EP0041534B1 - High pressure blowing tool having low noise level - Google Patents
High pressure blowing tool having low noise level Download PDFInfo
- Publication number
- EP0041534B1 EP0041534B1 EP81900027A EP81900027A EP0041534B1 EP 0041534 B1 EP0041534 B1 EP 0041534B1 EP 81900027 A EP81900027 A EP 81900027A EP 81900027 A EP81900027 A EP 81900027A EP 0041534 B1 EP0041534 B1 EP 0041534B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- nozzle
- exhaust
- outlet
- fluid
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000007664 blowing Methods 0.000 title claims abstract description 21
- 239000012530 fluid Substances 0.000 claims abstract description 15
- 230000005484 gravity Effects 0.000 claims description 10
- 239000003570 air Substances 0.000 abstract description 7
- 239000012080 ambient air Substances 0.000 abstract description 2
- 239000007789 gas Substances 0.000 description 18
- 238000010276 construction Methods 0.000 description 3
- 230000000994 depressogenic effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
- B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
- B05B1/005—Nozzles or other outlets specially adapted for discharging one or more gases
Definitions
- Fig. 1 is a longitudinal section view.
- the gas is supplied to the tool through a high pressure hose 2 which is connected to the gas source and has a high pressure above atmospheric.
- a hand grip 3 is depressed, a valve slide 4 being moved so that gas can pass through a groove in the slide and an extension tube 6 out through the mouth 7 of the extension tube.
- the pressure before the mouth at which critical pressure ratio can be obtained is determined by the counter pressure after the mouth which in its turn is influenced by the degree of co-ejection, i.e. to which extent the air jet leaving the mouth in its motion takes the ambient air with it, in such a way that the higher co-ejection that can be obtained the higher supply pressure can be applied on the high pressure hose 2 before the critical pressure ratio is reached.
- the resulting higher density of the gas gives larger blowing force in addition to the supplementary blowing power that co- ejected air gives.
- the pressure of the gaseous medium immediately before the outlet would substantially correspond to the applied supply pressure within the high pressure hose 2, i.e. at normally occurring supply pressure of 6-8 bars the pressure of the gas immediately before the outlet would be substantially equal to 6-8 bars.
- the pressure of the gas would, if all the air passages before the outlet are substantially greater than the outlet passage, after expansion be greater than 3.15 bars, i.e. more than 3 times the pressure existing around the tool.
- the object of the present invention which is based on studies is to provide a blowing tool of this general type having a low noise level, a great blowing power and a high mechanical efficiency.
- Figures 2 to 9 show examples of blowing tools according to the invention.
- the gas is supplied to the tool through a connection 8 and passes through a passage between the valve plate 9 and the valve seat 10 as the front rubber cone 11 is tilted.
- this passage is greater than 0,5, suitably greater than 0.65, preferably greater than 0.8 times the total outlet area of the outlet apertures 12 at the nozzle 13, i.e. preferably so that the velocity of the gas at the valve passage is lower than the velocity of the gas at the outlet passage, so that the generation of noise at the valve preferably is lower than the generation of noise at the outlet.
- valve passage By having the outlet apertures spaced from each other a large distance the valve passage can advantageously also be made larger, preferably substantially larger than the total outlet passage, so that mainly the whole supply pressure connected to the blowing tool can be utilized, i.e. the gas pressure in the chamber 14 can advantageously be essentially equal to the supply pressure.
- the front part of the tool can be formed as a cylinder, a truncated cone or with the chamfering increasing towards the nose.
- the outlet passages can advantageously end near or in the mantle surface as appears from Figs. 2-5 and Figs. 6-7 respectively.
- the outlet apertures are so positioned that co-ejection is obtained around the whole periphery of each partial jet.
- this can in practice be realized a.o. by placing the outlet apertures 12 on a circle the diameter D of which is greater than 4 times the diameter d of the largest outlet passage, which is less than 2 mm, preferably at the most 1.5, e.g. about 1 mm, and by spacing the apertures with a large distance and substantially not within the central parts of the nozzle.
- the outlet apertures should be positioned with a mutual centre distance which is larger than 2 times the diameter of the aperture for outlet apertures which are less than 1 mm.
- the mutual centre distance should be greater than 2 times the square of the diameter of the aperture. In this way also a reduced mutual interaction between the outgoing gas jet is obtained.
- more than 10%, suitably more than 20%, preferably more than 40%, of the outlet area should be positioned outside an area A c , which is 3 times greater than the sum A ut of the cross sectional areas of the outlet passages, A c being situated so that its centre of gravity coincides with the centre of gravity of a pattern area A f situated in the same plane as A c , being geometrically similar to A c and with the smallest possible periphery containing the outlet areas of all the exhaust passages.
