EP1129505B1 - Zylindrischer antrieb - Google Patents
Zylindrischer antrieb Download PDFInfo
- Publication number
- EP1129505B1 EP1129505B1 EP99954154A EP99954154A EP1129505B1 EP 1129505 B1 EP1129505 B1 EP 1129505B1 EP 99954154 A EP99954154 A EP 99954154A EP 99954154 A EP99954154 A EP 99954154A EP 1129505 B1 EP1129505 B1 EP 1129505B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- guide means
- actuator according
- generally cylindrical
- channel
- cylindrical member
- 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 - Lifetime
Links
Images
Classifications
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01Q—ANTENNAS, i.e. RADIO AERIALS
- H01Q1/00—Details of, or arrangements associated with, antennas
- H01Q1/12—Supports; Mounting means
- H01Q1/125—Means for positioning
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01Q—ANTENNAS, i.e. RADIO AERIALS
- H01Q1/00—Details of, or arrangements associated with, antennas
- H01Q1/12—Supports; Mounting means
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01Q—ANTENNAS, i.e. RADIO AERIALS
- H01Q3/00—Arrangements for changing or varying the orientation or the shape of the directional pattern of the waves radiated from an antenna or antenna system
Definitions
- the invention relates to actuating mechanisms and in particular to such mechanisms for use with parabolic reflector dishes.
- Parabolic reflector dishes are used to collect and focus energy carried by waves.
- the waves include radio waves for communications and solar radiation which is focused to produce heat for power generation or to drive a chemical reaction.
- Dishes are usually mounted on a structure with horizontal and vertical rotation axes providing altitude and azimuth tracking. It is known that placing the horizontal axis away from the centre of the dish places the dish closer to the ground when the dish is horizontal. With this configuration the vertical rotation axis is usually a kind of relatively simple turntable. The horizontal axis typically is more complicated.
- the actuating mechanism for rotating the dish about the horizontal axis is usually a hydraulic ram or a screw jack similar to that disclosed in US 2 096 050. Both these mechanisms tend to be expensive and so are relatively small to keep their size and cost down. The small size means the mechanism must be placed close to the horizontal axis, which cause small movements of the mechanism to produce large movements of the dish which makes accurate tracking difficult. Placing the mechanism close to the axis also produces large forces on the horizontal axis itself, the structure which supports it and the mechanism, requiring them to be of high strength and therefore cost.
- One method used to overcome the small sizes of current actuating mechanisms is to provide a 'walking ram' system which provides both altitude and azimuth tracking. This is achieved with a series of alternate extensions and contractions of appropriately mounted hydraulic rams. This system is however complicated and therefore expensive to manufacture and difficult to control.
- an actuator comprises:
- the actuator of the present invention With the actuator of the present invention, the elongation or contraction of the actuator is achieved by the relative rotation between the two parts. Accordingly, this allows very accurate control of the change in length of the actuator, since a large rotational movement results in a relatively small change in the length of the actuator. Furthermore, the actuator gives a high mechanical advantage, and therefore a relatively low force is able to overcome a much higher force resisting the change in length of the actuator. This allows the actuator to move heavy objects. Therefore, the present invention gives an actuator which is reliable, accurate and efficient. The actuator according to the present invention is also less expensive to manufacture than other known actuators.
- the actuator of the present invention can be made more easily and more cheaply than prior art actuators.
- the guideway is formed as a separate member to the cylinder.
- the formation of a separate guideway which is attached to the cylindrical member, for example by welding, is much easier and cheaper than providing a cylinder having a thick initial wall, and forming a guideway into the wall.
- the helical guideway is provided on the inner surface of the first generally cylindrical member, and the plurality of guide means are provided on the outer surface of the second generally cylindrical member.
- the helical guideway is provided on the outer surface of the second generally cylindrical member and the plurality of guide means are provided on the inner surface of the first cylindrical member.
- the helical guideway is in the form of a channel.
- the guide means are arranged to run inside the channel.
- the guide means include a first set of guide means which contact the base of the channel. This ensures the two generally cylindrical members remain generally co-axial.
