(Mode for carrying out the invention)
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an antistatic vibration suppression apparatus 1000 according to an embodiment of the present invention will be described in detail with reference to the drawings.
[Overall structure of static elimination device]
1 and 2, a perspective view of the antistatic vibration suppression apparatus 1000 shown in Figs. 1 and 2, and a perspective view of the antistatic vibration suppression apparatus 1000 shown in Figs. 3 and 4, with respect to the entire structure of the antistatic vibration suppression apparatus 1000 according to the embodiment of the present invention. A three-sided view of the apparatus 1000 and a functional block diagram of the static eliminator 1000 shown in Fig. The present static eliminator device 1000 is a compact, dry-type static eliminator device having good operability and visibility. However, the present invention is a static eliminator device of a retentive type (nozzle type and bar type, not a dry type) The valve unit 1100 according to the present embodiment may be provided outside the valve unit 1000. [
The perspective view and the three-sided view of the static eliminator apparatus 1000 shown in Figs. 1 to 4 are the same as those of the static eliminator apparatus 1000 except that the outer case covering the entire static eliminator apparatus 1000 is removed It is represented by the sun.
This eliminator / damping apparatus 1000 is an eliminator / damping apparatus that does not require external power supply, and roughly includes a power generator unit 1200 that generates electricity using compressed air supplied from the outside, A discharge unit 1400 for ionizing the air using corona discharge generated by applying the ionized air to the discharge electrode 1430, and a nozzle unit 1300 for jetting air ionized for discharging and destroying. In this antistatic vibration suppression apparatus 1000, compressed air supplied from the outside flows through an air piping 1030 for a duster and first compressed air supplied to a power generation unit 1200 through an air piping 1020 before power generation, And the second compressed air supplied to the nozzle unit 1300 without passing through the unit 1200.
The static eliminator 1000 is characterized in that the first air pipe (the pre-power generation air pipe 1020 and the post-power generation air pipe 1040) through which the first compressed air flows and the second The first air pipe and the second air pipe are branched from the valve unit 1100 on the upstream side of the compressed air rather than the power generation unit 1200, and the air pipe (duster air pipe 1030) The first air pipe and the second air pipe are joined by the nozzle unit 1300 on the downstream side of the compressed air than the first air pipe 1200.
The discharge eliminator 1000 is characterized in that the discharging needle 1430 of the discharging unit 1400 is disposed upstream of the nozzle unit 1300 in which the first air pipe and the second air pipe join, The first compressed air is ionized. It should be noted that the ionization by the discharge needle 1430 of the discharge unit 1400 is not limited to the first compressed air, and at least one of the first compressed air and the second compressed air may be ionized.
It is also characteristic that the fluctuation amount of the first compressed air is smaller than the fluctuation amount of the second compressed air in this antistatic vibration suppression apparatus 1000. It is characteristic that the flow rate of the second compressed air is changed in accordance with the operation amount of the operation unit 1110 by the user. Details of these will be described later.
Hereinafter, the detailed structure (element technology) of the electrostatic discharge neutralizing apparatus 1000 having such characteristics will be described by dividing it into a valve unit 1100, a power generation unit 1200, a nozzle unit 1300 and a discharge unit 1400 Explain.
[Structure of Valve Unit]
Next, the structure of the valve unit 1100 of the antistatic vibration-damping device 1000 will be described with reference to Figs. 1 to 5, a sectional view of the two-way valve 1120 shown in Fig. 6, (1120) will be described with reference to the drawings. As shown in these drawings, the valve unit 1100 roughly comprises a two-port valve 1120 of one input and two outputs and an operating portion 1110 for operating the two port valve 1120 And the operation unit 1110 includes a trigger of a double action (a first trigger 1112 on the outside and a second trigger 1114 on the inside) operated by the user.
The two-way valve 1120 constituting the valve unit 1100 has one input port 1024 and two output ports (a first output port 1026 and a second output port 1028). Further, if the following features are provided, the number of output ports may be three or more.
The two-way valve 1120 includes an input conduit 1124 connected to the input port 1024, a first output conduit 1126 connected to the first output port 1026 and a second output conduit 1126 connected to the second output port 1028 A first valve body 1150 for connecting or disconnecting the input conduit 1124 and the first output conduit 1126 with the user's operation and a second valve body 1150 connected to the first valve body 1150 1150 and the first output line 1126 are changed from the state in which the input line 1124 and the first output line 1126 are shut off to the state in which the input line 1124 and the first output line 1126 are in communication with each other, And a second valve body (1160) for connecting and disconnecting the two output pipe paths (1128).
It is characteristic that the second valve body 1160 of the two-way valve 1120 is configured such that the operation amount by the user's operation and the flow rate in the second output pipe 1128 are substantially proportional to each other, And communicates the input conduit 1124 and the second output conduit 1128 with each other.