- the largest cross sectional dimension of the outlet jet should be at the most 2 mm, preferably at the most 1.5 mm, e.g. about 1 mm, i.e. for circular outlet apertures the diameter should be at the most 2 mm, preferably at the most 1.5 mm and can e.g. be about 1 mm, for a.o. having a fast pressure equalization between the ambient pressure and the pressure in the central parts of the gas jet.
- a pattern area A f is first designed by connecting consecutively the outer outlet apertures in the configuration of the apertures with straight lines forming tangents to the outer side of said outer apertures, A F being limited by said straight lines between the tangential points of consecutive apertures and the outer side of each aperture between its tangential points.
- the area A c is so situated that its centre of . gravity coincides with the centre of gravity of the pattern area A f .
- Each side of A c is parallel to the corresponding side of the pattern area A f .
- the area A c is thus projected symmetrically around the centre of the circle.
- the mantle 15 at the termination of the nozzle can be conical or tapering as in one of the shown embodiments.
- Half of the cone angle, a according to Fig. 4 should then be less than 20°, however not less than 10°.
- the outlet apertures should be spaced with a centre distance exceeding 1.5, preferably exceeding 2 times the diameter of the aperture for the outlet passages which is less than 2 mm, preferably less than 1.5 mm, e.g. 1 mm.
- a ut of the cross sectional area of the exhaust passages at the outlet, transversally to the direction of the flow should be placed outside an area A' c which is 2 times larger than A ut , A' c being so located that its centre of gravity coincides with the centre of gravity of a pattern area A f , situated in the same plane as A' c , being geometrically similar to A' c and completely enclosing with the smallest possible periphery the outlet areas of all the outlet passages.
- Half of the cone angle a for the nozzle should then be between 10° and 20°, and in addition it is assumed that the direction of the flow from the outlet passages does. not deviate more than 10° from the axis of the cone.
- the termination of the nozzle can advantageously be provided with means 16 projecting from the nozzle body as shown in Figs. 2 and 4 to 9, which are so designed that they do not influence the co-ejection capacity of the nozzle or otherwise disturb the outflow of gas. It is important that the nozzle has this mechanical shield, because if for instance only one of the outlet apertures should be deformed, for instance by a burr or a flash arising within the flow area, this will result in an increase of the noise level which can be of 3 to 4 dB (A). Since the noise thus arising furthermore has the nature of a pure tone, the increase in the noise level should be placed on an equality, as regards the risk of impaired hearing, with an increase of the noise level of 13-14 dB (A) for a wide band noise.
- the exhaust passages of the nozzle together give directed exhaust of the gaseous fluid from the nozzle.
- the hypothetical central lines of the passages in the direction of the fluid flow can be parallel to each other, but this is not necessary, as said central lines can diverge up to about 20° or even 30° between themselves and in relation to the exhaust direction of the nozzle and yet give a directed jet of fluid from the nozzle.
- Annularly arranged exhaust passages of a nozzle having a conically mantle can for instance have their central lines located on a hypothetical conical surface situated inside and presenting a smaller cone angle than the conical mantle of the nozzle.
- Prototypes of the device according to the invention in accordance with the embodiments illustrated in Figs. 2 to 9 have been subjected to practical testing and have been compared with most commercially available so-called silent blowing nozzles having a body of porous, sintered metal inserted into the exhaust tube, and have also been compared with the majority of conventional blowing nozzles. In all the cases for a given blowing power in addtion to a higher air consumption the noise level was considerably higher for the comparison nozzles than for the blowing tool according to the invention.
Landscapes
- Jet Pumps And Other Pumps (AREA)
- Nozzles (AREA)
Abstract
Description
- The most common blowing tools have in principle a design according to Fig. 1 which is a longitudinal section view. The gas is supplied to the tool through a high pressure hose 2 which is connected to the gas source and has a high pressure above atmospheric. When the blowing tool is to be used a hand grip 3 is depressed, a valve slide 4 being moved so that gas can pass through a groove in the slide and an
extension tube 6 out through the mouth 7 of the extension tube. - When a gaseous medium in this way is brought to exhaust to the environment a velocity of discharge is obtained which depends on the pressure ratio between the counter pressure after, i.e. in the direction of the flow, the mouth and the pressure before the mouth.
