EP0741247B1 - Verstellring - Google Patents
Verstellring Download PDFInfo
- Publication number
- EP0741247B1 EP0741247B1 EP96106866A EP96106866A EP0741247B1 EP 0741247 B1 EP0741247 B1 EP 0741247B1 EP 96106866 A EP96106866 A EP 96106866A EP 96106866 A EP96106866 A EP 96106866A EP 0741247 B1 EP0741247 B1 EP 0741247B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- adjusting ring
- ring
- compressor
- segments
- adjusting
- 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
- 239000002131 composite material Substances 0.000 claims description 21
- 239000000835 fiber Substances 0.000 claims description 19
- 230000008859 change Effects 0.000 claims description 12
- 239000004744 fabric Substances 0.000 claims description 12
- 239000000969 carrier Substances 0.000 claims description 6
- 230000001360 synchronised effect Effects 0.000 claims description 6
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 5
- 230000007423 decrease Effects 0.000 claims description 5
- 238000009413 insulation Methods 0.000 claims description 4
- 229910052782 aluminium Inorganic materials 0.000 claims description 3
- 125000006850 spacer group Chemical group 0.000 claims description 3
- 239000003365 glass fiber Substances 0.000 claims description 2
- 230000004075 alteration Effects 0.000 claims 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims 1
- 239000004411 aluminium Substances 0.000 claims 1
- 229910052799 carbon Inorganic materials 0.000 claims 1
- 230000003247 decreasing effect Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 description 21
- 239000000463 material Substances 0.000 description 11
- 230000000694 effects Effects 0.000 description 7
- 239000007769 metal material Substances 0.000 description 7
- 229920000049 Carbon (fiber) Polymers 0.000 description 6
- 239000004917 carbon fiber Substances 0.000 description 6
- 230000002349 favourable effect Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 5
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 5
- 230000000284 resting effect Effects 0.000 description 3
- 239000000956 alloy Substances 0.000 description 2
- 229910045601 alloy Inorganic materials 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000009529 body temperature measurement Methods 0.000 description 1
- 238000005352 clarification Methods 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000011152 fibreglass Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000010936 titanium Substances 0.000 description 1
- 229910052719 titanium Inorganic materials 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/21—Utilizing thermal characteristic, e.g., expansion or contraction, etc.
- Y10T403/217—Members having different coefficients of expansion
Definitions
- the present invention relates to an adjusting ring for synchronous change of the angle of attack of guide vanes of a compressor that has several bearing points for storage on a housing of the compressor.
- Such an adjustment ring E.g. known from published patent application DE 42 16 033 A1.
- Such adjustment rings are used in particular in aeronautical engineering the compressor by adjusting the guide vanes adapt to different operating conditions, to ensure optimal operation of the compressor under different To enable requirement profiles.
- a simple replacement of the metallic by non-metallic Materials while maintaining the design principle of the adjustment ring is usually at least for the hot area, not feasible because the in Non-metallic materials generally come into consideration significantly lower coefficient of thermal expansion than the metallic one Have compressor housing and therefore the adjusting ring in the event of temperature increases occurring during the operation of the compressor on the expanding compressor housing would shrink, so that the adjusting ring no longer would be displaceable relative to the compressor housing and thus no longer for the synchronous change of the angle of attack Guide blades of the compressor could serve.
- the invention was therefore based on the object of an adjusting ring to create using at least some of the materials low thermal expansion coefficient can be manufactured and yet temperature compatible with a metallic compressor housing is.
- This task is at the beginning of an adjustment ring mentioned type solved in that the adjusting ring in each case arranged between two adjacent support points includes curved ring segments, the curvature of one Increasing the temperature of the ring segments decreases and leads to a change in the geometry of the adjusting ring So that the Support points between the ring segments in the radial direction to be moved outwards.
- the concept of the invention has the advantage that a change in the geometry of the adjustment ring the support points the same far enough in the radial direction to the outside be moved to shrink the adjustment ring to prevent the compressor housing.
- a homogeneous thermal expansion of the adjustment ring is for thermal expansion compatibility between the adjusting ring and the compressor housing not necessary, so that the adjustment ring with the required Structural rigidity at least partially from non-metallic Materials with very small, disappearing or even negative coefficient of thermal expansion and sufficient Stiffness can be made.
