TWI477702B - Both direction driving device - Google Patents

Description

Two-way transmission mechanism

The present invention relates to a two-way transmission mechanism, and in particular to a two-way transmission mechanism for use in a rotary power transmission system.

In the power transmission system of the conventional power unit, a transmission device capable of realizing forward rotation and reverse rotation is often provided according to different requirements, thereby driving different power systems. However, the current two-way transmission mechanism needs to shift the transmission gear through a fork structure, so that the gear is switched with different power systems to drive the corresponding power system, so that it is necessary to provide a transmission corresponding to the fork structure. The system, and manually driving the fork structure to realize the commutation, makes the structure of the transmission device more complicated, and the operation is cumbersome, and it is inconvenient to work in a power system that requires frequent commutation.

In view of this, it is necessary to provide a two-way transmission mechanism that can realize automatic switching and has a simple structure.

The present invention provides a two-way transmission mechanism that includes a main shaft, a retainer, an isolator ring, a plurality of reversing clutch blocks, two drive gears, and two shaft end caps. The retainer is sleeved on the main shaft, and a plurality of sliding grooves are formed on the retainer in the axial direction of the main shaft to close one end. The spacer ring is fixed in the middle of the cage. The plurality of reversing clutch blocks are respectively slidable Inside the chute of the cage. Each of the reversing clutch blocks includes two driving portions spaced apart from each other, and the two driving portions are respectively provided with the same outer oblique ribs. The two transmission gears are respectively sleeved on the cage and located on two sides of the isolation ring, and the outer side of the two transmission gears are respectively disposed with the outer oblique tooth on the reversing clutch block Corresponding internal helical ridges. The outer sides of the two transmission gears are provided with external ribs for respectively meshing with the peripheral power unit to transmit power. The shaft end caps are respectively fixed at both ends of the cage to restrict the reversing clutch block and the transmission gear to the cage. When the main shaft rotates in one direction, the one of the transmission gears approaches the isolation ring under the driving of one of the driving parts of each of the reversing clutch blocks, and is adjacent to the driving portion after being close to the isolating ring The outer oblique tooth is detached. At the same time, the inner helical tooth of the other transmission gear meshes with the outer oblique tooth of the other driving portion of each of the reversing clutch blocks and is driven away from the other driving portion of each of the reversing clutch blocks. The spacer ring is engaged with the outer bevel of the other drive portion.

Compared with the prior art, the two-way transmission mechanism of the invention cooperates with the cage and the reversing clutch block, thereby realizing automatic switching of the transmission gear during the rotation in different directions, and simplifies the structure, facilitates production, and has low cost. .

100‧‧‧Transmission mechanism

110‧‧‧ Spindle

112‧‧‧ arc slot

120‧‧‧Cage

121‧‧‧Chute

122‧‧‧ hollow cylinder

122a‧‧‧ inner side wall

122b‧‧‧Outer side wall

124‧‧ ‧ baffle

124a‧‧‧Support surface

130‧‧‧Isolation ring

140‧‧‧Reversing clutch

142‧‧‧ Drive Department

142a‧‧‧External slanting

142b‧‧‧arc roller

142c‧‧‧

FIG. 1 is an exploded perspective view of a bidirectional transmission mechanism provided in an embodiment of the present invention.

2 is a perspective view showing the assembled portion of the two-way transmission mechanism of FIG.

Figure 3 is a perspective view of the cage of the two-way transmission of Figure 1.

Figure 4 is a front elevational view showing the state of use of the two-way transmission mechanism of Figure 1.

Figure 5 is a front elevational view of another use state of the two-way transmission mechanism of Figure 1.

Figure 6 is a side elevational view of another use state of the two-way transmission mechanism of Figure 1.

Referring to FIG. 1 to FIG. 3, a bidirectional transmission mechanism 100 according to a preferred embodiment of the present invention is provided. The two-way transmission mechanism 100 includes a main shaft 110, a retainer 120, an isolator ring 130, a plurality of reversing clutch blocks 140, two transmission gears 150, and two shaft end caps 160. The retainer 120 is sleeved on the main shaft 110, and a plurality of sliding slots 121 are formed on the retainer 120 along the axial direction of the main shaft 110 to close one end. The spacer ring 130 is sleeved in the middle of the holder 120 and is fixed to the holder 120. The plurality of reversing clutch blocks 140 are respectively slidably inserted in the sliding slot 121 of the holder 120. Each of the reversing clutch blocks 140 includes two driving portions 142 spaced apart from each other. The two driving portions 142 are respectively provided with the same outer slanting rib 142a. The two transmission gears 150 are sleeved on the cage 120 and are spaced apart by the spacer ring 130. The inner sides of the two transmission gears 150 are respectively provided with inner helical ribs 152 corresponding to the outer slanting ribs 142a on the reversing clutch block 140. External ribs 154 are disposed on the outer sides of the two transmission gears 150 for respectively meshing with peripheral power units (not shown) to transmit power. The shaft end caps 160 are respectively fixed at both ends of the retainer 120 to restrict the reversing clutch block 140 and the transmission gear 150 to the retainer 120. When the main shaft 110 rotates in one direction, the one transmission gear 150 approaches the isolation ring 130 under the driving of one of the driving portions 142 of the reversing clutch 140, and is adjacent to the isolation ring 130 and the driving portion 142. The outer helical tooth 142a is disengaged while the other drive gear 150 is driven away from the spacer ring 130 by the other drive portion 142 of the reverse clutch 140 and meshes with the outer helical tooth 142a of the other drive portion 142.