The two-way valve 1120 is characterized in that the flow rate of the first output line 1126 is not reduced when the flow rate of the second output line 1128 is increased by the user's operation, And a needle piston 1140 as an adjusting mechanism for increasing the flow rate through the sieve 1150 and suppressing the amount of fluctuation of the flow rate in the first output line 1126. [ Here, as an example in which a phenomenon that the flow rate in the first output line 1126 decreases when the flow rate in the second output line 1128 is increased by the user's operation is assumed, 1126 and the pipe diameter of the second output pipe 1128 are not sufficiently large and the pipe diameter of the input pipe 1124 is not sufficiently large. In order to improve operability and visibility, 1000) is a phenomenon that usually occurs.
It is characteristic that the needle piston 1140 as an adjusting mechanism in the two-way valve 1120 is connected to the first output tube (not shown) through the first valve body 1150 in conjunction with the pressure fluctuation in the input tube 1124 (1126).
Details of the valve unit 1100 having these features will be described below.
The operation unit 1110 of the valve unit 1100 is constituted by a double action trigger (an outer first trigger 1112 and an inner second trigger 1114) The first valve body 1150 of the valve 1120 changes the state of the input pipe 1124 and the first output pipe 1126 from the closed state to the communicated state. Further, by pulling the second trigger 1114 together with the first trigger 1112 (at this time, the first trigger 1112 and the second trigger 1114 are overlapped and integrated), the second valve 1120 The valve body 1160 is changed from a state in which the input line 1124 and the second output line 1128 are shut off to a state in which the flow rate linked to the operation amount by the operation of the user flows.
Since the first trigger 1112 and the second trigger 1114 are overlapped and integrated at this time, the second trigger 1114 is returned together with the first trigger 1112 by reversing the second trigger 1114 And the second valve body 1160 of the two-way valve 1120 switches the state of the input line 1124 and the second output line 1128 from the communicated state to the blocked state, The first valve body 1150 of the two-way valve 1120 changes the state of the input line 1124 and the first output line 1126 from the communicated state to the disconnected state.
Next, the two-way valve 1120 of the valve unit 1100 will be described.
A predetermined pressure (about 0.1 to 1.2 MPa, preferably about 0.2 to 0.6 MPa) is compressed in the input port 1024 of the two-way valve 1120 from the air hose 1010 connected to the air pipe connection port 1012 Air is supplied. The first output port 1026 is connected to the pre-power generation air line 1020, and the second output port 1028 is connected to the duster air line 1030.
The piping configuration on the first compressed air side is as follows. An input line 1124 connected to the input port 1024 is branched to the first communicating line 1122 on the needle piston 1140 side as an adjusting mechanism on the downstream side of the input port 1024. The input pipeline 1124 branches to the needle piston 1140 on the further downstream side of the input port 1024 and to the second communicating pipeline 1130 on the first valve body 1150 side. The second communicating pipe passage 1130 is connected to a third communicating pipe passage 1132 for receiving the tip end tapered portion 1148 of the needle piston 1140. The third communicating pipe passage 1132 is connected to the first valve body 1150 And a rear end portion 1164 of the second valve body 1160. The first valve body 1160 is connected to the first housing conduit 1134 for housing the front end portion 1152 of the second valve body 1160 and the rear end portion 1164 of the second valve body 1160. When the first valve body 1150 is opened and the compressed air flows from the first accumulating duct 1134 to the first output duct 1126 and the input duct 1124 and the first output duct 1126 are blocked, .
The piping configuration on the second compressed air side is as follows. The input line 1124 connected to the input port 1024 is connected to the second storage line 1135 for storing the neck portion 1165 of the second valve element 1160 on the further downstream side of the second communicating line 1130 Respectively. When the second valve body 1160 is opened, the compressed air flows from the second accumulating duct 1135 to the second output duct 1128, and from the state in which the input duct 1124 and the second output duct 1128 are blocked, .
The first valve element 1150 is constituted by the tip end portion 1152 and the rear end portion 1154 connected by the neck portion 1155 and the side wall 1158 of the rear end portion 1154 and the side wall 1156 of the tip end portion 1152 , The compressed air is not leaked and the inner wall of the two-way valve 1120 is slid so that the first valve body 1150 can move in the left-right direction in Fig. When the first valve element 1150 moves to the right in Fig. 6 as shown in Fig. 7 (a), a clearance is formed between the neck portion 1155 and the inner wall 1170 of the two-way valve 1120 And the first valve body 1150 is opened.
7A, when the first valve body 1150 is in the open state, the compressed air introduced into the input conduit 1124 flows into the second communicating conduit 1130, the third communicating conduit 1132 And the first receiving duct 1134 and flows to the first output duct 1126.
The second valve body 1160 is constituted by the tip portion 1162 and the rear end portion 1164 connected by the neck portion 1165 and the tapered side wall 1166 of the neck portion 1165 does not leak the compressed air, The second valve body 1160 is slidable on the inner wall of the open valve 1120 so as to be movable in the left-right direction in Fig. When the second valve element 1160 moves to the right in Fig. 6 as shown in Fig. 7 (b), the tapered side wall 1166 of the neck portion 1165 and the tapered inner wall 1140 of the two- A gap is formed between the second valve body 1180 and the second valve body 1160 is opened.
7B, when the second valve element 1160 is opened, the compressed air introduced into the input line 1124 passes through the second accumulation line 1135 and flows into the second output line 1135. [ (1128).