- the guide means include a second set of guide means which engage the side walls of the channel. This prevents undesired axial movement between the two generally cylindrical members.
- the guide means are rotatable guide means such as wheels or rollers. These guide means are rotated as they run along the helical guideway. This results in low friction between the members acting against rotation, whilst ensuring close contact between the members to reduce any play, and thereby prevent jamming.
- a first set of rotatable guide means are arranged with an axis of rotation generally parallel to the base of the channel, and that the rotatable guide means have a width smaller than the width of the channel.
- the axis of rotation may also be generally perpendicular to the flanges or side walls of the channel.
- the first set of rotatable guide members are arranged to contact and run along the base of the helical guideway channel.
- a second set of the rotatable guide means are arranged with an axis of rotation generally parallel to the flanges. This axis of rotation may also be generally perpendicular to the base of the channel.
- Such rotatable guide means are arranged to contact and run along the side walls of the channel.
- the second set of rotatable guide means have a diameter less than the spacing between the opposed side walls of the channel.
- the second set of guide means are slightly offset from the helical path of the helical guideway such that some of the second set of guide means contact and run along one side wall of the channel, and the others of the second set of guide means contact and run along the opposite side wall of the channel.
- the generally helical guideway is formed as a projection from the side wall of the respective generally cylindrical member.
- one set of guide means are rotatable about an axis generally parallel to the side wall of the generally cylindrical member, and in use runs along the side wall of the generally cylindrical member.
- a strip typically of metal, may be provided on the side wall of the cylinder along which the guide means run. This protects the cylindrical member from wear.
- a second set of rotatable guide means may be provided which are rotatable about an axis generally parallel to the side faces of the projection, and which means are arranged to run along the side faces of the projection.
- some, or preferably all, of the components including the guide means and helical guideway are preferably formed of durable and advantageously corrosion resistant material. This helps prevent deterioration of the components which is especially important as these cannot be protected efficiently in other ways due to their relative movement.
- the radial position of the guide means are adjustable. This ensures centring of the first and second generally cylindrical members with respect to each other, and ensures that the guide means are in the optimum position to contact the helical guideway. This in turn ensures smooth running of the guide means on the guideway and thereby prevents jamming.
- the radial position of the guide means may be achieved by providing the guide means on a threaded shaft, in which case the distance between the side of the generally cylindrical member on which the guide means are mounted and the guide means themselves can be adjusted by rotation. In this case, the threaded shaft may be threaded directly into the side wall of the generally cylindrical member, and therefore the spacing of the guide means can be adjusted by rotation of the shaft.
- nuts may be provided on the threaded shaft, the nuts being provided on either side of the side wall of the generally cylindrical member to sandwich the side wall, and in this case adjustment of the nuts on the threaded shaft will adjust the effective length of the shaft and hence the spacing of the rotation guide member from the side wall of the generally cylindrical member.
- further guide means may be provided on the generally cylindrical member on which the helical guideway is provided, these guide means being arranged to contact the side wall of the other generally cylindrical member. This further assists in maintaining the coaxial arrangement between the generally cylindrical members and thereby prevents jamming and ensures smooth operation.
- These guide means are also preferably rotatable.
- further generally cylindrical members may be provided which are connected to the first or second cylindrical member by a similar arrangement of generally helical guide means and a plurality of guide members which are arranged in a generally corresponding helical fashion.
- this arrangement any desired number of coaxial components can be arranged in telescopic fashion to achieve any desired overall length of actuator.
- the actuator according to the present invention may advantageously be used for movement of a dish, such as a parabolic reflector dish for the collection and/or focusing of energy. Due to the accurate control of the actuator, and the good mechanical advantage, the actuator of the present invention may be provided close to the axis about which the dish is required to turn. However, the reduced cost of the actuator of the present invention compared to prior actuator means that larger actuators can be formed for the same cost as smaller prior actuators, and therefore the actuator can be provided further from the axis about which the dish is to rotate. This enables a reduction in the force required to turn the dish, and as the actuation is further from the axis, allowing greater accuracy and control and reducing the strength and therefore cost of axis and the structure supporting it.