The main shaft 110 is connected to a power source such as a motor for rotating under the driving of a power source. A plurality of concave arcuate grooves 112 are formed on the outer side walls of the main shaft 110 at equal intervals, and the arcuate grooves 112 are for receiving the reversing clutch block 140.

The cage 120 includes a hollow cylinder 122. The inner diameter of the hollow cylinder 122 is slightly larger than the diameter of the main shaft 110. The hollow cylinder 122 includes an inner sidewall 122a and an outer sidewall 122b. The sliding slots 121 are evenly spaced on the hollow cylinder 122 and penetrate the inner side wall 122a and the outer side wall 122b of the hollow cylinder 122. A baffle 124 extends in an axial direction of the hollow cylinder 122 at a side of the opening of each of the chutes 121 adjacent to the outer side wall 122b. The baffle 124 includes a support surface 124a facing the inner side of the hollow cylinder 122, and the support surface 124a is convexly curved toward the inner side of the hollow cylinder 122. In this embodiment, the hollow cylinder 122 is disposed at a position corresponding to each of the baffles 124 to be a curved surface matching the support surface 124a.

The spacer ring 130 surrounds the middle of the outer side wall 122b of the hollow cylinder 122 of the holder 120 and is fixed to the hollow cylinder 122 by bolts.

The two driving portions 142 of each of the reversing clutch blocks 140 are similar in structure, and each includes an arcuate roller 142b and a pendulum plate 142c formed on the arcuate roller 142b. In this embodiment, the arcuate rollers 142b of the two driving portions 142 of each of the reversing clutch blocks 140 are connected to each other. The pendulum plates 142c are each curved in an arc curved toward the curved roller 142b. The outer helical ribs 142a are respectively formed at one ends of the two sliding plates 142c of the two driving portions 142 opposite to each other, that is, the outer helical ribs 142a are respectively formed integrally after the curved rollers 142b are connected On both sides. The two yaw plates 142c of the reversing clutch block 140 are respectively disposed in the sliding slots 121 of the retainer 120, and the outer slanting ribs 142a on the two oscillating plates 142c are respectively located at the two dampers 124 side. The arcuate rollers 142b of each of the reversing clutch blocks 140 are seated in the arcuate slots 112 outside the main shaft 110.

The transmission gears 150 are respectively sleeved on the cage 120 and pass through the inner side thereof. The inner helical rib 152 engages with the reversing clutch 140 that is seated within the retainer 120.

Each of the shaft end caps 160 includes a circular side panel 162 and a flange 164 that surrounds the side panel 162. A central hole 162a penetrating the side plate 162 is inserted through the side plate 162 for the spindle 110 to pass through, and a plurality of bolt holes 162b are spaced apart from the side plate 162 surrounding the center hole 162a for A bolt (not shown) is passed through to secure the shaft end cap 160 to the retainer 120. It can be understood that when the shaft end cover 160 is fixed on the retainer 120, the distance between the flange 164 of the shaft end cover 160 and the spacer ring 130 on the retainer 120 is greater than the transmission gear. 150 is axially thick so that a sufficient distance is formed between the shaft end cap 160 and the spacer ring 130 to ensure that the drive gear 150 is movable along the main shaft 110 to mate with different drive trains.

Referring to FIGS. 4-6, when the two-way transmission mechanism 100 is in use, the two-way transmission mechanism is rotated by the main shaft 110 under an external power source (not shown), and the main shaft 110 drives the card to be placed in the arc groove. The curved roller 142b within 112 rotates. Since the outer side of each of the swinging plates 142c is abutted on the baffle 124, the curved roller 142b will drive the swinging plate 142c to slide a small extent in the sliding slot 121, thereby driving one of the driving plates 142c. The outer slanting rib 142a of the portion 142 is extended by the sliding slot 121 and meshes with the inner helical rib 152 of the corresponding transmission gear 150, so that the driving portion 142 is rotated by the outer helical rib 142a. At the same time, under the axial force of the outer helical tooth 142a, it slides to a position away from the spacer ring 130, and finally abuts against the flange 164 of the shaft end cover 160 and automatically meshes with the load gear to drive the load. Turn. At the same time, the outer helical rib 142a of the other driving portion 142 gradually enters the sliding slot 121 as the corresponding sliding plate 142c slides, and interacts with the inner helical rib 152 of the corresponding transmission gear 150. Disengaged, the outer helical gear of the corresponding driving gear 150 at the other driving portion 142 is in a period of time before the outer helical tooth 142a of the other driving portion 142 is disengaged from the inner helical tooth 152 The axial force of the rib 142a moves toward the approaching spacer ring 130, and resists the spacer ring when the outer helical rib 142a of the other driving portion 142 and the inner helical rib 152 are finally detached. 130. When rotated in the reverse direction, the above motion is achieved in the opposite direction in the same manner.