The gap between the front end of the first valve body 1150 and the rear end of the second valve body 1160 can be adjusted in a state in which the operating portion 1110 is not operated (i.e., the first valve body 1150 is closed) As shown in the drawing, the distance D is extended by the distance D, and the distance D is set to a distance between the first trigger 1112 and the second trigger 1114 in the double action triggers (the first trigger 1112 and the second trigger 1114) (The first trigger 1112 on the outer side and the second trigger 1114 on the inner side are superimposed on one another) that is pulled by the second trigger 1112 to abut against the second trigger 1114. That is, by pulling the outer first trigger 1112, the first valve body 1150 of the two-way valve 1120 moves in the rightward direction of Fig. 6, and the first outer trigger 1112 is moved The tip end of the first valve body 1150 of the two-way valve 1120 and the rear end of the second valve body 1160 are in contact with each other (distance D = 0).
In addition, by pulling the second trigger 1114 together with the first trigger 1112, the front end of the first valve body 1150 of the two-port valve 1120 and the rear end of the second valve body 1160 are in contact with each other The first valve body 1150 pushes the second valve body 1160 so that the first valve body 1150 and the second valve body 1160 of the two-way valve 1120 move together to the right in FIG. 6 The tapered side wall 1166 of the neck portion 1165 and the tapered side wall 1166 of the two-way valve 1120 move in the rightward direction in Fig. 6 while the first valve body 1150 remains open, A gap is formed between the inner wall 1180 and the second valve body 1160 is opened.
In this case, the tapered sidewall 1166 of the neck portion 1165 and the tapered inner wall 1180 of the two-way valve 1120 in the second valve body 1160 are arranged in the direction The larger the amount of movement in the rightward direction of the tapered sidewall 1166 is, the larger the gap between the tapered sidewall 1166 and the tapered inner wall 1180 becomes. Thus, the flow rate of the compressed air in the second output line 1128 is interlocked The taper of the tapered sidewall 1166 and the tapered inner wall 1180 is configured such that the flow rate of the flow of the compressed air in the second output pipe 1128 is substantially proportional to the flow amount of the flow of the compressed air in the second output pipe 1128, .
If the amount of the second trigger 1114 pulled is large, the flow rate of the compressed air in the second output pipe 1128 is large and the flow rate of the second trigger 1114 is increased The flow amount of the compressed air in the second output tube 1128 is small when the amount of pulling is small), and the present invention is not limited to the one in which the proportional relationship is expressed.
Next, when the second valve body 1160 is in the open state as shown in FIG. 7 (b), when the flow rate in the second output conduit 1128 increases, the flow rate in the first output conduit 1126 decreases A description will be given of the needle piston 1140 as an adjusting mechanism for increasing the flow rate passing through the first valve body 1150 and suppressing the amount of fluctuation of the flow rate in the first output pipe 1126. [
The needle piston 1140 is composed of a body 1142 and a lower end 1144 and a tip tapered portion 1148. The sliding portion 1143 of the body 1142 and the sliding portion 1145 of the lower end 1144, The valve 1120 slides on the inner wall of the two-way valve 1120 (which functions as a cylinder for the needle piston 1140) and moves in the up-and-down direction in Fig. 6 without leaking the compressed air.
The needle piston 1140 is urged by a first spring 1136 and a second spring 1138 to be described later and the needle piston 1140 is moved upward in Fig. In this state, when the gap between the tip end tapered portion 1148 and the third communicating pipe passage 1132 is opened and the first valve element 1150 is in the open state as shown in Fig. 7 (a) The compressed air that has passed through the first output pipe 1126 flows to the first output pipe 1126.
The rear end surface of the lower end portion 1144 receives the pressure of the compressed air in the first communicating pipe passage 1122 and the pressure of the compressed air in the first communicating pipe passage 1122 is lowered, The needle piston 1140 moves downward in Fig. 6 against the push-up force of the needle piston 1140 as shown in Fig. 7 (c).
The distal end tapered portion 1148 of the needle piston 1140 is formed so as to move in the downward direction of the needle piston 1140 on the structure of the third communicating tube path 1132 (this is not a tapered shape) The clearance between the tip tapered portion 1148 and the third communicating pipe 1132 becomes narrower as the gap between the tip tapered portion 1148 and the third communicating pipe 1132 becomes wider and the needle piston 1140 moves upward, Loses.
As described above, the needle piston 1140 is moved downward against the first spring 1136 and the second spring 1138 in response to the pressure drop of the compressed air in the first communicating pipe passage 1122 do. In this case, a pushing force is applied to the needle piston 1140 by the first spring 1136 and the second spring 1138.
The first spring 1136 urges the needle piston 1140 upward to balance the pushing force of the needle piston 1140 by the pressure drop of the compressed air in the first communicating pipe passage 1122 So that the amount of movement of the needle piston 1140 in the vertical direction with respect to the pressure fluctuation of the compressed air in the first communicating pipe passage 1122 is adjusted.