- FIG. 1 An embodiment of a dish actuating mechanism shown in Figure 1 has enlarged cross sections of outlined areas 2, 4 and 6 shown in Figures 2, 3 and 4 respectively.
- This embodiment will now be described with reference to Figures 1-5. It comprises a large diameter cylinder 8, the diameter of which is approximately 1 metre with 12 mm thick walls. Fixed inside this cylinder is a length of rolled steel channel 10, bent to a helical shape shown in Figure 5. This channel 10 is bolted or welded to the cylinder 8. The sectional dimensions of this channel are 40 mm x 20 mm.
- the outer diameter of the helix is equal to or slightly less than the inner diameter of cylinder 8, so that it can just fit inside the cylinder and be fixed to the inner wall of the cylinder.
- the pitch of the helix is about 100 mm.
- a further cylinder 12 has on outer diameter small enough to fit inside and clear the inner diameter of the helical channel.
- the cylinder 12 has a diameter of about 900 mm.
- On the bottom of cylinder 12 are holes 14 arranged in helical pattern of the same pitch as that of the helix of channel 10. Through some, but not all, of these holes are bolts 16 held in place with nuts 18 as shown in Figure 2.
- Bolts 16 have a reduced diameter shank 20 at the end of the threaded portion.
- a wheel, roller or bearing 22 On this shank is a wheel, roller or bearing 22. This wheel or bearing is of slightly smaller diameter than the distance between the flanges of channel 10.
- the remaining holes 14 in cylinder 12 each contain a threaded rod 24, shown in detail in Figure 3. This rod is held in place with nuts 26 on either side of cylinder 12. Fixed to the outside end of rod 22 is wheel or bearing 28 which has an axis of rotation parallel to the pitch of helix of channel 10. This wheel runs on the bottom of channel 10.
- a further set of holes 30 are positioned near the top of cylinder 8 in a plane parallel to the level top of the cylinder.
- these holes are rods with holes on their ends identical to rods 24 and wheels 28, as shown in Figure 4.
- these wheels are on the inside of cylinder 8 and run on the outside of cylinder 12.
- a helical strip of steel may be provided on the outside of the cylinder along which the wheels run to prevent wear of the cylinder 12.
- the guide means could be welded or otherwise secured.
- cylinder 8 is rotated whilst the rotation of cylinder 12 is prevented.
- Wheels 22 turn inside helical channel 10 as cylinder 8 rotates, making cylinder 12 extend from the inside of cylinder 8.
- Wheels on rods 24 in holes 30 run on the outside of cylinder 8 and hold cylinder 12 in the centre of cylinder 8 during extension, reducing the chances of the mechanism buckling.
- Threaded rods 24 are used to provide adjustment of wheels 22 in the radial direction of the cylinders. This reduces the cost of the cylinders by allowing standard sizes of cylinder to be used.
- Bolts 16 could also be replaced by threaded rods held in place with nuts on either side to allow for the radial adjustment of wheels 28 to match the diameter of the cylinder.
- the load lifted by the mechanism is therefore transferred from cylinder 12 to cylinder 8 through channel 10 and wheels 22 to place bolts 16 in shear.
- the depth of the bottom portion of cylinder 12 which contains holes 14, bolts 16 and wheels 22 is determined by the number of bolts 16 required to provide sufficient strength to carry the load placed on the actuating mechanism.
- wheels 22 have sufficient clearance to turn between the flanges of channel 10. Thus if the load in the mechanism changes from compression to tension, then the mechanism will extend until this wheel touches the top flange of channel 10, causing excessive movement of the dish and loss of accurate tracking. This can be overcome by arranging holes 14 and wheels 22 on cylinder 12 as shown in Figure 6.
- Figure 6 shows a second embodiment with holes 14 staggered so as to place some of wheels 22 in contact with the bottom flange of the channel and others in contact with the top.
- some wheels are already in contact with either flange of the channel, so the mechanism cannot extend.