- the thermal expansion compatibility between an annular or tubular support and one at support points on the carrier, surrounding it or supported by the same ring-shaped or tubular Element that is a material with less thermal expansion than that of the material of the carrier comprises to produce that the carried element along its circumference in Ring or arranged between two support points Pipe segments is divided, the curvature at an increase the temperature of the worn element decreases so that the bearing points shifted outwards in the radial direction become.
- the worn element comprises a material with greater thermal expansion than that of the material of the carrier, that the curvature of the ring or tube segments at an increase in temperature increases so that the bearing points can be moved inwards in the radial direction.
- the adjustment ring advantageously comprises at least three Ring segments to a sufficient number of support points for mounting the adjustment ring on the compressor housing to obtain.
- the geometry change effect decreases with one growing number of ring segments into which the adjusting ring is divided, while the manufacturing cost of the adjusting ring increase, so it is advantageous if the Adjustment ring comprises a maximum of 16 ring segments.
- Embodiments of the adjusting ring are particularly preferred with six to ten ring segments.
- the curvature of the ring segments when the temperature rises can advantageously be achieved in that the ring segments one each arranged on the outside of the adjusting ring Circumferential part that has a first coefficient of thermal expansion in the circumferential direction of the adjusting ring, and one arranged on the inside of the adjusting ring Beam that has a second coefficient of thermal expansion in Has circumferential direction of the adjusting ring, include, wherein the second coefficient of thermal expansion is greater than that first coefficient of thermal expansion and the peripheral part and the beam of each ring segment fixed to each other are that with an increase in the temperature of the ring segments their curvature decreases.
- the required geometry change of the adjusting ring is replaced by one of Temperature measuring strips known bimetallic effect similar Effect caused by an increase in temperature of the ring segments. At least the peripheral parts of the ring segments can be made from one non-metallic material.
- the beams should be on the outside be arranged on the inside of the adjusting ring.
- the required structural rigidity of the adjusting ring also favorable if the peripheral parts at least partially consist of a fiber composite material.
- This composite material can be, for example, a carbon fiber composite material or fiberglass composite his.
- any material can be used for the beams, which has a significantly larger coefficient of thermal expansion than the material of the peripheral parts, in particular a Fiber composite material with a corresponding coefficient of thermal expansion.
- the adjustment ring is particularly preferred, in which the beams at least partially made of aluminum, especially one Aluminum powder alloy.
- each ring segment of the adjustment ring can manufactured as individual parts and only when the adjusting ring is assembled be joined together.
- peripheral parts of the ring segments as two circumferential half rings are formed because in this way an advantageous compromise between assembly and manufacturing costs is achieved.
- Another embodiment of the invention relates to a compressor with a compressor housing, guide vanes and one Adjustment ring for synchronous change of the angle of attack Guide vanes, in which the adjusting ring after an adjusting ring is one of claims 1 to 12.
- the compressor includes sliding shoes, on which the adjustment ring is mounted and one each Have sliding surface for sliding on the compressor housing.
- sliding shoes can also be used to save weight advantageously made of a fiber composite material consist.
- the compressor housing includes adjusting ring carrier, which each have a sliding surface.
- the compressor both Includes sliding shoes as well as adjusting ring carrier, the Sliding surfaces of the sliding shoes on the sliding surfaces of the adjusting ring carrier can slide off.
- the adjustment ring carrier advantageously consists of a fiber composite material to save additional weight.
- the adjusting ring carrier they have a layer structure in which in a axial direction of the compressor dense fabric layers and less dense spacings follow each other. Through in the Cavities contained spacing layers is the weight of the Adjustment ring carrier reduced in a particularly effective manner.
- the fabric layers have a negative coefficient of thermal expansion in the radial direction of the compressor exhibit.
- the adjustment ring carrier is shortened with a temperature increase in the radial Direction of the compressor and thus partially compensate for the Expansion of the compressor housing. That is enough a smaller displacement of the support points of the adjustment ring in a radial outward direction to ensure thermal expansion compatibility between the adjusting ring and the compressor housing to ensure.
- a particularly large negative coefficient of thermal expansion the fabric layers in the radial direction can be reach when the fabric layers fibers that under one Angle of approximately plus 30 ° against the radial direction of the Compressor are aligned, and fibers under one An angle of approximately minus 30 ° to the radial direction of the Compressor are aligned include.
