IPC분류정보
국가/구분 |
United States(US) Patent
등록
|
국제특허분류(IPC7판) |
|
출원번호 |
US-0844113
(2001-04-25)
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발명자
/ 주소 |
- Chisum, Dennis
- Freeborn, Perry
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대리인 / 주소 |
Birch, Stewart, Kolasch & Birch, LLP
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인용정보 |
피인용 횟수 :
9 인용 특허 :
28 |
초록
▼
An abrasivejet cutting head is disclosed for use in an abrasivejet cutting system. The cutting head includes a replaceable generally cylindrical insert member having a fluid passageway aligned with the passageway of the housing. A waterjet-forming orifice member is supported within the insert in axi
An abrasivejet cutting head is disclosed for use in an abrasivejet cutting system. The cutting head includes a replaceable generally cylindrical insert member having a fluid passageway aligned with the passageway of the housing. A waterjet-forming orifice member is supported within the insert in axial alignment with the abrasivejet discharge nozzle located at the downstream end of the cutting head. The insert is locked into the cutting head by the sleeve of an abrasive-carrying conduit, and provides the mixing region in which the abrasive is entrained into the waterjet. By making the jet-forming orifice and mixing region an integral unit, the mixing chamber is conveniently changed every time the wear in the jet-forming orifice requires an orifice change to maintain high cutting efficiency, while adding virtually no cost in additional components since it merely requires a slightly elongated insert than would otherwise be necessary. In addition, the relatively expensive abrasivejet nozzle, which is typically the longest lasting component of the three, need not be replaced until necessary and, when necessary, is easily removed and replaced in co-axial alignment with the orifice. Lastly, the arrangement results in self-alignment of the waterjet-forming orifice, the mixing region and the abrasivejet nozzle.
대표청구항
▼
An abrasivejet cutting head is disclosed for use in an abrasivejet cutting system. The cutting head includes a replaceable generally cylindrical insert member having a fluid passageway aligned with the passageway of the housing. A waterjet-forming orifice member is supported within the insert in axi
An abrasivejet cutting head is disclosed for use in an abrasivejet cutting system. The cutting head includes a replaceable generally cylindrical insert member having a fluid passageway aligned with the passageway of the housing. A waterjet-forming orifice member is supported within the insert in axial alignment with the abrasivejet discharge nozzle located at the downstream end of the cutting head. The insert is locked into the cutting head by the sleeve of an abrasive-carrying conduit, and provides the mixing region in which the abrasive is entrained into the waterjet. By making the jet-forming orifice and mixing region an integral unit, the mixing chamber is conveniently changed every time the wear in the jet-forming orifice requires an orifice change to maintain high cutting efficiency, while adding virtually no cost in additional components since it merely requires a slightly elongated insert than would otherwise be necessary. In addition, the relatively expensive abrasivejet nozzle, which is typically the longest lasting component of the three, need not be replaced until necessary and, when necessary, is easily removed and replaced in co-axial alignment with the orifice. Lastly, the arrangement results in self-alignment of the waterjet-forming orifice, the mixing region and the abrasivejet nozzle. tion of said at least six drive shafts and the weights carried by said drive shafts to impart the substantially horizontal force to the material-conveying trough; wherein the belt is routed in a specific pattern such that each pair of drive shafts rotates at a predetermined rotational speed; and wherein the rotational speed of each pair of drive shafts and the weights carried by each pair of drive shafts are selected to approximate the terms of a Fourier series. 2. A differential motion conveyor drive as recited in claim 1, in which said first pair of shafts counter-rotate at a predetermined operating speed ω, said second pair of shafts counter-rotate rotate at an operating speed 2ω, and said third pair of shafts counter-rotate at an operating speed 3ω. 3. A differential motion conveyor drive as recited in claim 2, in which the respective weights carried by the first, second, and third pairs of drive shafts are WR, essentially (0.50)WR, and essentially (0.33)WR. 4. A differential motion conveyor drive as recited in claim 2, in which the respective weights carried by the first, second, and third pairs of drive shafts are WR, essentially (0.18)WR, and essentially (0.05)WR. 5. A differential motion conveyor drive as recited in claim 1, wherein the weights carried by said second pair of drive shafts are out of phase by -90° with respect to the weights of said first pair of drive shafts, and wherein the weights carried by said third pair of drive shafts are out of phase by 180° with respect to the weights of said first pair of drive shafts. 