- If the mouth is not formed as a so-called Laval nozzle maximum velocity of discharge is obtained at the so-called critical pressure ratio. The pressure before the mouth at which critical pressure ratio can be obtained is determined by the counter pressure after the mouth which in its turn is influenced by the degree of co-ejection, i.e. to which extent the air jet leaving the mouth in its motion takes the ambient air with it, in such a way that the higher co-ejection that can be obtained the higher supply pressure can be applied on the high pressure hose 2 before the critical pressure ratio is reached. The resulting higher density of the gas gives larger blowing force in addition to the supplementary blowing power that co- ejected air gives.
- If the interior of the blowing tool is designed so as to achieve low losses, i.e. if all of the flow passages before the outlet have a substantially greater cross sectional area than that of the outlet 7, the pressure of the gaseous medium immediately before the outlet would substantially correspond to the applied supply pressure within the high pressure hose 2, i.e. at normally occurring supply pressure of 6-8 bars the pressure of the gas immediately before the outlet would be substantially equal to 6-8 bars.
- Since the pressures of gases immediately after their expansion are never lower than the critical pressure, i.e. not lower than 0.528 times the pressure immediately before the outlet, the pressure of the gas would, if all the air passages before the outlet are substantially greater than the outlet passage, after expansion be greater than 3.15 bars, i.e. more than 3 times the pressure existing around the tool.
- It is important to design the outlet nozzle in such a way that co-ejection is sufficient for the counter pressure after the outlet 7 to deviate only slightly from the pressure immediately after the expansion zone. The more the pressure differs immediately after the expansion from the ambient pressure the stronger turbulence and with that generation of noise, results namely outside the outlet.
- For constructions known up to now it has been possible to reduce this effect to a certain extent by providing a restriction by the air passages before the outlet passage each individually or jointly, i.e. they provide a pressure depression of the supplied pressure connected to the tool. For the conventional tool according to Fig. 1 the flow area at the
air passage 5 is for example only about 0.45 times the flow area at the outlet 7. In such a construction a gas pressure is obtained within the extension tube which is about 0.42 times the supply pressure connected to the tool. The pressure upstream the expansion cross section at the outlet port is thus at normal supply pressures then only about 2.5 to 3.4 bars. - As the co-ejection in such constructions is small, however, a counter pressure is obtained after the outlet port which is lower than 0.528 times the gas pressure existing before the outlet. The difference between the pressure of the gas after the expansion and the present counter pressure results in a strong turbulence also herein the gas flow leaving the outlet port-though to a smaller extent-in comparison with a situation with the whole supplied 'pressure of 6 to 8 bars prevailing within the
extension tube 6. - The publication Verkstaderna, No. 14, issued 1975, October 29, H. Moss, H. Elvhammar, "Renblasning vid skarande bearbetning, pages 27, 28,29,32, especially figure 4B discloses an exhaust nozzle having a plurality of exhaust passages which jointly give directed exhaust of fluid from the nozzle.
- The object of the present invention which is based on studies is to provide a blowing tool of this general type having a low noise level, a great blowing power and a high mechanical efficiency.
- This object is obtained by a blowing device according to the invention which has the characteristic features stated in the claims.
- Figures 2 to 9 show examples of blowing tools according to the invention. The gas is supplied to the tool through a
connection 8 and passes through a passage between the valve plate 9 and thevalve seat 10 as thefront rubber cone 11 is tilted. For a fully opened valve this passage is greater than 0,5, suitably greater than 0.65, preferably greater than 0.8 times the total outlet area of the outlet apertures 12 at thenozzle 13, i.e. preferably so that the velocity of the gas at the valve passage is lower than the velocity of the gas at the outlet passage, so that the generation of noise at the valve preferably is lower than the generation of noise at the outlet. - By having the outlet apertures spaced from each other a large distance the valve passage can advantageously also be made larger, preferably substantially larger than the total outlet passage, so that mainly the whole supply pressure connected to the blowing tool can be utilized, i.e. the gas pressure in the
chamber 14 can advantageously be essentially equal to the supply pressure. - The front part of the tool can be formed as a cylinder, a truncated cone or with the chamfering increasing towards the nose.
- The outlet passages can advantageously end near or in the mantle surface as appears from Figs. 2-5 and Figs. 6-7 respectively.
- The outlet apertures are so positioned that co-ejection is obtained around the whole periphery of each partial jet. For the embodiments according to Figs. 2 to 5 and Figs. 8 to 9 this can in practice be realized a.o. by placing the outlet apertures 12 on a circle the diameter D of which is greater than 4 times the diameter d of the largest outlet passage, which is less than 2 mm, preferably at the most 1.5, e.g. about 1 mm, and by spacing the apertures with a large distance and substantially not within the central parts of the nozzle.