- each has a heat insulation layer between the compressor housing and each of the adjusting ring carriers is arranged.
- the thermal expansion coefficient of Circumferential parts and beams of the ring segments so on top of each other and matched to the length and curvature of the ring segments are that the support points of the adjusting ring at a temperature increase essentially the same distance be moved radially outwards like the adjusting ring carrier.
- FIG. 1 An adjusting ring 10 according to the invention shown in FIG. 1 a compressor designated as a whole by 11 several, for example eight, essentially circular arcs Ring segments 12, two of which are adjacent to each other Ring segments 12 are shown enlarged in Fig. 2.
- Each of the ring segments 12 includes one on the outside of the Adjustment ring 10 arranged peripheral part 14 in the form of a Circular ring section and one on the inside of the Circumferential part 14, for example on four contact surfaces 16, fixed beam 18, the inside of the Circumferential part 14 to an axis 20 of the adjusting ring 10 projects.
- the peripheral parts 14 are made of such a material that they along the circumferential direction of the adjusting ring 10 a small, vanishing or even negative coefficients of thermal expansion exhibit.
- peripheral parts 14 can also be made of a glass fiber composite material are manufactured.
- the coefficient of thermal expansion for the expansion along the Ring circumference is clearly in the positive range however, only around half of the coefficient of thermal expansion of the metallic compressor housing.
- Adjacent peripheral parts 14 are formed integrally with one another and form a circumferential half ring 22.
- the two so resulting circumferential half rings 22 are at two connection points 24 (only one of which can be seen in FIG. 1) fixed and thus form a complete, closed Circumferential ring 26.
- Each of the beams 18 is substantially in the shape of a Section of a hollow ring profile with a rectangular cross section on, with the respective peripheral part 14 facing Sidewall of the profile the same height as that Has peripheral part 14 and is flush with the same.
- everyone Beam 18 is chamfered at both ends and faces Weight saving, for example, three between the contact surfaces 16 arranged recesses 28.
- Each beam 18 has in the area of each of its, for example four, contact surfaces 16 each have a radial through hole 30, each with a corresponding radial through bore 32 in the associated peripheral part 14 is aligned, as shown in Fig. 3.
- each through hole 30 in each of the beams 18 is one arranged with an internally threaded thread insert 34, in the one with an external thread hollow cylindrical Guide bush 36 is screwed into the through holes 30 and 32 in the beam 18 and in the associated Perforated part 14 and at her in the radial direction outer end carries a wreath 38 on the outside of the peripheral part 14 rests.
- an internally threaded thread insert 34 in the one with an external thread hollow cylindrical Guide bush 36 is screwed into the through holes 30 and 32 in the beam 18 and in the associated Perforated part 14 and at her in the radial direction outer end carries a wreath 38 on the outside of the peripheral part 14 rests.
- the beams 18 are made of a material that at least in the circumferential direction of the adjusting ring 10 Has coefficient of thermal expansion.
- an aluminum powder alloy can be used which also have sufficient flexural rigidity the ring segments 12 guaranteed even at high temperatures.
- the through holes 32 in the peripheral parts 14 are longitudinal of the circumference of the circumferential parts 14 are arranged equidistantly from one another.
- an essentially cuboid bearing block 42 is arranged on the inside of the circumferential ring 26 that one the support block 42 in the radial direction of the compressor 11 threaded hole 44 in the middle with the Through hole 40 in the circumferential ring 26 is aligned, as in Fig. 4 shown.
- each support block 42 has two projections 45 on the opposite directions from the Support block 42 in the circumferential direction of the adjusting ring 10 protrude and both on the inside of a peripheral part 14 as well as on a beam 18.
- an external thread hollow cylindrical guide bush 36 screwed in the through hole 40 penetrates in the circumferential ring 26 and with their ring 38 rests on the outside of the circumferential ring 26.
- the area of the support block lying in the radial direction 42 is in a substantially cuboid recess 46 of a slide shoe 48 with little play in guided in the radial direction.
- the adjusting ring is supported on the outer surfaces of the bearing blocks 42 10 on the slide shoe 48.
- the bearing blocks 42 thus represent support points of the adjusting ring 10.
