Transmission system that converts reciprocating motion into forward power output

Abstract

The present invention provides a transmission system for converting reciprocating motion into positive rotation power output, comprising: a reciprocating actuator including a swing rod, and a steering and power output mechanism, which converts the reciprocating motion input by the swing rod into a positive rotation direction by the steering and power output mechanism to output uninterrupted positive rotation force.

Description

Technical Field

[0001] The invention relates to the field of transmission, and in particular to a transmission system for converting reciprocating motion into forward power output. Background Art

[0002] U.S. Patent No. 9,139,251 discloses a mechanism that can change the action of a reciprocating rod into a single-direction rotary action, but it has the following disadvantages:

[0003] 1. When the reciprocating rod 15 is driven back and forth, the belts 26 and 27 are blocked by the friction of the blocking wheel 22, which consumes a lot of energy and greatly reduces its output power.

[0004] 2. The entire mechanism requires the installation of many rollers and belts, which increases costs and maintenance issues, and also wastes a great deal of kinetic energy output, reducing its efficiency.

[0005] 3. The system is complex, has many components, and occupies a large amount of space, so it cannot be used in the production of sophisticated machinery. Summary of the invention

[0006] The object of the present invention is to provide a transmission system which can convert reciprocating motion into forward power output.

[0007] To achieve the above-mentioned purpose, a transmission system for converting reciprocating motion into forward power output of the present invention comprises: a reciprocating actuator 100, and a reversing and power output mechanism 200; the reversing and power output mechanism 200 comprises: an input gear 22 fixedly connected to an input shaft 21, so that the reciprocating actuator 100 is in forward or reverse rotation when reciprocating; a bidirectional driving gear 24 meshing with the input gear 22 through an intermediate gear 23, and the bidirectional driving gear 24 is rotatably sleeved on a transmission shaft 21a; the bidirectional driving gear 24 is connected to the input shaft 21a and the input gear 22 is connected to the input ... The movable gear 24 includes a plurality of positive rotation ratchet teeth 241 arranged on the first wheel surface 242 or the front wheel surface of the bidirectional driving gear 24, and a plurality of reverse rotation ratchet teeth 243 arranged on the second wheel surface 244 or the rear wheel surface of the bidirectional driving gear 24; a positive rotation clutch 25 is slidably engaged with the transmission shaft 21a, and includes a plurality of positive rotation ratchet wheels 251 arranged on the rear wheel surface 252 of the positive rotation clutch 25, which can always match the plurality of positive rotation ratchet teeth 241 on the first wheel surface 242 of the bidirectional driving gear 24, and the positive rotation of the bidirectional driving gear 24 is When the forward clutch 25 rotates forward, the front gear 26 also rotates forward and rotates the transmission shaft 21a forward. The front gear 26 meshes with an output gear 21c fixed on an output shaft 21b to output kinetic energy in the forward direction. A reverse clutch 27 is rotatably sleeved on the transmission shaft 21a, and includes a plurality of reverse ratchet teeth 271 arranged around the front wheel surface 27 of the reverse clutch 27. 2 can be matched with the multiple reverse ratchet teeth 243 on the second wheel surface 244 of the two-way driving gear 24 when the two-way driving gear 24 is reversed R, so as to drive the two-way driving gear 24 in the reverse R direction; and a reverse gear train 28 is meshed between the reverse clutch 27 and a rear gear 29 fixedly connected to the rear end of the transmission shaft 21a. When the two-way driving gear 24 is reversed R, the rear gear 29 is also rotated forward F through the reverse gear train 28, so as to rotate the transmission shaft 21a forward and the front gear 26 to output kinetic energy in the forward direction.

[0008] Optionally, each of the multiple forward rotating ratchet teeth 241 provided on the first wheel surface 242 of the bidirectional driving gear 24 is protruded on the first wheel surface 242, and forms at least one first inclined surface 241s from the first tooth ridge 241r toward the first wheel surface 242 and intersects with the forward rotation direction F to form a first acute angle 241a; and each of the multiple reverse rotating ratchet teeth 243 provided on the second wheel surface 244 is protruded on the second wheel surface 244, and forms at least one second inclined surface 243s from the second tooth ridge 243r toward the second wheel surface 244 and intersects with the reverse direction R to form a second acute angle 243a.