However, the pressure of the compressed air in the first communicating pipe passage 1122 is restored (raised) to the needle 1114 by only generating the force for pushing up the needle piston 1140 by the first spring 1136 alone, The sliding portion 1143 of the body 1142 and the sliding portion 1145 of the lower end 1144 and the inner wall of the two-way valve 1120 (the needle piston 1140) The needle piston 1140 does not move quickly in the upward direction in Fig. That is, when the needle piston 1140 is about to move, the linear characteristic of the first spring 1136 and the fluctuation component of the compressed air can not be maintained by this static friction. Therefore, the second spring 1138 constantly generates a weak force to push up the needle piston 1140, thereby reducing the static friction, and the amount of change in the compressed air and the amount of movement of the needle piston 1140 in the vertical direction The linearity of the linearity is maintained.
Further, the present invention can exhibit the linear characteristic of the variation amount of the compressed air in the first communicating pipe passage 1122 and the movement amount of the needle piston 1140 in the up-down direction, The present invention is not limited to the above-described configuration as long as the amount of fluctuation of the flow rate in the first output line 1126 can be suppressed by increasing or decreasing the flow rate.
The two-way valve 1120 of the valve unit 1100 having such a configuration is configured such that the first valve body 1150 and the second valve body 1160 shown in Fig. 6 are closed, Fig. The first valve body 1150 and the second valve body 1160 shown in Fig. 7 (b) are opened, the first valve body 1150 and the second valve body 1160 are closed, When the first valve body 1150 and the second valve body 1160 shown in Fig. 7 (c) are opened, the pressure of the compressed air in the first communicating pipe passage 1122 is lowered and the needle piston 1140 is lowered The flow rate of the compressed air passing through the needle piston 1140 and the first valve body 1150 increases or the pressure of the compressed air in the first communicating path 1122 is restored (raised), and the needle piston 1140 rises, And a state in which the compressed air flow rate passing through the piston 1140 and the first valve body 1150 is not increased.
The compressed air flowing through the first valve body 1150 and flowing into the first output line 1126 flows through the power generation unit 1200 via the power generation air piping 1020 connected to the first output port 1026, The compressed air flowing through the second valve body 1160 and flowing into the second output line 1128 flows through the duster air piping 1030 connected to the second output port 1028 To the second input hole 1318 of the nozzle unit 1300. [
[Structure of Power Generation Unit]
Next, a structure of the power generation unit 1200 of the static electricity suppressing apparatus 1000 will be described with reference to Figs. 1 to 5, a side view of the power generation unit 1200 shown in Fig. 8, And other rotary blades shown in Figs. 10 to 12 will be described. Fig. As shown in these figures, the power generation unit 1200 roughly includes a rotary blade 1220 housed in a housing case 1210 connected to the pre-power generation air pipe 1020 and the post-power generation air pipe 1040, And a generator 1290 which is a rotary electric machine housed in a generator case 1280. [
The power generation unit 1200 is provided between an input port 1214 through which the compressed air flows, an output port 1218 through which the compressed air flows, an input port 1214 and an output port 1218, A rotary blade 1220 that is housed in the housing case 1210 and rotates by the compressed air to constitute a drag-like windmill, and a rotary blade 1220 that is connected to the rotary shaft of the rotary blade 1220, And a generator. An electric power generation piping 1020 is connected to the input port 1214 and an electric power generation piping 1040 is connected to the output port 1218.
In this housing case 1210,
(1) The compressed air flowing from the input port 1214 side flows through the output port 1218 side by changing the flow direction by about 90 degrees,
(2) The rotating shaft is perpendicular to the flow direction of the compressed air.
The input port 1214 side and the output port 1218 side are connected to each other by the housing case 1210 (more specifically, the housing inner wall 1216 (upper side) of the housing case 1210) and the rotary vane 1220 (Reverse rotation inhibition by not passing the air A to be described later).
Further, a characteristic ratio is that the ratio of the circumferential velocity of the rotary blade 1220 to the velocity of the compressed air in the power generating unit 1200 does not exceed 2.
It is characteristic that a plurality of blades 1222 having a curved surface are installed on the rotary disk 1224 in the rotary vane 1220 in the power generating unit 1200. Further, the rotating disk 1224 is not limited to having a plane perpendicular to the rotation axis.
The power generating unit 1200 is characterized in that when the pressure of the compressed air is 0.1 to 1.2 MPa and the flow rate is 50 to 600 liters per minute and the radius of the rotating disk is 5 to 50 mm, 50000 rpm or less.
Preferably, in the power generating unit 1200, when the pressure of the compressed air is 0.2 to 0.6 MPa, the flow rate is 50 to 200 liters / minute, and the radius of the rotating disk is 20 to 40 mm, 20000 to 40000 rpm. Here, regarding the number of revolutions of the rotating shaft, the optimum number of revolutions is suitably set in accordance with the characteristics of the revolving electric machine (the generator 1290) employed in the above-mentioned range.
Details of the power generating unit 1200 having these features will be described below.
(1) and (2) described above for the purpose of suppressing over-rotation of the small-sized rotary vane by using high-pressure compressed air and not lowering the rotation efficiency, .