- a facing away from the support block 42 in the radial direction internal concave sliding surface 50 of the sliding block 48 has the shape of a section of an annular surface on, is provided with a sliding coating and lies on a correspondingly curved convex sliding surface 52 one referred to as centralizer 54 adjusting ring carrier.
- centralizer 54 adjusting ring carrier There Amount and direction of curvature of the concave sliding surface 50 of the sliding block 48 on the one hand and the convex sliding surface 52 of the centralizer 54 match each other, everyone can Slide shoe 48 on the associated centralizer 54 in the circumferential direction of the adjusting ring 10 slide off.
- Each centralizer 54 has an upper and a lower, each have an essentially trapezoidal guide plate 56, between which the beams 18 of each Centralizer 54 adjacent ring segments 12 at one Movement of the adjusting ring 10 along its circumference become.
- the clear distance between the two Guide plates 56 each centralizer slightly larger than that Height of beams 18.
- each of the centralizers 54 has a stepped, central one radial through bore 58, the one in the radial direction outer section 60 and one in narrower portion 62 in the radial direction includes.
- the narrower portion 62 of the stepped through hole 58 opens on a base area lying in the radial direction 64 of the centralizer 54, which is on an essentially cuboid isolation block 66, which in turn is from an essentially hollow cylindrical, coaxial to the adjusting ring 10 arranged compressor housing 68 is worn.
- the centralizer 54 becomes perpendicular to the guide plates 56 penetrated by a further through bore 69, which the stepped through bore 58 intersects and into which cylindrical pin 70 is inserted so that a central radial through hole of the same with the narrower section 62 of the stepped through bore 58 is aligned.
- Each centralizer 54 is by means of a screw 71 which the Through hole in pin 70, the narrower section 62 of the stepped through bore 58 and an aligned therewith Passed through hole in the insulation block 66, in a radial threaded hole 72 screwed into the compressor housing 68 is and with her head against the pin 70, fixed.
- the pin 70 ensures good force coupling into the Centralizer 54 reached.
- the centralizers 54 can be made of carbon fiber composite material be made so that they have a low positive, one vanishing or a negative coefficient of thermal expansion exhibit.
- Fig. 5 One to achieve a negative coefficient of thermal expansion in the radial direction and a low weight advantageous layer structure of the centralizer material is in Fig. 5 shown.
- Compressor dense fabric layers 73 and less dense Spacer layers 74 which are oriented transversely to the fabric layers 73 Include webs 75 of spacer fabric, one on top of the other.
- the fabric layers 73 include fibers that are at an angle of approximately plus 30 ° against the radial direction of the compressor are arranged and fibers at an angle of approximately minus 30 ° against the radial direction of the compressor are aligned in terms of amount as possible large negative thermal expansion coefficient of the Centralizers 54 in the radial direction of the compressor receive.
- Fig. 5 are the radial direction of the compressor through the Arrow 73a and the directions in which the fibers of the fabric layers 73 are shown by arrows 73b and 73c.
- the insulation blocks 66 can be made of a high temperature resistant Be made of plastic, which has a high thermal resistance has, so that the compressor housing 68th during the operation of the compressor via the centralizer 54 transferred to the adjusting ring 10 and thus the heat thermal load on the adjusting ring 10 is as low as possible is held.
- each of the vanes 78 points one outwards in the radial direction protruding adjusting shaft 80, each having a radial Through hole 82 in the compressor housing 68 and one each arranged on the outer wall of the compressor housing 68 to the adjusting shaft 80 passes through coaxial bearing bushing 84 and at its free end rotatably with one perpendicular to the axis the adjustment shaft 80 aligned adjustment arm 86 connected is.
- Each of the adjustment arms 86 carries one at its free end Articulation pin 88 projecting inwards in the radial direction, the one in each of the guide bushings 36 of the circumferential ring 26 is stored. This creates an articulated connection between the adjusting ring 10 on the one hand and the guide vane grille 76 on the other hand.
- the angle of attack Guide vanes 78 of the compressor synchronously with the respective Adjust operating conditions. Due to the circumferential ring 26
- the adjustment ring 10 has a carbon fiber composite material high rigidity and strength in the circumferential direction, while the aluminum beams 18 have high flexural rigidity ensure the adjustment ring 10.
- the operating temperature of the compressor is considerably higher the room temperature.