[0009] Optionally, each of the multiple forward ratchet teeth 251 provided on the rear wheel surface 252 of the forward clutch 25 is provided on the rear wheel surface 252 of the forward clutch 25, and at least one third inclined surface 251s is formed from the third tooth ridge 251r toward the rear wheel surface 252 to form a first obtuse angle 251a with the forward direction F. Therefore, when the bidirectional drive gear 24 is rotated forward F, the forward ratchet tooth 241 of the bidirectional drive gear 24 engages with the forward ratchet tooth 251 on the rear wheel surface 252 of the forward clutch 25, and the forward clutch 25 is rotated together.

[0010] Optionally, each of the multiple reverse ratchet teeth 271 provided on the front wheel surface 272 of the reverse clutch 27 is protruding from the front wheel surface 272 of the reverse clutch 27, and at least one fourth inclined surface 271s is formed from the fourth tooth ridge 271r toward the front wheel surface 272, intersecting with the reverse direction R to form a third obtuse angle 271a. Therefore, when reversing the bidirectional drive gear 24, the reverse ratchet teeth 271 of the reverse clutch 27 are meshed by the reverse ratchet teeth 243 of the bidirectional drive gear 24, and the reverse clutch 27 is linked to present a reverse R.

[0011] Optionally, the forward clutch 25 is radially provided with two protruding keys 253, which are located between the shaft hole 254 and the rim of the clutch 25. The two protruding keys 253 extend forward to slide in a pair of grooves 262 recessed by the protruding edges 261 on both sides of the shaft hole 260 of the front gear 26. When the two-way drive gear 24 and the forward clutch 25 are rotated forward, the protruding keys 253 of the forward clutch 25 slide in the grooves 262 of the front gear 26, and the forward clutch 25 is linked to drive the front gear 26 and the fixed transmission shaft 21a, and the rotational power in the forward direction is output by the meshed output gear 21c and the fixed output shaft 21b.

[0012] The present invention provides a transmission system for converting reciprocating motion into positive rotation power output, wherein the reciprocating actuator includes a swing arm and a steering and power output mechanism, which can convert the reciprocating motion input by the swing arm into a positive rotation direction through the steering and power output mechanism to output uninterrupted positive rotation force. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a schematic diagram of the structure of the present invention during forward rotation.

[0014] Figure 2 It is a front view of the reciprocating actuator of the present invention.

[0015] Figure 3 It is an enlarged schematic diagram of some gears of the present invention.

[0016] Figure 4 It is a top view of the forward clutch of the present invention.

[0017] Figure 5 The forward clutch of the present invention is Figure 4 Front view of.

[0018] Figure 6 It is a top view of the front gear of the present invention.

[0019] Figure 7 The front gear of the present invention is Figure 6 Rear view of.

[0020] Figure 8 It is a top view schematically showing the forward clutch engaging the front gear of the present invention.

[0021] Fig. 9 It is a schematic diagram of the structure of the present invention when it is reversed. DETAILED DESCRIPTION

[0022] The present invention is further described below in conjunction with the accompanying drawings and specific embodiments so that those skilled in the art can better understand the present invention and implement it, but the embodiments are not intended to limit the present invention. Referring to the various drawings, the present invention includes: a reciprocating actuator 100, and a reversing and power output mechanism 200.

[0023] As attached Figure 1 , 2, the reciprocating actuator 100 includes: a swing rod 11; a rod shaft 12 pivotally connected in a chamber 10 and connected to the rod end of the swing rod 11, and axially connected to a sector gear 13; an intermediate actuating gear 14 meshing with the sector gear 13 and pivotally connected to a gear shaft 140; and a drive shaft gear 15 meshing with the intermediate actuating gear 14 and fixedly connected to the front end (or outer end) of the input shaft 21 of the reversing and power output mechanism 200. The intermediate actuating gear 14 includes a pinion 141 meshing with the sector gear 13, and a large gear 142 concentrically connected to the pinion 141. The large gear 142 is further meshed with the drive shaft gear 15. The chamber 10 is connected to the front side (or outer side) of the main body 20 of the reversing and power output mechanism 200 to accommodate the gears 13, 14, 15. The swing rod 11 can be reciprocated manually or by mechanical force or physical force.