- Studies which have been carried out show that even with large distances between the outlet apertures placed on a circle having the diameter D, it is extremely difficult to obtain good co-ejection for those outlet apertures which are placed within the central parts of the nozzle, i.e. inside the diameter D.
- The outlet apertures should be positioned with a mutual centre distance which is larger than 2 times the diameter of the aperture for outlet apertures which are less than 1 mm. For outlet apertures which are larger than 1 mm the mutual centre distance should be greater than 2 times the square of the diameter of the aperture. In this way also a reduced mutual interaction between the outgoing gas jet is obtained.
- In order to obtain the object of the invention more than 10%, suitably more than 20%, preferably more than 40%, of the outlet area should be positioned outside an area Ac, which is 3 times greater than the sum Aut of the cross sectional areas of the outlet passages, Ac being situated so that its centre of gravity coincides with the centre of gravity of a pattern area Af situated in the same plane as Ac, being geometrically similar to Ac and with the smallest possible periphery containing the outlet areas of all the exhaust passages.
- Further, the largest cross sectional dimension of the outlet jet should be at the most 2 mm, preferably at the most 1.5 mm, e.g. about 1 mm, i.e. for circular outlet apertures the diameter should be at the most 2 mm, preferably at the most 1.5 mm and can e.g. be about 1 mm, for a.o. having a fast pressure equalization between the ambient pressure and the pressure in the central parts of the gas jet.
- To design the area Ac a pattern area Af is first designed by connecting consecutively the outer outlet apertures in the configuration of the apertures with straight lines forming tangents to the outer side of said outer apertures, AF being limited by said straight lines between the tangential points of consecutive apertures and the outer side of each aperture between its tangential points.
- The area Ac is so situated that its centre of . gravity coincides with the centre of gravity of the pattern area Af. Each side of Ac is parallel to the corresponding side of the pattern area Af.
- At a nozzle in which the outlet apertures are positioned on a circle with equal partition, the area Ac is thus projected symmetrically around the centre of the circle. The
mantle 15 at the termination of the nozzle can be conical or tapering as in one of the shown embodiments. Half of the cone angle, a according to Fig. 4 should then be less than 20°, however not less than 10°. - For the embodiment according to Fig. 6 or 7 the outlet apertures should be spaced with a centre distance exceeding 1.5, preferably exceeding 2 times the diameter of the aperture for the outlet passages which is less than 2 mm, preferably less than 1.5 mm, e.g. 1 mm.
- To obtain the object of the invention with this embodiment more than 10%, preferably more than 20%, and best more than 40%, of the sum Aut of the cross sectional area of the exhaust passages at the outlet, transversally to the direction of the flow, should be placed outside an area A'c which is 2 times larger than Aut, A'c being so located that its centre of gravity coincides with the centre of gravity of a pattern area Af, situated in the same plane as A'c, being geometrically similar to A'c and completely enclosing with the smallest possible periphery the outlet areas of all the outlet passages. Half of the cone angle a for the nozzle should then be between 10° and 20°, and in addition it is assumed that the direction of the flow from the outlet passages does. not deviate more than 10° from the axis of the cone.
- To get a mechanical shield so that the outlet apertures are not deformed by hits or impacts the termination of the nozzle can advantageously be provided with
means 16 projecting from the nozzle body as shown in Figs. 2 and 4 to 9, which are so designed that they do not influence the co-ejection capacity of the nozzle or otherwise disturb the outflow of gas. It is important that the nozzle has this mechanical shield, because if for instance only one of the outlet apertures should be deformed, for instance by a burr or a flash arising within the flow area, this will result in an increase of the noise level which can be of 3 to 4 dB (A). Since the noise thus arising furthermore has the nature of a pure tone, the increase in the noise level should be placed on an equality, as regards the risk of impaired hearing, with an increase of the noise level of 13-14 dB (A) for a wide band noise. - Common to the devices according to the invention is that the exhaust passages of the nozzle together give directed exhaust of the gaseous fluid from the nozzle. To obtain this the hypothetical central lines of the passages in the direction of the fluid flow can be parallel to each other, but this is not necessary, as said central lines can diverge up to about 20° or even 30° between themselves and in relation to the exhaust direction of the nozzle and yet give a directed jet of fluid from the nozzle. Annularly arranged exhaust passages of a nozzle having a conically mantle can for instance have their central lines located on a hypothetical conical surface situated inside and presenting a smaller cone angle than the conical mantle of the nozzle.