- the compressor housing 68 expands therefore until the operating temperature is reached, whereby arranged on the circumference of the compressor housing 68 Centralizer 54 and the on the convex sliding surfaces 52 of the Centralizer 54 overlying slide shoes 48 in the radial direction to be moved outwards.
- the support points for the support blocks 42 forming the adjusting ring 10 have to a corresponding distance in the radial direction to the outside hike to prevent the shoes 48 from being too strong the centralizer 54 is pressed against the convex sliding surfaces 52 be so that sliding of the concave sliding surfaces 50 on the convex sliding surfaces 52 and thus a twisting of the adjusting ring 10 difficult or even impossible in the circumferential direction is made.
- Such thermal expansion compatibility between the compressor housing 68 and the adjusting ring 10 would be exclusive to one adjustment ring made of fiber composite materials 10 unreachable because of fiber composite materials in the direction their fibers, which are expediently in the circumferential direction of the adjusting ring 10 are aligned, much smaller Have coefficients of thermal expansion than usual metallic materials from which the compressor housing 68 consists.
- Fig. 6 shows a highly schematic and simplified Top view of the adjusting ring 10 according to the invention eight ring segments 12 is composed, two each Adjacent ring segments 12 at one another at a support point 90 limits.
- the eight ring segments 12 each essentially have the shape of an eighth circle with a radius R 1 . Consequently, the adjusting ring 10 at this temperature is a circle with the radius R 1 , from the center 92 of which the bearing points 90 are each at a distance R 1 .
- Fig. 7 shows the highly schematic adjustment ring 10 Fig. 6 at a well above the resting temperature Operating temperatur.
- the ring segments 12 Due to the different coefficients of thermal expansion of the Beams 18 and the peripheral parts 14 are the ring segments 12 less curved at the operating temperature. For clarification the curvature of the ring segments 12 are in Fig. 7 shown as straight lines, which is greatly exaggerated is, however, the significant geometry change effect on most clearly shows.
- the adjusting ring 10 no longer corresponds to an exact circle with a radius R 1 , but rather the adjusting ring 10 is deformed into an octagon, the corners of which are formed by the bearing points 90 between the ring segments 12.
- the support points 90th (the support blocks 42) by substantially the same amount can be moved in the radial direction outwards like that Slip shoes 48, making thermal expansion compatibility between the adjusting ring 10 and the compressor housing 68 is guaranteed.
- the adjustment ring 10 both at rest and at maximum operating temperature and at all temperatures in between easily by sliding the concave sliding surfaces 50 of the Sliding shoes 48 on the convex sliding surfaces 52 of the Centralizer 54 along its circumference with respect to the compressor housing 68 are rotated so that in any operating state an exactly synchronous change in the angle of attack of the guide vanes 78 is possible.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
Description
- Fig. 1
- eine perspektivische Darstellung eines auf einem Verdichtergehäuse gelagerten erfindungsgemäßen Verstellrings zur synchronen Änderung des Anstellwinkels von Leitschaufeln des Verdichters;
- Fig. 2
- eine Draufsicht auf zwei einander benachbarte Ringsegmente des Verstellrings aus Fig. 1 mit einer dazwischen liegenden Auflagerstelle;
- Fig. 3
- einen Schnitt durch den Verstellring längs der Mittelebene desselben im Bereich I der Fig. 2;
- Fig. 4
- einen Schnitt durch den Verstellring und das Verdichtergehäuse längs der Mittelebene des Verstellrings im Bereich II der Fig. 2;
- Fig. 5
- eine schematische perspektivische, teilweise aufgebrochene Darstellung eines Verstellringträgers (Centralizers);
- Fig. 6
- eine stark schematisierte Draufsicht auf einen erfindungsgemäßen Verstellring bei einer Ruhetemperatur; und
- Fig. 7
- eine stark schematisierte Draufsicht auf den Verstellring aus Fig. 3 bei einer oberhalb der Ruhetemperatur liegenden Betriebstemperatur.