The flow of the air introduced from the input port 1214 side is changed by about 90 degrees to flow out to the output port 1218 side so that the kinetic energy of the compressed air in the region 1212 of FIG. (1222) receives energy and is converted into rotational energy of the rotary vane (1220).
First, a description will be given of the point that the power generating unit 1200 rotates the rotating blades 1220 with high efficiency (without lowering the rotating efficiency) and suppressing reverse rotation.
As shown in Fig. 8, when high-pressure compressed air (compressed air of relatively high pressure up to 1.2 MPa) flows into the small housing case 1210 and the rotary vane 1220 in the power generating unit 1200, Turbulence outside the supposed range occurs in the region 1213 in the rotary blade 1220 indicated by oblique lines in Fig. 8, and the turbulent flow flows to the downstream side, and a turbulent flow T is generated. The air A and the air B indicated by the arrow A in the opposite direction to the original flow in the power generating unit 1200 (the mainstream from the input port 1214 to the output port 1218) Air B is generated. In order to suppress the reverse rotation without lowering the rotation efficiency, it is preferable that the pressure of the introduced compressed air (mainstream)> the pressure of the air (B)>>> the pressure of the air (A). In the configuration shown in Fig. 8, 1/4 of the plurality of rotary vanes 1220 acts in the reverse rotation direction, and the other 3/4 acts in the forward rotation direction. The air B generated after passing through the rotary vane 1220 joins with the input air (mainstream) flowing in from the input port 1214 in the region where the air B acts, Strengthen.
As described above, in the power generating unit 1200, 1/4 of the rotary vane 1220 is directly subjected to pressure from the compressed air, and the compressed air that exits the rotary vane 1220 is opposite to the mainstream of the turbulent flow (Air A) and air B (air B) generated in the direction of rotation of the air B are generated, but the air B is utilized for rotation in the forward rotation direction So it does not turn over).
Next, a description will be given of how the power generating unit 1200 rotates the rotating blade 1220 so as not to rotate excessively (overcontrol). In addition, the over-rotation suppression is designed not to exceed the rotational speed limited by the mechanical characteristics of the rotating electric machine (generator). As for the over-rotation suppression, it is preferable that the fluctuation of the flow rate of the first air by the valve unit 1100 is small and the flow rate can be reduced, the characteristic that the peripheral speed ratio is around 1 (when it exceeds 2, Shaped rotary blades 1260 as shown in Fig. 12, which will be described later, and the rotary vanes 1220 having the rotary vanes 1220, A structure in which the energy of air is transmitted, and the like.
By suppressing the over-rotation in this way, the pressure of the compressed air is 0.1 to 1.2 MPa and the flow rate is 50 to 600 liters (the flow velocity of the peripheral speed / compressed air, which is the tip speed of the rotary vane 1220) / Min, and the radius of the rotating disk is 5 to 50 mm, the number of rotations of the rotating shaft is 50,000 rpm or less.
The input port 1214 side and the output port 1218 side are blocked by the housing inner wall 1216 (upper side) of the housing case 1210 and the tip end of the blade 1222 of the rotary vane 1220, (Air A) from the port 1218 side to the input port 1214 side can be suppressed, contributing to suppression of reverse rotation.
The reason that the first air flowing into the power generating unit 1200 is rectified is that the flow rate passing through the first valve body 1150 by the needle piston 1140 is And the fluctuation amount of the flow rate in the first output pipe 1126 is suppressed. Then, the compressed air of a constant flow rate stably flows into the power generating unit 1200, so that it is possible to stably generate a constant power with the features (1) and (2) described above.
9, eight blades 1222 are installed upright on the rotating disk 1224 on the surface of the rotating blade 1220 (the reverse side of the generator 1290), and the end of the blade 1222 on the rotating shaft side is supported by the supporting portion 1226, respectively. The blade 1222 has a curved surface shape with good energy conversion efficiency. The rotation shaft support portion 1230 is installed at the center of the rotation disc 1224 at the back face of the rotary wing 1220 (on the side of the generator 1290), and the four ribs 1228 standing upright on the back face of the rotation disc 1224 The rotary shaft support portion 1230 is supported.
10 is a view of a rotary vane 1240 in which the number of blades 1222 is changed from 8 to 6 in the rotary vane 1220 of Fig. 9, and Fig. 11 is a view of the rotary vane 1220 of Fig. FIG. 12 is a view of a rotating blade 1250 in which the shape of a curved surface of the blade is changed. FIG. 12 is a view showing the shape of a curved surface of the blade in the rotating blade 1220 shown in FIG. The shape of the rotary blade 1260 is changed from a curved shape to a curved shape.
11 and 12, (a) is a reference rotation angle of 0 degree, (b) is 45 degrees from a reference rotation angle, (c) is 90 degrees from a reference rotation angle, Respectively. As shown in Fig.
All of the rotary vane 1220 shown in Fig. 9, the rotary vane 1240 shown in Fig. 10, the rotary vane 1250 shown in Fig. 11, and the rotary vane 1260 shown in Fig. A plurality of blades having a curved surface are installed upright on the rotary disk 1224 having the above-described features (1) and (2). Further, the rotation disc 1224 is not limited to a plane having a plane perpendicular to the rotation axis.