[0024] The reversing and power output mechanism 200 comprises: a main body 20 for accommodating all the components of the mechanism 200; an input shaft 21 pivotally connected to the main body 20 (the rod end of the input shaft 21 is connected to the drive shaft gear 15 of the reciprocating actuator 100 and is pivotally connected to the chamber 10); an input gear 22 fixedly connected to the input shaft 21; an intermediate gear 23 rotatably sleeved on a middle shaft 230, the middle shaft 230 is pivotally connected to the middle part of the main body 20; a bidirectional driving gear 24 meshing with the intermediate gear 23; The two-way driving gear 23 is rotatably sleeved on a transmission shaft 21a; the two-way driving gear 24 includes a plurality of forward-rotating ratchet teeth 241 disposed on a first wheel surface (or front wheel surface) 242 of the two-way driving gear 24, and a plurality of reverse-rotating ratchet teeth 243 disposed on a second wheel surface (or rear wheel surface) 244 of the two-way driving gear 24; a forward-rotating clutch 25 is slidably engaged on the transmission shaft 21a, and includes a plurality of forward-rotating ratchet wheels 251 disposed on a rear wheel surface 252 of the forward-rotating clutch 25, which can always match the two-way driving gear 24. The plurality of forward-rotating ratchet teeth 241 on the first wheel surface 242 of the gear 24 are used to drive the bidirectional driving gear 24 in the forward rotation F; a front gear 26 is fixedly connected to the transmission shaft 21a and can axially slide with the forward-rotating clutch 25 to rotate the transmission shaft 21a in the forward direction, and mesh with an output gear 21c fixed on an output shaft 21b to output kinetic energy; a reverse clutch 27 is rotatably sleeved on the transmission shaft 21a, and contains a plurality of reverse-rotating ratchet teeth 271 annularly arranged on the front wheel surface 272 of the reverse clutch 27 to rotate in the reverse direction. When the two-way driving gear 24 is reversed R, the two-way driving gear 24 is matched with the multiple reverse ratchet teeth 243 on the second wheel surface 244 of the two-way driving gear 24, so that the two-way driving gear 24 is reversed R driven; and a reverse gear train 28 is meshed with the reverse clutch 27 and a rear gear 29 fixed to the rear end of the transmission shaft 21a, so that when the two-way driving gear 24 is reversed R, the rear gear 29 is also forwardly rotated F through the reverse gear train 28, so as to forwardly rotate the transmission shaft 21a, and the front gear 26 outputs kinetic energy in the forward direction. The transmission shaft 21a and the output shaft 21b are respectively pivoted in the main body 20.

[0025] There is a tension spring 250 between the front gear 26 and the forward clutch 25 to elastically push the forward clutch 25 to normally engage the bidirectional driving gear 24 and be driven by the bidirectional driving gear 24 in the forward direction. Figure 1 shown.

[0026] There is a tension spring 270 between the rear gear 29 and the reverse clutch 27 to elastically push the reverse clutch 27 to push the reverse clutch 27 toward the second wheel surface 244 of the two-way driving gear 24, so that the two-way driving gear 24 can be reversely driven by R.

[0027] The reverse gear train 28 includes a first gear 281 meshed with the reverse clutch 27 and fixed to the middle shaft 230, a second gear 282 located behind the first gear 281 and also fixed to the middle shaft 230, and a third gear 283 meshed between the second gear 282 and the rear gear 29, converting the reverse direction R of the reverse clutch 27 into the forward direction F of the rear gear 29 and the transmission shaft 21a.

[0028] The intermediate gear 23 actually includes a small gear 231 meshing with the input gear 22 and a large gear 232 coaxially fixed to the small gear 231 and meshing with the bidirectional driving gear 24 to accelerate the rotation speed of the gear.

[0029] The output shaft 21b can be connected to any rotary machine or device to output kinetic energy in a positive direction, that is, to convert the reciprocating input kinetic energy into a single-direction positive direction (non-reciprocating positive and negative direction) rotational output power.