Claims (22)
- Verstellring zur synchronen Änderung des Anstellwinkels von LeitLeitschaufeln eines Verdichters, der mehrere Auflagerstellen zur Lagerung auf einem Verdichtergehäuse des Verdichters aufweist,
dadurch gekennzeichnet, daß der Verstellring (10) jeweils zwischen zwei einander benachbarten Auflagerstellen (42, 90) angeordnete gekrümmte Ringsegmente (12) umfaßt, deren Krümmung bei einer Erhöhung der Temperatur der Ringsegmente (12) abnimmt und zu einer Änderung der Geometrie des Verstellrings (10) führt, so daß die Auflagerstellen (42, 90) zwischen den Ringsegmenten (12) in radialer Richtung nach außen verschoben werden. - Verstellring nach Anspruch 1, dadurch gekennzeichnet, daß der Verstellring (10) mindestens drei Ringsegmente (12) umfaßt.
- Verstellring nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Verstellring (10) höchstens sechzehn Ringsegmente umfaßt.
- Verstellring nach einem der voranstehenden Ansprüche,
dadurch gekennzeichnet, daß die Ringsegmente (12) jeweils ein an der Außenseite des Verstellrings (10) angeordnetes Umfangsteil (14), das einen ersten Wärmeausdehnungskoeffizienten in Umfangsrichtung des Verstellrings (10) aufweist, und einen an der Innenseite des Verstellringes (10) angeordneten Unterzug (18), der einen zweiten Wärmeausdehnungskoeffizienten in Umfangsrichtung des Verstellrings (10) aufweist, umfassen, wobei der zweite Wärmeausdehnungskoeffizient größer ist als der erste Wärmeausdehnungskoeffizient und das Umfangsteil (14) und der Unterzug (18) jeden Ringsegmentes (12) so aneinander festgelegt sind, daß bei einer Erhöhung der Temperatur der Ringsegmente (12) die Krümmung derselben abnimmt. - Verstellring nach Anspruch 4, dadurch gekennzeichnet, daß die Umfangsteile (14) zumindest teilweise aus einem Faserverbundwerkstoff bestehen.
- Verstellring nach Anspruch 5, dadurch gekennzeichnet, daß die Umfangsteile (14) zumindest teilweise aus einem kohlenstoffaserverbundwerkstoff bestehen.
- Verstellring nach Anspruch 5, dadurch gekennzeichnet, daß die Umfangsteile (14) zumindest teilweise aus einem Glasfaserverbundwerkstoff bestehen.
- Verstellring nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß die Fasern des Faserverbundwerkstoffes im wesentlichen in Umfangsrichtung des Verstellrings (10) ausgerichtet sind.
- Verstellring nach einem der Ansprüche 4 bis 8, dadurch gekennzeichnet, daß die Unterzüge (18) zumindest teilweise aus Aluminium bestehen.
- Verstellring nach einem der Ansprüche 4 bis 9, dadurch gekennzeichnet, daß die Umfangsteile (14) mehrerer einander benachbarter Ringsegmente (12) einstückig miteinander ausgebildet sind.
- Verstellring nach Anspruch 10, dadurch gekennzeichnet, daß die Umfangsteile (14) der Ringsegmente (12) als zwei Umfangshalbringe (22) ausgebildet sind.
- Verstellring nach Anspruch 10, dadurch gekennzeichnet, daß die Umfangsteile (14) aller Ringsegmente (12) einstückig miteinander ausgebildet sind.
- Verdichter mit einem Verdichtergehäuse, Leitschaufeln und einem Verstellring zur synchronen Veränderung des Anstellwinkels der Leitschaufeln, dadurch gekennzeichnet, daß der Verstellring (10) ein Verstellring (10) nach einem der Ansprüche 1 bis 12 ist.
- Verdichter nach Anspruch 13, dadurch gekennzeichnet, daß der Verdichter (11) Gleitschuhe (48) umfaßt, auf denen der Verstellring (10) gelagert ist und die jeweils eine Gleitfläche (50) zum Gleiten auf dem Verdichtergehäuse (68) aufweisen.
- Verdichter nach Anspruch 14, dadurch gekennzeichnet, daß die Gleitschuhe (48) aus einem Faserverbundwerkstoff bestehen.
- Verdichter nach einem der Ansprüche 13 bis 15, dadurch gekennzeichnet, daß das Verdichtergehäuse (68) Verstellringträger (54) umfaßt, die jeweils eine Gleitfläche (52) aufweisen.
- Verdichter nach Anspruch 16, dadurch gekennzeichnet, daß die Verstellringträger (54) aus einem Faserverbundwerkstoff bestehen.
