JP2010031809A - Generator driving device for driving generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a miniaturized generator driving device for driving a generator capable of developing high output and capable of exhibiting excellent power generation efficiency. <P>SOLUTION: The generator driving device is provided with two weights; a traction member connected to the two weights respectively; two endless conveying means having a driving end rotated by driving force from a driving source, a driven end to the driving end, and an endless moving member laid between the driving end and the driven end so as to be reciprocated; a weight lifting means connected to the endless moving member and lifting the two weights by imparting tensile strength to the traction member; a driving force transmitting mechanism for transmitting the driving force from the driving source to the driving end so that the two weights are alternately lifted and lowered by the weight lifting means; and an output side shaft connected to an input part of the generator and the two driven ends in order to drive the generator and rotatably supported. The driving force transmitting mechanism is provided with an intermittent transmitting member for connecting the driving force transmission mechanism to the driving end when lifting the weight and releasing connection of the driving force transmitting mechanism to the driving end when the weight is lowered. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention mainly relates to a generator driving device for driving a generator.

  Conventionally, a generator has been used as a power source when normal power supply cannot be received during outdoor construction, leisure, or emergency. Moreover, even in a factory, the rated input may differ depending on the device or apparatus to be operated, and a generator corresponding to the rated input may be used.

There are various types of generators, and the most commonly used is an engine generator that generates power using an internal combustion engine. Various proposals have been made to increase the output performance and power generation efficiency of a generator drive device used in an engine generator (for example, Patent Documents 1, 2, and 3).

JP 2003-97284 A JP 2004-60567 A JP 2007-205266 A

As described above, although there are various conventional generator driving devices, a generator that is small and has high power generation efficiency that can obtain a large output due to the recent increase in interest in environmental conservation and rising fuel costs. There is an increasing desire for a generator drive for driving the vehicle.

Accordingly, an object of the present invention is to provide a generator driving device for driving a generator that is small in size and has high power generation efficiency and high power generation efficiency.

A first aspect of a generator driving apparatus for driving a generator according to the present invention for solving the above-described problems includes two weights, a traction member connected to each of the two weights, and a drive source. Two endless conveying means having a driving end that rotates by a driving force, a driven end relative to the driving end, and an endless moving member that spans between the driving end and the driven end and reciprocates; and the endless A weight lifting means connected to the moving member and lifting the two weights by applying a tensile force to the pulling member, and the two weights from the drive source so that the two weights are alternately raised and lowered by the weight lifting means. A driving force transmission mechanism for transmitting a driving force to the driving end; an output side shaft coupled to the input portion of the generator and the two driven ends for driving the generator and rotatably supported; The driving force transmission The structure includes an intermittent transmission member that connects the driving force transmission mechanism to the driving end when the weight is raised, and releases the connection of the driving force transmission mechanism to the driving end when the weight is lowered. Features.

According to the second aspect of the generator driving device for driving the generator of the present invention, the intermittent transmission member is a rotatable notch gear provided with a gear portion at a part of the outer peripheral portion. It is characterized by that.

  Moreover, according to the 3rd aspect of the generator drive device for driving the generator of this invention, two said drive force transmission mechanisms are provided corresponding to each of the two drive ends of the said two endless conveyance means. The rotational phases of the two notch gears are different from each other.

  Furthermore, according to the fourth aspect of the generator driving apparatus for driving the generator of the present invention, the weight raising means is supported between one end and the other end, and the traction is provided on the one end. It has two oscillating arms to which the weight is connected through a member, and the other ends of the two oscillating arms are alternately pushed down by utilizing this action.

  Further, according to the fifth aspect of the generator driving apparatus for driving the generator of the present invention, the support point for supporting the two swing arms is from the length to the one end to the other end. Is characterized by a short length.

  According to the present invention, since the driving force transmission mechanism has an intermittent transmission member, the drive transmission mechanism is connected to the driving end only when the weight is raised by the weight lifting means, and when the weight falls, The connection between the drive force transmission mechanism and the drive end is released, and mechanical loss due to friction or the like in the drive transmission mechanism can be suppressed.

Therefore, the energy generated when the weight falls can be efficiently used as the energy for raising the other weight. As a result, it is possible to provide a generator drive device for driving a generator with high power generation efficiency that can obtain a large output even if it is small.