For example, as shown in Fig. 12 (c), for example, when the number of revolutions of the rotary vane 1260 is 90 degrees from the reference rotation angle and the drag force of the generator 1290 is raised accordingly It is preferable that the flow of the compressed air starts to pass through between the rotary blades 1260, which are saberoid type blades, thereby suppressing over rotation.
Even if any rotary blades are used, the peripheral speed ratio in the power generating unit 1200 does not exceed 2, the pressure of the compressed air is 0.1 to 1.2 MPa, the flow rate is 50 to 600 l / min, Is 5 to 50 mm, the rotation speed of the rotation shaft is 50000 rpm or less.
[Structure of Discharge Unit]
Next, the structure of the discharge unit 1400 of the discharge neutralizing apparatus 1000 will be described with reference to Fig. The supporting structure of the discharge needle 1430 of the discharge unit 1400 will be described later in the structure of the nozzle unit 1300. [
The discharge unit 1400 ionizes the compressed air that has passed through the post-generation air pipe 1040. The discharge unit 1400 includes a control board 1410 connected to the generator 1290 to receive power supplied from the generator 1290 and a control board 1410 connected to the control board 1410 to generate high voltage power based on the power generated by the generator 1290 A high voltage power generation substrate 1420 and a discharge needle 1430 connected to the high voltage power generation substrate 1420 and generating a corona discharge by applying high voltage power.
The control substrate 1410, the high-voltage power generation substrate 1420, and the discharge needle 1430 (the structure of the discharge needle 1430 itself) are well-known, and thus the detailed description thereof will not be repeated.
[Structure of Nozzle Unit]
Next, the structure of the nozzle unit 1300 of the static eliminator device 1000 will be described with reference to Figs. 1 to 5, a sectional view of the nozzle unit 1300 shown in Fig. 13, a nozzle unit 1300 A partial three-sided view of the nozzle unit 1300 shown in Fig. 15, a more partial sectional view and an enlarged view of the nozzle unit 1300 shown in Fig. 16, and a cap 1370 With reference to three-side view and cross-sectional view.
The nozzle unit 1300 functions as a nozzle unit that jets and ejects two or more systems of compressed air having different flow rates. The nozzle unit 1300 functions as a second compressed air having a flow velocity higher than that of the first compressed air The second nozzle 1340 is located upstream of the compressed air at the tip of the second nozzle 1340 and in the vicinity of the second nozzle 1340 1, and a first nozzle for blowing compressed air (power generation side air). The first compressed air is sucked by the negative pressure generated by the second compressed air ejected from the second nozzle 1340, Is ejected together with the second compressed air. Here, the first nozzle will be described later. However, as shown in Fig. 13, the tip of the gap formed by the inner wall of the member (cap 1370) and the second output hole 1312 and the second tube outer cylinder surface 1314 (Inner diameter of the cap 1370> outer diameter of the second pipe outer surface 1314> outer diameter of the second output hole 1312).
More specifically, the nozzle unit 1300 includes a first input hole 1334 through which the first compressed air flows, a second input hole 1318 through which the second compressed air with a flow velocity higher than that of the first compressed air flows, A first output hole 1322 through which the first compressed air is ejected, a second output hole 1312 through which the second compressed air is ejected, a first input hole 1334 and a first output hole 1322 And a second conduit 1316 connecting the second input hole 1318 and the second output hole 1312. The second conduit 1316 connects the second input hole 1318 and the second output hole 1312 to each other. A second nozzle 1340 having a small diameter nozzle hole for ejecting the second compressed air is provided as a second output hole 1312 at the tip end of the second conduit 1316 and a second nozzle 1340 (Specifically, the cap 1370) in which the first compressed air flows through the inside thereof due to the negative pressure generated by the second compressed air ejected from the nozzle (cap 1370) (Hereinafter sometimes referred to as a space) between the outer circumferential surface of the first duct and the outer diameter of the second duct 1316 (the second duct outer circumferential surface 1314) 1370) so as to expose the nozzle hole.
This member is a cap which covers the periphery of the tip end portion of the second duct 1316 at the tip end side thereof and which is provided on the first output hole side as a first output hole and in which the first compressed air flows along the inner wall of the cap And is ejected from the distal end portion 1313 of the gap.
As described above, the non-straight tube portion 1330, which is the first tube, is non-straight tube type and the second tube 1316 is straight tube type.
Also characteristic is that the cap 1370 has a hollow, generally frustoconical shape with a downstream side of the compressed air and a second output hole 1312 in which the downstream side of the compressed air has a solid, substantially cylindrical shape A second nozzle 1340 having a plurality of small-diameter nozzle holes radially formed at the tip of the second conduit 1316 is formed. A plurality of grooves are radially provided on the inner wall of the cap.
Details of the nozzle unit 1300 having these features will be described below.
In this nozzle unit 1300, a post-power generation air pipe 1040 is connected to the first input hole 1334, and an air pipe 1030 for the duster is connected to the second input hole 1318, respectively.