- Prototypes of the device according to the invention in accordance with the embodiments illustrated in Figs. 2 to 9 have been subjected to practical testing and have been compared with most commercially available so-called silent blowing nozzles having a body of porous, sintered metal inserted into the exhaust tube, and have also been compared with the majority of conventional blowing nozzles. In all the cases for a given blowing power in addtion to a higher air consumption the noise level was considerably higher for the comparison nozzles than for the blowing tool according to the invention.
Claims (4)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT81900027T ATE8850T1 (en) | 1979-12-12 | 1980-12-09 | HIGH PRESSURE NOISE WITH LOW NOISE. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE7910235A SE7910235L (en) | 1979-12-12 | 1979-12-12 | HIGH PRESSURE BLADE TOOL WITH LOW SIZE LEVEL |
SE7910235 | 1979-12-12 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0041534A1 EP0041534A1 (en) | 1981-12-16 |
EP0041534B1 true EP0041534B1 (en) | 1984-08-08 |
Family
ID=20339540
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP81900027A Expired EP0041534B1 (en) | 1979-12-12 | 1980-12-09 | High pressure blowing tool having low noise level |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP0041534B1 (en) |
JP (1) | JPH0316182B2 (en) |
BE (1) | BE886598A (en) |
DE (1) | DE3068922D1 (en) |
DK (1) | DK323781A (en) |
FI (1) | FI69256C (en) |
IT (1) | IT1134668B (en) |
SE (1) | SE7910235L (en) |
WO (1) | WO1981001668A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4652234A (en) * | 1984-03-01 | 1987-03-24 | Voorheis Industries, Inc. | Constant pressure-variable orifice burner nozzle assembly |
US4690639A (en) * | 1984-03-01 | 1987-09-01 | Voorheis Industries, Inc. | Constant pressure variable orifice burner nozzle assembly |
US6561236B1 (en) * | 2000-03-08 | 2003-05-13 | Sealed Air Corporation (Us) | Inflatable packing and inflation apparatus |
CN1316090C (en) | 2001-07-18 | 2007-05-16 | 株式会社尤尼克斯 | Metallic fiber nonwoven fabric manufacturing apparatus, its manufacturing method and laminated aluminium material manufacturing method |
DE102010046710A1 (en) * | 2010-09-28 | 2012-03-29 | Lucien Masson | Pneumatic tool for blowing out |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2917244A (en) * | 1957-08-29 | 1959-12-15 | Ralph L Gould | Safety air gun |
US3047239A (en) * | 1960-02-15 | 1962-07-31 | Joseph M Canavan | Nozzle construction |
JPS4837405B1 (en) * | 1969-12-30 | 1973-11-10 | ||
US3870039A (en) * | 1973-01-18 | 1975-03-11 | Prod Associes | Fractionated liquid jet |
JPS6033544B2 (en) * | 1977-03-17 | 1985-08-03 | 株式会社豊田中央研究所 | Pressure fluid release device for low noise |
SE7806883L (en) * | 1978-06-14 | 1979-12-15 | Ingemanssons Ingenjorsbyra Ab | BLOWER DEVICE WITH LAYER SIZE LEVEL |
-
1979
- 1979-12-12 SE SE7910235A patent/SE7910235L/en unknown
-
1980
- 1980-12-09 DE DE8181900027T patent/DE3068922D1/en not_active Expired
- 1980-12-09 JP JP56500179A patent/JPH0316182B2/ja not_active Expired - Lifetime
- 1980-12-09 EP EP81900027A patent/EP0041534B1/en not_active Expired
- 1980-12-09 WO PCT/SE1980/000327 patent/WO1981001668A1/en active IP Right Grant
- 1980-12-11 IT IT26560/80A patent/IT1134668B/en active
- 1980-12-11 BE BE0/203121A patent/BE886598A/en not_active IP Right Cessation
-
1981
- 1981-07-20 DK DK323781A patent/DK323781A/en not_active Application Discontinuation
- 1981-07-23 FI FI812316A patent/FI69256C/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
DK323781A (en) | 1981-07-20 |
JPS56501754A (en) | 1981-12-03 |
BE886598A (en) | 1981-04-01 |
WO1981001668A1 (en) | 1981-06-25 |
DE3068922D1 (en) | 1984-09-13 |
JPH0316182B2 (en) | 1991-03-04 |
IT8026560A0 (en) | 1980-12-11 |
FI69256B (en) | 1985-09-30 |
SE7910235L (en) | 1981-06-13 |
IT1134668B (en) | 1986-08-13 |
FI812316L (en) | 1981-07-23 |
EP0041534A1 (en) | 1981-12-16 |
FI69256C (en) | 1986-01-10 |
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