(Example)
A generator driving apparatus for driving a generator according to an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a plan view illustrating a schematic structure of a generator driving device 101 according to the embodiment, FIG. 2 is a front view illustrating a schematic structure of the generator driving device 101 according to the embodiment, and FIG. FIG. 4 is a diagram showing a part of the driving force transmission mechanism as seen from the direction of arrow III in FIG. 1, and FIG. 4 is a partial cross-sectional view along line IV-IV in FIG. 3. In FIG. 1, a part of the configuration is shown separately. In FIG. 2, the second swing arm 211, the moving pin 167, and the weight lifting chain 207 are indicated by a one-dot chain line in order to clarify the configuration of the generator driving device 101. Show. Further, for clarity of the structure, frames and bearings are omitted from the drawings.

The generator driving device 101 is used to transmit the driving force of the driving motor 109 as a driving source to the generator 103. The generator drive device 101 is rotated mainly by two weights 105 and 205, weight lifting chains (traction members) 107 and 207 each having one end connected to the weights 105 and 205, and a driving force from the drive motor 109. Between a sixth sprocket (gear) 147 that is a driving end, a seventh sprocket 47 that is a driven end with respect to the sixth sprocket 147 (165), and between the sixth sprocket 147 and the seventh sprocket 47 A third chain 151 that is an endless moving member that spans and reciprocates, and is connected to the third chain 151, by applying an external force to each of the weight lifting chains 107 and 207. First and second swinging arms 111 and 211 which are weight lifting means for operating the weights 105 and 205 to be lifted; A driving force transmission mechanism that transmits the driving force from the driving motor 109 to the sixth sprocket 147 so that the two weights 105 and 205 are alternately raised by the two swing arms 111 and 211, and the generator 103. Therefore, the input side shaft 159 is connected to the seventh sprocket 47 and the driven sprocket 48, and the output side shaft 39 that is rotatably supported, and the output side shaft 39 is rotated only in a predetermined direction. And ratchet mechanisms 1 and 2 interposed between the output side shaft 39 and the seventh sprocket 47 and the driven sprocket 48.

The driving force transmission mechanism connects the driving force transmission mechanism to the sixth sprocket 147 when the weights 105 and 205 are raised, and the sixth sprocket 147 (165 of the driving force transmission mechanism when the weights 105 and 205 are lowered. ) Are provided with intermittent transmission members, i.e., notch gears 135 and 235.

The driving force transmission mechanism has a driving force transmission path for transmitting the driving force to the endless transport means for swinging the swing arms 111 and 211 to which the two weights 105 and 205 are coupled, respectively. The configuration for swinging the two weights 105 and 205 is symmetrical as shown in FIG. 1, and the operation is common in many respects. Therefore, the driving force is changed from the motor 109 to the first swing arm 111. The explanation will focus on the route that travels up to.

First, the rotational force of the drive motor 109 is transmitted to the first sprocket 113 connected to the shaft 110 of the drive motor 109. Further, the rotational force is transmitted to the second sprocket 115 via the first chain 117 wound around the first sprocket 113. The second sprocket 115 is fixed to the outer peripheral surface of the branch shaft 119 that is rotatably supported, and the branch shaft 119 rotates integrally with the second sprocket 115.

A third sprocket 121 and a fourth sprocket 123 are fixed to both ends of the branch shaft 119 in the axial direction. Therefore, when the branch shaft 119 rotates, the third and fourth sprockets 121 and 123 rotate. By this branch shaft 119, the rotational force from the drive motor 109 is branched to the first swing arm 111 and the second swing arm 211, respectively.

The rotational force of the third sprocket 121 is transmitted to the fifth sprocket 127 via the second chain 125. The fifth sprocket 127 is fixed to the outer periphery of the first shaft 129 that is rotatably supported. Further, a ratchet member 131 for transmitting the rotation only in one direction is connected to the first shaft 129.

The ratchet member 131 will be described below with reference to FIGS. The ratchet member 131 is disposed on the outer peripheral surface of the ratchet gear 171, the ratchet gear 171 rotatably supported by the first shaft 129, the annular rolling element 177 that is disposed concentrically with the ratchet gear 171, and that can rotate relative to each other. And a stopper 175 fixed to the rolling element 177 that meshes with the notch 173 provided.

Further, an intermittent transmission member, that is, a notch gear 135 is fixed to the rolling element 177 concentrically. A cylindrical portion 181 that protrudes in the axial direction is provided on the outer peripheral edge portion of the rolling element 177 so as to face the outer peripheral surface of the ratchet gear 171. The cylindrical portion 181 has a stopper accommodating portion 179 that extends outward in the radial direction and accommodates the stopper 175 therein.