First, the supporting structure of the discharge needle 1430 of the discharge unit 1400 will be described with reference to FIG. The discharge needle 1430 is supported by the discharge needle holder 1360 and the discharge needle holder 1360 is connected to the ceramic body 1364 And a metal cylinder (metal barrel) 1362 attached thereto. And the downstream side of the ceramic cylinder 1364 is supported by the storage needle 1430 of the discharge needle 1430 on the upstream side of the ceramic cylinder 1364. The compressed air from the non- And is inserted into the connection hole 1326 so as to flow toward the needle 1430 side.
Next, the configuration of the nozzle unit 1300 will be described with reference to FIG. The nozzle unit 1300 is constituted by approximately three parts excluding the supporting parts of the discharge needle 1430 described above and includes a rectifying plate 1310, a cap 1370, a rectifying plate And a nozzle case 1390 that integrally supports the cap 1370 and the cap 1370. [ Hereinafter, the structure of the rectifying plate 1310 will be described with reference to Figs. 14 to 16, and the structure of the cap 1370 will be described with reference to Fig.
As shown in Figs. 14 and 15, the rectifying plate 1310 is configured to penetrate the support disc 1320, the non-straight pipe portion 1330 and the straight pipe portion 1324 as the first pipe, and the support disc 1320 And a second channel 1316 having an installed straight pipe shape. The surface of the outer tube constituting the second channel 1316 is referred to as a second tube outer tube surface 1314.
14 shows the flow of the first compressed air (power generation side) and the second compressed air (duster side) in the rectifying plate 1310 with arrows. The flow of the first compressed air in this flow regulating plate 1310 flows from G (1) to G (2), and the flow of the second compressed air flows from D (1) to D (2).
More specifically, as shown in Figs. 14 and 15, the first compressed air entered from the first input hole 1334 of the non-straight tube portion 1330 as the first pipe collides against the supporting disk 1320, And is discharged to the first output hole 1322 through the straight pipe portion 1324 from the connection hole 1326. The straight pipe portion 1324 is connected to the straight pipe portion 1330, do. The discharged first compressed air passes through a space formed by the second output hole 1312 and the second tube outer tube surface 1314 and the cap 1370 to form a tip portion 1313 as a first nozzle provided on the downstream side thereof, Is discharged from the antistatic vibration damping apparatus (1000). The first compressed air discharged from the non-straight tube portion opening 1332 is ionized by the corona discharge generated from the discharge needle 1430 when the first compressed air enters the connection hole 1326. That is, the first compressed air impinges on the supporting disk 1320, is led to the non-straight pipe portion 1330, and the direction of the flow is changed, so that the first compressed air is ionized in a state where the flow velocity is considerably lowered. In order to efficiently eject the first compressed air having the reduced flow velocity from the first nozzle (the tip end portion 1313), the second compressed air maintaining the high-pressure and high-speed state without changing the direction of the flow, (1340).
14 and 15, the second compressed air entered from the second input hole 1318 of the second conduit 1316 is not changed in the direction of flow but is provided as the second output hole 1312 And is discharged from the second nozzle 1340.
In this way, in the rectifying plate 1310, the direction of the flow of the first compressed air is changed to face the first nozzle (the tip end 1313), while the direction of flow of the second compressed air is not changed, And is directed to the nozzle 1340.
The structure of the second nozzle 1340 will be described with reference to Fig. 16 (a) is an enlarged cross-sectional view of an arrow XX in Fig. 15, Fig. 16 (b) is an enlarged cross-sectional view of an arrow YY in Fig. 15, and Fig. 16 .
As shown in Figs. 15A and 16C, the second nozzle 1340 has a plurality of (here, six) nozzle holes 1342 with the center portion 1380 as the center of point symmetry And a negative pressure groove 1346 corresponding to the number of the nozzle holes 1342 is provided between the nozzle holes 1342. A negative pressure generated by the second compressed air ejected from the nozzle hole 1342 at a high pressure and at a high speed is rectified by the negative pressure groove 1346 and the negative pressure along the negative pressure groove 1346 is applied to the first nozzle The first compressed air is efficiently sucked.
The structure of the cap 1370 will be described with reference to Fig. The cap 1370 has a substantially hollow conical shape with a downstream side of the compressed air and has a substantially cylindrical shape with a cylindrical body 1374 and an opening 1372 on the downstream side of the cylinder 1374 and a flange 1376 on the upstream side of the cylinder 1374 . 17 (b) and 17 (c), the shape of the cap 1370 is not symmetrical in the vertical direction as viewed from the side. However, the present invention is not limited to this shape, 1370 may have a hollow, generally frusto-conical shape.
A groove 1380 is radially provided on the inner wall of the cylindrical body 1374 and is formed by the second output hole 1312 and the second pipe outer cylinder surface 1314 and the cap 1370 as shown in Fig. The negative pressure generated by the second compressed air ejected from the nozzle hole 1342 is rectified by this groove 1380 (effectively inducing the negative pressure) in the space where the first nozzle (the tip end 1313) 1 Effective jet of compressed air. The groove 1380 is formed by cutting the inner wall of the cylinder 1374 so as to leave, for example, the convex portion 1378. [
[Operation of static eliminating apparatus]
The operation of the antistatic vibration suppression apparatus 1000 according to the present embodiment having the above-described structure will be described with reference to FIGS. 18 and 19 7).