The two-way transmission mechanism 100 of the present invention cooperates with the cage 120 and the reversing clutch block 140, thereby realizing automatic switching of the transmission gear 150 during the rotation in different directions, at the same time simplifying the structure, facilitating production, and low cost.

In summary, the present invention complies with the requirements of the invention patent and submits a patent application according to law. However, the above description is only the preferred embodiment of the present invention, and the scope of the present invention is not limited to the above-described embodiments, and equivalent modifications or variations made by those skilled in the art in light of the spirit of the present invention are It should be covered by the following patent application.

100‧‧‧Two-way transmission mechanism

110‧‧‧ Spindle

112‧‧‧ arc slot

121‧‧‧Chute

122‧‧‧ hollow cylinder

122a‧‧‧ inner side wall

122b‧‧‧Outer side wall

124‧‧ ‧ baffle

124a‧‧‧Support surface

130‧‧‧Isolation ring

140‧‧‧Reversing clutch

142‧‧‧ Drive Department

142a‧‧‧External slanting

142b‧‧‧arc roller

142c‧‧‧

150‧‧‧Transmission gear

152‧‧‧Internal slanting

154‧‧‧ external tooth

160‧‧‧ shaft end cap

162‧‧‧ side panels

162a‧‧‧Center hole

162b‧‧‧Bolt hole

164‧‧‧Flange

Claims (8)

A two-way transmission mechanism comprising a main shaft, a retaining frame, an isolating ring, a plurality of reversing clutch blocks, two transmission gears, and two shaft end caps, the outer side walls of the main shaft being equally spaced apart a concave arcuate groove, the retainer is sleeved on the main shaft, and a plurality of sliding grooves are formed on the retainer in the axial direction of the main shaft to close one end, the spacer ring Separatingly disposed in a middle portion of the holder, the plurality of reversing clutch blocks are respectively slidably inserted in the sliding groove of the holder, and each of the reversing clutch blocks includes a driving portion spaced apart from each other The two driving portions are respectively disposed with the same outer slanting groove, and each of the driving parts of the reversing clutch includes an arc roller and a swing plate connected to the arc roller The arcuate rollers of the driving portion are respectively clamped in the arcuate slots of the main shaft, the pendulum plate is locked in the sliding slot, and the two transmission gears are respectively sleeved on the cage Located on both sides of the isolation ring and in the two transmission gears The side is respectively provided with an inner slanting rib corresponding to the outer slanting ridge on the reversing clutch block, and outer ribs are arranged on the outer side of the two transmission gears for respectively meshing with the peripheral power device for transmitting Dynamically, the shaft end caps are respectively fixed at both ends of the cage to restrict the reversing clutch block and the transmission gear to the cage, and when the spindle rotates in one direction, the one of the transmissions The gear is driven by the one of the driving portions of each of the reversing clutches to approach the isolating ring, and is detached from the outer bevel on the driving portion after being close to the isolating ring, and at the same time, the inner oblique of the other transmission gear The ribs mesh with the outer slanting ribs of the other driving portion of each of the reversing clutch blocks and are driven away from the spacer ring by the other driving portion of each of the reversing clutch blocks, and the other driving portion The outer slanting teeth are meshed. The two-way transmission mechanism of claim 1, wherein the swinging plate has an arc curved toward the curved roller. The two-way transmission mechanism of claim 2, wherein: the arc rollers of the two driving portions of each of the reversing clutch blocks are connected to each other, and the outer side of each of the reversing clutch blocks The helical ribs are respectively formed at one ends of the oscillating plates of the two driving portions that are diagonal to each other. The two-way transmission mechanism of claim 3, wherein: the cage comprises a hollow cylinder, the hollow cylinder comprises an inner side wall and an outer side wall, and the sliding groove is evenly spaced apart On the hollow cylinder, and extending through the inner side wall and the outer side wall of the hollow cylinder, a side of the end of each of the sliding slot openings adjacent to the outer side wall extends along the axial direction of the hollow cylinder The outer slanting ribs on the two driven oscillating plates of each of the reversing clutch blocks are respectively located on two sides of the baffle. The two-way transmission mechanism of claim 4, wherein: the baffle includes a support surface facing the inner side of the hollow cylinder, and the support surface is convex toward the inner side of the hollow cylinder. . The two-way transmission mechanism of claim 5, wherein: the position of each of the baffles on the hollow cylinder is set to be a curved surface matching the support surface. The two-way transmission mechanism of claim 6, wherein: each of the shaft end covers includes a circular side plate and a flange surrounding the side plate, and a central plate is provided through the side plate at a center position of the side plate a central hole through which the side plate is placed on the main shaft and fixed to the end of the holder. The two-way transmission mechanism of claim 7, wherein: a distance between a flange of the shaft end cover and an isolation ring on the cage is greater than an axial thickness of the transmission gear.