[0030] Each of the plurality of positive rotation ratchet teeth 241 provided on the first wheel surface 242 of the bidirectional driving gear 24 is as shown in FIG. Figure 3 As shown, it is protruded on the first wheel surface 242, and at least one first inclined surface 241s is formed from the first tooth ridge 241r toward the first wheel surface 242 to intersect with the positive rotation direction F to form a first acute angle 241a; and each reversing ratchet tooth 243 of the multiple reversing ratchet teeth 243 provided on the second wheel surface 244 is protruded on the second wheel surface 244, and at least one second inclined surface 243s is formed from the second tooth ridge 243r toward the second wheel surface 244 to intersect with the reversing reverse direction R to form a second acute angle 243a.

[0031] Each of the plurality of forward-rotating ratchet teeth 251 provided on the rear wheel surface 252 of the forward-rotating clutch 25 is protruded from the rear wheel surface 252 of the forward-rotating clutch 25, and at least one third inclined surface 251s is formed from the third tooth ridge 251r toward the rear wheel surface 252 to intersect with the forward-rotating direction F to form a first obtuse angle 251a. Therefore, when the bidirectional driving gear 24 is rotated forward F, the forward-rotating ratchet teeth 241 of the bidirectional driving gear 24 are engaged with the forward-rotating ratchet teeth 251 on the rear wheel surface 252 of the forward-rotating clutch 25, and the forward-rotating clutch 25 is rotated together. Figure 1 shown.

[0032] Each of the multiple reverse ratchet teeth 271 provided on the front wheel surface 272 of the reverse clutch 27 is protruded on the front wheel surface 272 of the reverse clutch 27, and at least one fourth inclined surface 271s is formed from the fourth tooth ridge 271r toward the front wheel surface 272 to intersect with the reverse direction R to form a third obtuse angle 271a. Therefore, when the two-way driving gear 24 is reversed, the reverse ratchet teeth 271 of the reverse clutch 27 are meshed by the reverse ratchet teeth 243 of the two-way driving gear 24, and the reverse clutch 27 is linked to present a reverse R, as shown in FIG. Fig. 9 shown.

[0033] like Figure 4 , 5, 6 and 7, the forward clutch 25 is radially provided with two protruding keys 253 between the shaft hole 254 and the clutch 25 rim, and the two protruding keys 253 extend forward to slide in a pair of grooves 262 recessed by the flanges 261 on both sides of the shaft hole 260 of the front gear 26. Therefore, when the two-way driving gear 24 and the forward clutch 25 are rotated forward, the protruding keys 253 of the forward clutch 25 slide in the grooves 262 of the front gear 26, and the forward clutch 25 is linked to drive the front gear 26 and the fixed transmission shaft 21a, and the rotational power in the forward direction is output by the meshed output gear 21c and the fixed output shaft 21b.

[0034] The bidirectional driving gear 24 and the reverse clutch 27 can be rotatably sleeved or slidably engaged with the transmission shaft 21a. When the bidirectional driving gear 24 is in forward rotation F, the reverse ratchet 243 on the rear wheel surface 244 of the driving gear 24 will obliquely push the reverse ratchet 271 on the reverse clutch 27 so that the two ratchet teeth 243, 271 are separated from each other (such as Figure 1 As shown in FIG. 2 , since the reverse clutch 27 is only rotatably mounted on the transmission shaft 21 a, it will not be linked or affected by the forward rotation of the shaft 21 a.

[0035] When the present invention is used, the deflection swing rod 11 is downward ( Figure 2 The bevel gear 130 meshes with the intermediate actuating gear 14, causing the drive shaft gear 15 to rotate in the forward direction F, and at the same time drives the input shaft 21 to rotate in the forward direction F. The input gear 22 fixed to the input shaft 21 rotates in the forward direction F synchronously, and the acceleration gear 23 meshes with the bidirectional driving gear 24 to rotate in the forward direction F. Through the meshing of the two ratchet teeth 241 and 251, the forward clutch 25 rotates in the forward direction F, and the sliding coupling front gear 26 is also driven to rotate in the forward direction F, and the forward rotation power is output by the output shaft 21b.