- This could also be achieved by using much smaller wheels 22 and placing them on bolts through holes 14 with one hole positioned approximately vertically above the other to give a pair of wheels one above the other, as in Figure 7.
- the wheels may or may not be in contact with each other.
- wheels 28 are tapered themselves to match the taper 32 of channel 38.
- rod 36 is bent to place wheel 22 on an angle which matches the taper of channel 38.
- bolts 16 are replaced with threaded rods 36 similar to rods 24 to allow for adjustment of the wheels to fit the cylinders and the channel.
- the tapered channel and wheels 32 or 34 hold cylinder 12 in the centre of cylinder 8 because movement of cylinder 12 in any lateral direction would try to push wheels 32 or 34 deeper into the channel where the space between the flanges is smaller and the wheels cannot fit. For this reason staggered wheels or two wheels as shown in Figures 6 and 7 must be used with this embodiment. If one wheel were used, as in the first embodiment, without wheels 28, it would have to be tapered similar to wheels 32, and sideways movement of cylinder 12 inside cylinder 8 would cause wheel 22 to jam in the taper and not turn.
- Channels 10 can be replaced with other shapes of cross section such as angles of rolled steel bars.
- the helical members are in pairs with wheels 22 running between each pair.
- the vertical distance between the members forming each pair need not be the same as the distance between the pairs themselves.
- the helical guideway is preferably formed of stainless steel, as are the other components.
- the guideway can include a simple projection, and in this case the wheels or other guide means run along the sides of the projection and the side of the cylinder.
- the extension of the mechanism can be increased if it is made telescopic.
- a further cylinder with wheels attached to it in a similar manner to those attached to cylinder 12 would be placed inside cylinder 12.
- the diameter of this cylinder may be 800 mm.
- the wheels similar to wheels 22 and 28 attached to this smallest diameter cylinder would interact with a helical channel similar to channel 10.
- the outer diameter of this channel would be small enough to just fit inside and be fixed inside cylinder 12.
- a form of stop would be needed at the top of cylinders 8 and 12.
Landscapes
- Transmission Devices (AREA)
- Valve Device For Special Equipments (AREA)
- Fluid-Damping Devices (AREA)
- Fluid-Driven Valves (AREA)
- Actuator (AREA)
- Surgical Instruments (AREA)
Claims (22)
- Ein Antrieb bestehend auseinem ersten allgemein zylindrischen Bauteil (8);einem zweiten allgemein zylindrischen Bauteil, das wenigstens teilweise darin aufgenommen wird und mit dem ersten allgemein zylindrischen Bauteil (12) koaxial ist;einer allgemein spiralförmigen Führungsbahn (10), die an einem der ersten und zweiten allgemein zylindrischen Bauteile bereitgestellt ist; undeiner Vielheit von Führungsmitteln (14, 16, 18, 20, 22, 24, 26, 28), die in einer allgemein entsprechenden spiralförmigen Anordnung an den anderen der ersten und zweiten allgemein zylindrischen Bauteile (20) bereitgestellt werden und so angeordnet sind, dass sie der spiralförmigen Führungsbahn (10) entlang laufen,
- Ein Antrieb nach Anspruch 1, bei dem die Führungsbahn als ein vom Zylinder separates Bauteil geformt ist.
- Ein Antrieb nach Anspruch 1 oder Anspruch 2, bei dem die spiralförmige Führungsbahn an der Innenfläche des ersten allgemein zylindrischen Bauteils bereitgestellt ist, und die Vielheit von Führungsmitteln an der Außenfläche des zweiten allgemein zylindrischen Bauteils bereitgestellt sind.
- Ein Antrieb nach Anspruch 1 oder Anspruch 2, bei dem die spiralförmige Führungsbahn an der Außenfläche des zweiten allgemein zylindrischen Bauteils bereitgestellt ist und die Vielheit von Führungsmitteln auf der Innenfläche des ersten zylindrischen Bauteils bereitgestellt ist.