A spring 183 is attached to one end of the stopper 175 in the stopper accommodating portion 179 and is always urged radially inward of the rolling element 177. A claw portion 185 is provided at the other end of the stopper 175. The claw portion 185 has a tapered shape and is defined by an engagement surface 185a extending in a substantially radial direction in a front view of FIG. 3 and an inclined surface 185b forming an acute angle between the engagement surface 185a.

In addition, the notch 173 that accommodates the claw portion 185 and meshes with the claw portion 185 includes an engagement surface 173a that is continuous with the outer peripheral surface of the ratchet gear 171 and extends substantially in the radial direction in the front view of FIG. An inclined surface 173b that forms an acute angle with 173a and smoothly continues to the outer peripheral surface of the ratchet gear 171 is defined. The angle formed by the engaging surface 173a and the inclined surface 173b is substantially equal to the angle formed between the engaging surface 185a and the inclined surface 185b of the claw portion 185. In this embodiment, one notch 173 is provided in the ratchet gear 171, but it goes without saying that the number, size, and shape can be changed as appropriate.

Therefore, when the claw portion 185 rotates in the direction of the arrow R with respect to the ratchet gear 171, the stopper 175 biased by the spring 183 enters the notch 173 and cuts off the engagement surface 185a of the claw portion 185. The engaging surface 173a of the notch 173 is locked with each other, and the stopper 175 and the ratchet gear 171 are engaged with each other. On the contrary, when the stopper 175 rotates in the direction opposite to the arrow R with respect to the ratchet gear 171, even if the stopper 175 enters the notch 173, the inclined surface 173b and the inclined surface 185b of the claw portion 185 are The stopper 175 and the ratchet gear 171 are not engaged with each other without being locked.

In the above configuration, when the rolling element 177 rotates counterclockwise (in the direction of arrow R in FIG. 3), the rolling element 177 and the ratchet gear 171 rotate integrally. When the rolling element 177 rotates clockwise, the stopper 175 is notched. 173 does not mesh with 173 and the rolling element 177 rotates idly.

Thus, the rotational force from the fifth sprocket 127 is transmitted to the rolling element 177, and when the rotational direction is the arrow R direction, it is transmitted to the notch gear 135 via the ratchet gear 171. When the rolling element 177 rotates in the direction opposite to the arrow R direction, the rolling element 177 rotates idly with respect to the ratchet gear 171, and the rotational force is not transmitted to the notch gear 135.

Here, the notch gear 135 is one in which teeth are engraved on a part of the outer peripheral portion of the gear. As shown in FIG. 3, teeth 135 a are engraved on almost half of the outer periphery of the gear. The region where the teeth 135a are engraved is defined from the relationship such as the gear diameter and the gear ratio. A more detailed configuration will be described in association with swing arms 111 and 211 described later.

Further, a first gear 137 meshing with the notch gear 135 is rotatably supported. A second gear 139 that meshes with the first gear 137 is fixed to one end of the second shaft 145. The first and second gears 137 and 139 are so-called spur gears whose teeth are provided at equal intervals on the outer periphery thereof.

When the notch gear 135 rotates, the first gear 137 meshes with the first gear 137 in the region where the gear portion composed of the plurality of teeth 135a of the notch gear 135 exists, and the rotational force is the second gear 139. Is transmitted to. However, when the first gear 137 reaches the region 135b where the tooth portion 135a of the notch gear 135 is not engraved, the meshing of both is released, and the rotational force is applied to the first gear 137 and the second gear 139. Not transmitted. Thus, the notch gear 135 has a function of intermittently transmitting a rotational force that is a driving force.

As shown in FIGS. 1 and 2, a second gear (spur gear) 139 arranged to engage with the first gear 137 is one end of a second shaft 145 that is rotatably supported. The sixth sprocket 147 is fixed to the other end portion of the second shaft 145. Therefore, the rotational force of the first gear 137 is transmitted to the second gear 139 and the sixth sprocket 147.

A sixth sprocket 147 is fixed to the other end of the second shaft 145. Further, a seventh sprocket 47 is rotatably arranged so that the sixth sprocket 147 and its rotation axis are parallel to each other, and a third chain 151 is wound around the sixth and seventh sprockets 147 and 47. ing. The sixth and seventh sprockets 147 and 47 and the third chain 151 constitute endless conveying means, and the rotational force of the sixth sprocket 147 is transmitted to the seventh sprocket 47.