The user grasps the static eliminator device 1000 and holds the static eliminator object 1000 at the time t (1) toward the front end (second nozzle 1340) of the static eliminator device 1000, The two-way valve 1120 shifts from the state shown in Fig. 6 to the state shown in Fig. 7 (a), so that the power generation unit 1200 is provided with the first Compressed air starts to flow.
The rotating blade 1220 is rotated by the first compressed air flowing in the power generating unit 1200 so that the generator 1290 connected to the rotating shaft of the rotating blade 1220 starts to rotate and at the time t (2) And starts corona discharging from the discharge needle 1430 at the subsequent time t (3). At the subsequent time t (4), the first compressed air is ejected from the first nozzle (tip end 1313). At this time, however, since the second compressed air is not ejected from the second nozzle 1340, the suction action by the negative pressure is not generated. In Fig. 18, the difference in the flow rate of the first compressed air from the first nozzle (front end portion 1313) due to the presence of negative pressure suction is not expressed.
The real time of the times t (1) to t (4) is the delay time of the compressed air, the delay time on the electric circuit of the electric circuit (the generator 1290, the control board 1410 and the high voltage power generating board 1420) A corona discharge delay time in the discharge needle 1430, and is, for example, a short time of several seconds or less. In such a short time, it is preferable that the compression air is made to be ionized at time t (4) at which the first compressed air is injected in the antistatic vibration damping apparatus 1000. However, the present invention is not limited to the static elimination device that exhibits such an operation.
Next, at time t (5), when the user pulls the inner second trigger 1114 (pulls the inner second trigger 1114 together with the outer first trigger 1112), the two-way valve 1120 7 (a) to the state shown in Fig. 7 (b), and while the first compressed air flows in the power generation unit 1200 while keeping the predetermined amount Q (1) The second compressed air starts to flow. At the subsequent time t (6), the second compressed air is ejected from the second nozzle 1340. At this time, since the second compressed air is ejected from the second nozzle 1340, the suction action by the negative pressure is developed, and the first compressed air from the first nozzle (the tip 1313) is ejected efficiently .
After this time t (5), in proportion to the valve opening degree of the second valve body 1160 of the two-way valve 1120, until the second trigger 1114 becomes fully open, The ejection flow rate (and the total ejection flow rate) of the second compressed air from the ejection opening 1340 is changed. 18, it is assumed that the user opens the second trigger 1114 at a constant rate with respect to time in order to explain this approximately proportional relationship.
During this time t (5) to t (7) (when the second valve element 1160 is in the open state as shown in FIG. 7 (b)), the flow rate of the second compressed air is increased (In particular, when the second valve body 1160 is abruptly opened by abruptly holding the second trigger 1114, and the two-port valve opening indicated by the one-dot chain line in Fig. 18) Explain.
When the second trigger 1114 is suddenly opened at the time t (12) in the middle of increasing the flow rate of the second compressed air for vibration suppression at the time t (11), the pressure in the first communicating pipe 1122 The pressure of the compressed air drops. 7 (c), the needle piston 1140 is pressed by the first spring 1136 and the second spring 1138 against the pushing force by the first spring 1136 and the second spring 1138 at the time t (12) 6 < / RTI > The gap between the tip tapered portion 1148 and the third communicating pipe 1132 is widened as the needle piston 1140 moves downward and the gap between the tip tapered portion 1148 and the third communicating pipe 1132 is increased, 1 compressed air is not reduced.
Thereafter, at time t (13), when the sudden opening of the second trigger 1114 is stopped, at time t (14), the pressure of the compressed air in the first communicating path 1122 is recovered. 6, the clearance between the tip end tapered portion 1148 and the third communicating pipe 1132 is narrowed, and the pressure in the first valve body 1140 is reduced. As a result, The first compressed air supplied to the power generation unit 1200 through the first flow path 1150 is adjusted to return to the original flow rate.
Furthermore, the relationship of the time t (13) and the time t (14) is not limited to that shown in Fig. The pressure of the compressed air in the first communicating path 1122 may be restored even when the second trigger 1114 is rapidly opened.
[Function and effect]
As described above, according to the electrostatic discharge eliminating apparatus 1000 according to the present embodiment,
As a first feature, the compressed air used for power generation and the compressed air for damping are divided,
As a second feature, a valve unit having an adjustment mechanism as a valve unit is used to divide the air flow path into two systems,
As a third feature, a compact power generating unit using high-pressure compressed air as an energy source is employed,
As a fourth feature, a nozzle unit for jetting and jetting two or more systems of compressed air having different flow velocities is employed,
It is possible to provide an electrostatic discharge suppressing apparatus which can sufficiently exhibit the discharge function and the vibration damping function and is small in size, low in cost, and excellent in operability.
It is also to be understood that the presently disclosed embodiments are illustrative and non-restrictive in all respects. The scope of the present invention is not limited to the above description, but is defined by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.