- Ein Antrieb nach einem beliebigen der vorhergehenden Ansprüche, bei dem die spiralförmige Führungsbahn die Form eines U-Profils hat.
- Ein Antrieb nach Anspruch 5, bei dem die Führungsmittel angeordnet sind im U-Profil zu laufen.
- Ein Antrieb nach Anspruch 6, bei dem die Führungsmittel einen ersten Satz Führungsmittel einschließen, die die Basis des U-Profils berühren.
- Ein Antrieb nach Anspruch 7, bei dem die Führungsmittel einen zweiten Satz Führungsmittel einschließen, die in die Seitenwänden des U-Profils eingreifen.
- Ein Antrieb nach einem beliebigen der vorhergehenden Ansprüche, bei dem die Führungsmittel drehbare Führungsmittel wie beispielsweise Räder oder Rollen sind.
- Ein Antrieb nach Anspruch 5, oder irgendwelchen davon abhängigen Ansprüchen, bei dem ein erster Satz drehbarer Führungsmittel mit einer Drehachse angeordnet sind, die allgemein parallel zur Basis des U-Profils ist, und bei dem die drehbaren Führungsmittel eine Breite haben, die kleiner als die Breite des U-Profils ist.
- Ein Antrieb nach Anspruch 10, bei dem der erste Satz von drehbaren Führungsmitteln angeordnet ist die Basis der spiralförmigen Führungsbahn zu berühren und entlang zu laufen.
- Ein Antrieb nach Anspruch 10 oder 11, bei dem ein zweiter Satz der drehbaren Führungsmittel mit einer Drehachse angeordnet ist, die allgemein parallel zu den Flaschen ist.
- Ein Antrieb nach Anspruch 12, bei dem der zweite Satz drehbarer Führungsmittel einen geringeren Durchmesser als der Abstand zwischen den entgegengesetzten Seitenwänden des U-Profils hat.
- Ein Antrieb nach Anspruch 12 oder 13, bei dem der zweite Satz von drehbaren Führungsmitteln vom spiralförmigen Pfad der spiralförmigen Führungsbahn so versetzt sind, dass einige des zweiten Satzes von Führungsmitteln eine Seitenwand des U-Profils berühren und entlang laufen und die anderen des zweiten Satzes von Führungsmitteln die entgegengesetzte Seitenwand des U-Profils berühren und entlang laufen.
- Ein Antrieb nach einem beliebigen der Ansprüche 1 bis 4, bei dem die allgemein spiralförmige Führungsbahn als ein Vorsprung aus der Seitenwand des jeweiligen allgemein zylindrischen Bauteils geformt ist.
- Ein Antrieb nach Anspruch 15, bei dem ein Satz von Führungsmitteln um eine Achse drehbar ist, die allgemein parallel zur Seitenwand des allgemein zylindrischen Bauteils ist.
- Ein Antrieb nach Anspruch 16, bei dem ein zweiter Satz drehbarer Führungsmittel bereitgestellt sein kann, die um eine Achse drehbar sind, die allgemein parallel zu den Seitenflächen des Vorsprungs ist und welche Mittel angeordnet sind den Seitenflächen des Vorsprungs entlang zu laufen.
- Ein Antrieb nach Anspruch 17, bei dem einige des zweiten Satzes von Führungsmitteln eine Seitenfläche des Vorsprungs berühren und entlang laufen und andere des zweiten Satzes von Führungsmitteln die andere Seitenfläche des Vorsprungs berühren und entlang laufen.
- Ein Antrieb nach einem beliebigen der vorhergehenden Ansprüche, bei dem die radiale Position der Führungsmittel verstellbar ist.
- Ein Antrieb nach Anspruch 19, bei dem die radiale Position der Führungsmittel durch Bereitstellen der Führungsmittel auf einer Gewindewelle erzielt wird, in welchem Fall der Abstand zwischen der Seite des allgemein zylindrischen Bauteils, auf dem die Führungsmittel montiert sind und den Führungsmitteln selbst durch Drehung verstellt werden kann.