A movement pin 163 to be described later is fixed to the third chain 151. As the third chain 151 rotates, the moving pin 163 reciprocates between the sixth and seventh sprockets 147 and 47. Further, the moving pin 163 is connected to the first swing arm 111. The configuration and operation of the moving pin 163 will be described later.

Note that the sixth sprocket 147 and the seventh sprocket 47 have the same shape and are arranged so that their rotation centers are parallel to each other in the vertical direction. Therefore, in FIG. 147 is hidden behind the seventh sprocket 47 and cannot be seen. However, in order to clearly show the structure, a configuration in which the third chain 151 is cut and the driving force is transmitted from the seventh sprocket 147 to the generator 103 is separately shown below the one-dot chain line.

A known ratchet mechanism 1 that transmits rotational force only in one direction is attached to one end of a rotation shaft (output-side shaft) 39 that rotatably supports the seventh sprocket 47. Accordingly, the rotational force of the seventh sprocket 47 in the predetermined direction (arrow R direction) is transmitted to the rotation shaft 39, but the rotation in the direction opposite to the arrow R direction is not transmitted to the rotation shaft 39.

Similarly, the other end portion of the rotary shaft 39 is mounted with the driven sprocket 48 that is linked to the drive sprocket 165 and is linked to the drive sprocket 165, which cooperates with the second swing arm 211. Has been. The ratchet mechanism 2 and the driven sprocket 48 are the same in shape and operation as the ratchet mechanism 1 and the seventh sprocket 47 only in directions. That is, the rotational force in the direction of arrow R of the seventh sprocket 47 and the driven sprocket 48 is transmitted to the rotary shaft 39.

An eighth sprocket 153 is fixed substantially at the center of the rotating shaft 39. The rotational force of the eighth sprocket 153 is transmitted to the ninth sprocket 155 via the fourth chain 157. Since the ninth sprocket 155 is fixed to the shaft (input part) 159 of the generator 103, the rotational force is transmitted to the generator 103.

With reference to FIG. 2, the 1st rocking | fluctuation arm 111 and the 2nd rocking | fluctuation arm 211 with which the weights 105 and 205 are connected via the weight raising / lowering chains 107 and 207 are demonstrated. Although the first and second swing arms 111 and 211 and related members are arranged differently, as shown in FIG. 1, they are symmetrically configured and the operations are the same. Only the first swing arm 111 will be described.

The first swing arm 111 is a bar member having a predetermined length. A through-hole extending in a substantially rectangular shape along the longitudinal direction, that is, a pin hole 161 is provided in the other end 111b facing the one end 111a to which the weight lifting chain 107 is connected. The first swing arm 111 is supported so as to be rotatable about a portion near the other end 111b as a fulcrum p (center). By positioning the fulcrum p in this way, this action can be used to lift the weights 105 and 205.

A moving pin 163 fixed to the third chain 151 is slidably mounted in the pin hole 161. Therefore, when the third chain 151 moves in the arrow S direction, the first swing arm 111 also reciprocates between the sixth sprocket 147 and the seventh sprocket 47.

When the moving pin 163 moves, the first swing arm 111 is connected to the third chain 151 via the moving pin 163 and thus moves in the vertical direction in FIG. When the other end 111b of the first swing arm 111 is in the vicinity of the seventh sprocket 47, the weight 105 is lowered, and when the other end 111b is in the vicinity of the sixth sprocket 147, the weight 105 is raised. It becomes.

As shown in FIG. 1, a notch gear 235 is also disposed in the driving force transmission path related to the second swing arm 211 in the same manner as the driving force transmission path related to the first swing arm 111. Here, in the present embodiment, the notch gear 135 and the notch gear 235 are arranged with different rotational phases, and the timing at which the former and the latter mesh with the first gears 137 and 237 is shifted. Yes.

Specifically, with respect to the traveling direction of the third chain 151 (arrow S direction), the position where the moving pin 163 slightly exceeds the sixth sprocket 147 (the uppermost point) (the moving pin 163 is shown in FIG. 2). The number of teeth necessary to move from a position where the moving pin 167 is slightly over to the position slightly beyond the seventh sprocket 47 (the lowest point) (the position corresponding to the position where the moving pin 167 is shown in FIG. 2). Thus, teeth 135a are engraved on a part of the outer periphery of the notch gear 135, and teeth are similarly engraved on the other notch gear 235.