[0036] When the swing rod 11 is deflected upward U, the sector gear 13 meshes with the intermediate actuating gear 14 and the drive shaft gear 15 in the reverse R direction, and reverses the input shaft 21 and the input gear 22 in the reverse R direction, and meshes the bidirectional driving gear 24 through the acceleration gear 23. At this time, the ratchet 243 engages with the ratchet 271 to drive the reverse clutch 27 in the reverse R direction, and the forward clutch 25 is pushed open (the ratchet 241 is pushed obliquely and the ratchet 251 is separated). The reverse clutch 27 meshes with the rear gear 29 through the reverse gear train 28 to make it rotate forward F, which is the forward rotation of the The transmission shaft 21a fixed to the rear gear 29 outputs the rotational power in the forward rotation F, so no matter whether the swing arm 11 swings downward or upward, the input gear 22 will rotate forward or reverse, but through the mechanism of the two-way drive gear 24, the forward clutch 25, and the reverse clutch 27, the transmission shaft 21a rotates forward F, that is, no matter the direction of forward rotation or reverse rotation, it rotates in the forward direction, that is, even if the swing arm swings upward U and the input shaft 21 reverses, the output shaft 21b can also output in the forward direction, so that the rotational kinetic energy can be continuously output in the forward direction without interruption, and the energy is fully utilized.

[0037] When the reverse clutch 27 is reversed R, the first gear 281 of the reverse gear train 28 is meshed to make it rotate forward, and the second gear 282 at the rear also rotates forward synchronously, and then the third gear 283 is reversed, and finally the rear gear 29 and the transmission shaft 21a are rotated forward F to make the output rotate forward.

[0038] The output shaft 21b of the present invention is not limited to the rotary machine or kinetic energy output device or energy conversion device connected thereto. The input reciprocating actuator 100 can also be connected to various reciprocating or swing input devices or systems, and the present invention is not limited thereto.

[0039] The inclined surfaces 241s, 243s, 251s, 271s of each ratchet tooth 241, 243, 251, 271 may be two inclined surfaces; the degree of the acute angle or obtuse angle between each inclined surface and each wheel surface 242, 244, 252, 272 is also not limited.

[0040] The present invention is superior to the prior art in that:

[0041] 1. The gear system of the present invention can be used to produce a compact transmission system that does not occupy a large space.

[0042] 2. During the input and output process, the friction loss is minimized, which can increase the kinetic energy output efficiency.

[0043] 3. The system components are not complicated, which can reduce the production cost, increase the convenience of operation, and reduce the trouble and difficulty of maintenance.

[0044] The above-described embodiments are only preferred embodiments for fully illustrating the present invention, and the protection scope of the present invention is not limited thereto. Equivalent substitutions or changes made by those skilled in the art based on the present invention are within the protection scope of the present invention. The protection scope of the present invention shall be subject to the claims.

Claims

1. A transmission system for converting reciprocating motion into forward power output, characterized in that: include: A reciprocating actuator (100), and a reversing and power output mechanism (200); The reversing and power output mechanism (200) comprises: an input gear (22) fixedly connected to an input shaft (21) so that the reciprocating actuator (100) rotates forward or reversely during reciprocating motion; a bidirectional driving gear (24) meshing with the input gear (22) through an intermediate gear (23), and the bidirectional driving gear (24) is rotatably sleeved on a transmission shaft (21a); ​​the bidirectional driving gear (24) comprises a plurality of forward-rotating ratchet teeth (241) arranged on a first wheel surface (242) or a front wheel surface of the bidirectional driving gear (24), and a plurality of reverse-rotating ratchet teeth (243) arranged on a second wheel surface (244) or a rear wheel surface of the bidirectional driving gear (24). A forward clutch (25) is slidably engaged with the transmission shaft (21a), and includes a plurality of forward ratchet teeth (251) annularly arranged on the rear wheel surface (252) of the forward clutch (25) and capable of always matching the plurality of forward ratchet teeth (241) on the first wheel surface (242) of the bidirectional driving gear (24), and when the bidirectional driving gear (24) rotates forward (F), the bidirectional driving gear (24) drives the forward driving gear (24) to rotate forward; a front gear (26) is fixedly connected to the transmission shaft (21a) and capable of axially slidably engaging with the forward clutch (25), and a tension spring (250) is provided between the front gear (26) and the forward clutch (25) to elastically push the forward clutch (25) ) is constantly meshed with the bidirectional driving gear (24), when the forward clutch (25) rotates forward, the front gear (26) also rotates forward and rotates the transmission shaft (21a) forward, the front gear (26) meshes with an output gear (21c) fixed on an output shaft (21b) to output kinetic energy in the forward direction; a reverse clutch (27) is rotatably sleeved on the transmission shaft (21a), comprising a plurality of reverse ratchet teeth (271) annularly arranged on a front wheel surface (272) of the reverse clutch (27) and capable of matching the plurality of reverse ratchet teeth (243) on a second wheel surface (244) of the bidirectional driving gear (24) when the bidirectional driving gear (24) is reversed (R), The bidirectional driving gear (24) is driven to rotate in reverse (R); and a reverse gear train (28) is meshed between the reverse clutch (27) and a rear gear (29) fixed to the rear end of the transmission shaft (21a). A tension spring (270) is provided between the rear gear (29) and the reverse clutch (27) to elastically push the reverse clutch (27) to push the reverse clutch (27) toward the second wheel surface (244). When the bidirectional driving gear (24) rotates in reverse (R), the reverse gear train (28) causes the rear gear (29) to rotate forward (F), thereby rotating the transmission shaft (21a) and the front gear (26) in the forward direction to output kinetic energy.