- Ein Antrieb nach einem beliebigen der vorhergehenden Ansprüche, bei dem Führungsmittel auf dem allgemein zylindrischen Bauteil bereitgestellt sind, auf dem die spiralförmige Führungsbahn bereitgestellt ist, wobei diese Führungsmittel angeordnet sind die Seitenwand des anderen allgemein zylindrischen Bauteils zu berühren.
- Ein Antrieb nach einem beliebigen der vorhergehenden Ansprüche, der weiter allgemein zylindrische Bauteile, die durch eine ähnliche Anordnung von allgemein spiralförmigen Führungsmitteln mit dem ersten oder zweiten Seitenbauteil verbunden sind und eine Vielheit von Führungsmitteln, die in einer allgemein entsprechenden spiralförmigen Art und Weise angeordnet sind, umfasst.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GBGB9824550.9A GB9824550D0 (en) | 1998-11-09 | 1998-11-09 | Actuator |
GB9824550 | 1998-11-09 | ||
PCT/GB1999/003687 WO2000028619A1 (en) | 1998-11-09 | 1999-11-05 | Cylindrical actuator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1129505A1 EP1129505A1 (de) | 2001-09-05 |
EP1129505B1 true EP1129505B1 (de) | 2004-02-04 |
Family
ID=10842126
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99954154A Expired - Lifetime EP1129505B1 (de) | 1998-11-09 | 1999-11-05 | Zylindrischer antrieb |
Country Status (10)
Country | Link |
---|---|
EP (1) | EP1129505B1 (de) |
AT (1) | ATE259102T1 (de) |
AU (1) | AU773380B2 (de) |
DE (1) | DE69914624D1 (de) |
ES (1) | ES2215408T3 (de) |
GB (1) | GB9824550D0 (de) |
MA (1) | MA25269A1 (de) |
MX (1) | MXPA01004273A (de) |
PT (1) | PT1129505E (de) |
WO (1) | WO2000028619A1 (de) |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2096050A (en) * | 1934-06-25 | 1937-10-19 | Auto Specialties Mfg Co | Lifting jack |
GB2266996A (en) * | 1992-05-01 | 1993-11-17 | Racal Res Ltd | Antenna support providing movement in two transverse axes. |
JP2746200B2 (ja) * | 1995-04-26 | 1998-04-28 | 日本電気株式会社 | アンテナ駆動装置 |
-
1998
- 1998-11-09 GB GBGB9824550.9A patent/GB9824550D0/en not_active Ceased
-
1999
- 1999-11-05 AT AT99954154T patent/ATE259102T1/de not_active IP Right Cessation
- 1999-11-05 MX MXPA01004273A patent/MXPA01004273A/es not_active IP Right Cessation
- 1999-11-05 PT PT99954154T patent/PT1129505E/pt unknown
- 1999-11-05 DE DE69914624T patent/DE69914624D1/de not_active Expired - Lifetime
- 1999-11-05 WO PCT/GB1999/003687 patent/WO2000028619A1/en active IP Right Grant
- 1999-11-05 ES ES99954154T patent/ES2215408T3/es not_active Expired - Lifetime
- 1999-11-05 AU AU10588/00A patent/AU773380B2/en not_active Ceased
- 1999-11-05 EP EP99954154A patent/EP1129505B1/de not_active Expired - Lifetime
-
2001
- 2001-06-08 MA MA26227A patent/MA25269A1/fr unknown
Also Published As
Publication number | Publication date |
---|---|
MXPA01004273A (es) | 2002-06-04 |
AU1058800A (en) | 2000-05-29 |
GB9824550D0 (en) | 1999-01-06 |
WO2000028619A1 (en) | 2000-05-18 |
DE69914624D1 (de) | 2004-03-11 |
EP1129505A1 (de) | 2001-09-05 |
MA25269A1 (fr) | 2001-10-01 |
AU773380B2 (en) | 2004-05-27 |
ES2215408T3 (es) | 2004-10-01 |
ATE259102T1 (de) | 2004-02-15 |
PT1129505E (pt) | 2004-06-30 |
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