If the rotation phases of one notch gear 135 and the other notch gear 235 are arranged to be different from each other by 180 degrees, for example, the rotational force of the branch shaft 119 is applied to the notch gears 135 and 235 at the same timing. Even if transmitted, the rotational force is transmitted to the first gears 137 and 237 at different timings. Therefore, when one weight 105 is at the uppermost point (lowermost point), the other weight 205 is at the lowermost point (uppermost point).

That is, in a simple configuration in which the notch gear is applied to the driving force transmission path, it is possible to set the timing for driving the swing arm 111 and the timing for driving the other swing arm 211, respectively.

Further, since the notch gears 135 and 235 are provided, a transmission path to the sixth sprocket 147 (165) is formed only when the weights 105 and 205 are raised by the swing arms 111 and 211, and the weight 105 , 205 falls, the driving force transmission path is physically separated from the sixth sprocket 147 (165), and mechanical loss due to friction or the like in the driving force transmission path can be suppressed.

Therefore, for example, the energy generated when one weight 105 falls can be efficiently used as the energy for raising the other weight 205. As a result, the generator driving device 101 for driving the generator with high power generation efficiency can be realized.

In this embodiment, the moving pins 163 and 167 are located at positions where the moving pin 163 slightly exceeds the sixth sprocket 147 with respect to the traveling direction of the third chain 151 (the moving pin 163 is shown in FIG. 2). Position) and a position slightly beyond the seventh sprocket 47. Even if the rotational force from the notch gear 135 is not transmitted, the moving pin 163 faces in the direction opposite to the arrow S direction. , 167 is set so that the weights 105 and 205 are not moved. Since the weight lifting chain 107 (207) is connected to the weight 105 (205) at one end thereof, the two rotatable rollers 185 and 187 (285 and 287) are connected as long as the weight does not contact the ground. It is the structure supported in the state with tension applied.

  In the above embodiment, the rotational force between the sprockets is transmitted by the chain. However, it goes without saying that a belt may be used.

  The present invention can be embodied in many forms without departing from its essential characteristics. Therefore, it is needless to say that the above-described embodiment is exclusively for description and does not limit the present invention.

It is a top view which shows schematic structure of the generator drive device which concerns on an Example. It is a front view which shows schematic structure of the generator drive device which concerns on an Example. It is a figure which shows a part of driving force transmission mechanism seen from the arrow III direction of FIG. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 3.

Explanation of symbols

39 Output side shaft 47 7th sprocket (driven end)
101 generator driving device 103 generator 105, 205 weight 107, 207 weight lifting chain (traction member)
109 Drive motor 111, 211 Swing arm (weight lifting means)
147, 165 Sixth sprocket (drive end)
151 Third chain (endless moving member)
167 Moving pin 173 Notch gear

Claims (5)

A generator driving device for driving a generator,
Two weights,
A traction member coupled to each of the two weights;
Two endless conveying means having a driving end that rotates by a driving force from a driving source, a driven end with respect to the driving end, and an endless moving member that spans between the driving end and the driven end and reciprocates. When,
A weight raising means connected to the endless moving member and raising the two weights by applying a tensile force to the pulling member;
A driving force transmission mechanism for transmitting a driving force from the driving source to the driving end so that the two weights are alternately raised and lowered by the weight raising means;
An output side shaft connected to the input part of the generator and the two driven ends for driving the generator, and rotatably supported;
The driving force transmission mechanism connects the driving force transmission mechanism to the driving end when the weight is raised, and an intermittent transmission member that releases the connection of the driving force transmission mechanism to the driving end when the weight is lowered. A generator driving apparatus for driving a generator. The generator driving device for driving a generator according to claim 1, wherein the intermittent transmission member is a rotatable notch gear having a gear portion provided at a part of an outer peripheral portion thereof. 3. The power generation according to claim 2, wherein two driving force transmission mechanisms are provided corresponding to two driving ends of the two endless conveying means, and the rotational phases of the two notch gears are different from each other. Generator driving device for driving the machine. The weight raising means has two swing arms that are supported between one end and the other end and to which the weight is connected to the one end via the pulling member. The generator driving device for driving a generator according to any one of claims 1 to 3, wherein the other end of the arm is alternately pushed down by utilizing this action. 5. The generator for driving a generator according to claim 4, wherein a support point for supporting the two swing arms has a length to the other end shorter than a length to the one end. 6. Drive device.

Images