6. A differential motion conveyor drive as recited in claim 5, in which the respective weights carried by the three pairs of drive shafts are WR, essentially (0.33)WR, and essentially (0.10)WR. 7. A differential motion conveyor drive as recited in claim 1, wherein the weights carried by the respective drive shafts are mounted so as to produce equal but opposite vertical force components that cancel one another throughout the rotation of said drive shafts. 8. A differential motion vibratory conveyor having a trough for carrying material, comprising: at least three pairs of counter-rotating shafts mounted to a frame and extending substantially perpendicular to a direction of movement of the material carried by said trough, each of said shaft pairs carrying eccentric weights, the eccentric weight carried by each shaft of a respective shaft pair being essentially the same magnitude as the eccentric weight of the other shaft of the shaft pair, such that the forces imparted to the trough by the rotating eccentric weights are substantially horizontal, said first, second, and third shaft pairs being rotated respectively at speeds of essentially ω, 2ω, and 3ω, and the associated eccentric weights of each of said shafts pairs selected to approximate the first several terms of a Fourier series, 9. A differential motion vibratory conveyor as recited in claim 8, in which the respective eccentric weights carried by the three pairs of shafts are WR, essentially (0.50)WR, and essentially (0.33)WR. 10. A differential motion vibratory conveyor as recited in claim 8, in which the respective eccentric weights carried by the three pairs of shafts are WR, essentially (0.18)WR, and essentially (0.05)WR. 11. A differential motion conveyor drive as recited in claim 8, wherein the eccentric weights carried by said second pair of shafts are out of phase by -90° with respect to the eccentric weights of said first pair of shafts, and wherein the eccentric weights carried by said third pair of shafts are out of phase by 180° with respect to the eccentric weights of said first pair of shafts. 12. A differential motion conveyor drive as recited in claim 11, in which the respective eccentric weights carried by the three pairs of drive shafts are WR, essentially (0.33)WR, and essentially (0.10)WR. 13. A method of maximizing conveying speed in a differential motion vibratory conveyor having a trough carrying material by approximating a Fourier series, representing an idealized velocity profile during a complete cycle in which the trough is provided with a slower forward velocity as a portion of the complete cycle, and a faster return velocity as the remainder of the complete cycle, comprising the steps of: (a) providing the conveyor with at least three pairs of counter-rotating shafts extending essentially perpendicular to a direction of conveyance, each of said shaft pairs carrying eccentric weights, the eccentric weight carried by each shaft of a respective shaft pair being essentially the same magnitude as the eccentric weight of the other shaft of the shaft pair, such that the forces imparted to the trough by the rotating eccentric weights are substantially horizontal; and (b) arranging the first, second, and third shaft pairs to rotate at predetermined speed and the associated eccentric weights of the first, second, and third shaft pairs having magnitudes essentially approximating respective first, second, and third terms of the Fourier series. 14. A method as recited in claim 13, in which said first pair of shafts counter-rotate at a predetermined operating speed ω, said second pair of shafts counter-rotate at an operating speed 2ω, and said third pair of shafts counter-rotate at an operating speed 3ω. 15. A method as recited in claim 14, in which the respective weights carried by the three pairs of shafts are WR, essentially (0.50)WR, and essentially (0.33)WR. 16. A method as recited in claim 14, in which the respective weights carried by the three pairs of shafts are WR, essentially (0.18)WR, and essentially (0.05)WR. 17. A method as recited in claim 13, wherein the weights carried by said second pair of shafts are out of phase by -90° with respect to the weights of said first pair of shafts, and wherein the weights carried by said third pair of shafts are out of phase by 180° with respect to the weights of said first pair of shafts. 18. A method as recited in claim 16, in which the respective weights carried by the three pairs of shafts are WR, essentially (0.33)WR, and essentially (0.10)WR.
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