end face cam 101 and end face cam 102 assembly from a position where it can closely mesh with the downward-facing end face cam 201 to form a complementary relationship. The end face cam 202 is then rigidly connected to the bottom of the shaft 203 at a position close to the bottom of the end face cam 101 and end face cam 102 assembly. The bottom of the machine body 3 has an opening 301. The end face cam 1 passes through the bottom opening 301 of the machine body 3 via the bottom rotating shaft 104, so that it can only rotate and cannot move up and down in the bottom opening 301 of the machine body 3.The body 3 also has horizontally bisected holes 302. A pin 303 passes through the bisected holes 302 on the body 3 and the elongated hole 204 on the cylindrical wall of the end face cam 2, fixing the end face cam 2 radially to the body 3. This prevents the end face cam 2 from rotating, as it can only reciprocate linearly along the axes of the end face cam 1 and end face cam 2. The amplitude of this linear reciprocating motion does not exceed the peak-to-peak value PP of the specific contour curve along the edge of the cam surface on the radially outer cylindrical surface of the end face cam 1 or end face cam 2.

2. A drive device according to claim 1, capable of directly converting rotary motion into linear reciprocating motion, characterized in that: The body 3 in the device can be a piston air compressor with cylinders and auxiliary configurations, or it can be an internal combustion engine with cylinders and auxiliary configurations.

3. A drive device having claims 1 and 2, capable of directly converting rotary motion into linear reciprocating motion, characterized in that: The specific profile curves of the top edge of the end face cam 1 and end face cam 2 are n, where n ≥ 1 and n is an integer multiple of 1. The specific profile curves of the top edge of the end face cam 1 and end face cam 2 can be triangular waves or sine waves.

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