2. The transmission system for converting reciprocating motion into forward power output as claimed in claim 1, characterized in that: Each of the plurality of forward-rotating ratchet teeth (241) provided on the first wheel surface (242) of the bidirectional driving gear (24) is protrudingly provided on the first wheel surface (242), and forms at least one first inclined surface (241s) from the first tooth ridge (241r) toward the first wheel surface (242), and intersects a first acute angle (241a) with the forward rotation direction (F); and each of the plurality of reverse-rotating ratchet teeth (243) provided on the second wheel surface (244) is protrudingly provided on the second wheel surface (244), and forms at least one second inclined surface (243s) from the second tooth ridge (243r) toward the second wheel surface (244), and intersects a second acute angle (243a) with the reverse rotation direction (R).

3. The transmission system for converting reciprocating motion into forward power output as claimed in claim 1, characterized in that: Each of the plurality of forward-rotating ratchet teeth (251) provided on the rear wheel surface (252) of the forward-rotating clutch (25) is provided on the rear wheel surface (252) of the forward-rotating clutch (25), and at least one third inclined surface (251s) is formed from a third tooth ridge (251r) toward the rear wheel surface (252) and intersects a first obtuse angle (251a) with the forward-rotating direction (F), so that when the bidirectional driving gear (24) is rotated forward (F), the forward-rotating ratchet teeth (241) of the bidirectional driving gear (24) mesh with the forward-rotating ratchet teeth (251) on the rear wheel surface (252) of the forward-rotating clutch (25), and the forward-rotating clutch (25) is rotated together.

4. The transmission system for converting reciprocating motion into forward power output as claimed in claim 1, characterized in that: Each of the multiple reverse ratchet teeth (271) provided on the front wheel surface (272) of the reverse clutch (27) is protrudingly provided on the front wheel surface (272) of the reverse clutch (27), and at least one fourth inclined surface (271s) is formed from a fourth tooth ridge (271r) toward the front wheel surface (272) and intersects a third obtuse angle (271a) with the reverse direction (R), so that when the bidirectional driving gear (24) is reversed, the reverse ratchet teeth (271) of the reverse clutch (27) are meshed with the reverse ratchet teeth (243) of the bidirectional driving gear (24), and the linked reverse clutch (27) presents a reverse rotation (R).

5. The transmission system for converting reciprocating motion into forward power output as claimed in claim 1, characterized in that: The forward clutch (25) is radially provided with two protruding keys (253) between the shaft hole (254) and the clutch (25) wheel rim. The two protruding keys (253) extend forward to slide in a pair of grooves (262) recessed in the flanges (261) on both sides of the shaft hole (260) of the front gear (26). When the bidirectional driving gear (24) and the forward clutch (25) are rotated forward, the protruding keys (253) of the forward clutch (25) slide in the grooves (262) of the front gear (26), so that the forward clutch (25) is linked to drive the front gear (26) and the transmission shaft (21a) fixed thereto, and the rotational power in the forward direction is outputted through the meshed output gear (21c) and the output shaft (21b) fixed thereto.

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