- Verdichter nach Anspruch 17, dadurch gekennzeichnet, daß die Verstellringträger (54) eine Schichtstruktur aufweisen, bei der in einer radialen Richtung des Verdichters (11) dichte Gewebelagen (73) und weniger dichte Abstandslagen (74) aufeinanderfolgen.
- Verdichter nach Anspruch 18, dadurch gekennzeichnet, daß die Gewebelagen (73) einen negativen Wärmeaus-dehnungskoeffizienten in der radialen Richtung des Verdichters (11) aufweisen.
- Verdichter nach Anspruch 19, dadurch gekennzeichnet, daß die Gewebelagen (73) Fasern, die unter einem Winkel von ungefähr plus 30° gegen die radiale Richtung des Verdichters (11) ausgerichtet sind, und Fasern, die unter einem Winkel von ungefähr minus 30° gegen die radiale Richtung des Verdichters (11) ausgerichtet sind, umfassen.
- Verdichter nach einem der Ansprüche 16 bis 20, dadurch gekennzeichnet, daß jeweils eine Wärmeisolationsschicht (66) zwischen dem Verdichtergehäuse (68) und jedem der Verstellringträger (54) angeordnet ist.
- Verdichter nach einem der Ansprüche 16 bis 21, dadurch gekennzeichnet, daß der Verstellring (10) ein Verstellring (10) nach einem der Ansprüche 4 bis 12 ist und daß die Wärmeausdehnungskoeffizienten der Umfangsteile (14) und der Unterzüge (18) so aufeinander und auf die Länge und die Krümmung der Ringsegmente (12) abgestimmt sind, daß die Auflagerstellen (42, 90) des Verstellrings (10) bei einer Temperaturerhöhung im wesentlichen um dieselbe Strecke radial nach außen verschoben werden wie die Verstellringträger (54).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19516382 | 1995-05-04 | ||
DE19516382A DE19516382A1 (de) | 1995-05-04 | 1995-05-04 | Verstellring |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0741247A2 EP0741247A2 (de) | 1996-11-06 |
EP0741247A3 EP0741247A3 (de) | 1998-05-20 |
EP0741247B1 true EP0741247B1 (de) | 2003-02-26 |
Family
ID=7761078
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96106866A Expired - Lifetime EP0741247B1 (de) | 1995-05-04 | 1996-05-01 | Verstellring |
Country Status (4)
Country | Link |
---|---|
US (1) | US5700129A (de) |
EP (1) | EP0741247B1 (de) |
JP (1) | JP2703750B2 (de) |
DE (2) | DE19516382A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017124339B4 (de) | 2017-10-18 | 2023-03-02 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Verstellring, Verdichter und Verfahren zum Betreiben eines Verstellrings |
EP4130491A4 (de) * | 2020-03-31 | 2024-04-03 | Kawasaki Heavy Ind Ltd | Verstellring für gasturbinenmotor |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
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US6240727B1 (en) * | 2000-04-27 | 2001-06-05 | The United States Of America As Represented By The Secretary Of The Navy | Manufacture of Nitinol rings for thermally responsive control of casing latch |
EP1512832A1 (de) * | 2003-09-02 | 2005-03-09 | Alstom Technology Ltd | Verfahren zum Herstellen eines Turbinenrotors mit Regelrad |
DE10351202A1 (de) * | 2003-11-03 | 2005-06-02 | Mtu Aero Engines Gmbh | Vorrichtung zum Verstellen von Leitschaufeln |
FR2879687B1 (fr) * | 2004-12-16 | 2007-04-20 | Snecma Moteurs Sa | Turbomachine a stator comportant un etage d'aubes de redresseur actionnees par une couronne rotative deplacee par des moyens moteurs electriques |
FR2882577A1 (fr) * | 2005-02-25 | 2006-09-01 | Snecma Moteurs Sa | Dispositif de reglage du centrage d'un anneau de synchronisation de commande d'aubes pivotantes de turbomachine |
FR2882578B1 (fr) * | 2005-02-25 | 2007-05-25 | Snecma Moteurs Sa | Dispositif de reglage du centrage d'un anneau de synchronisation de commande d'aubes pivotantes de turbomachine |
US8092157B2 (en) * | 2007-12-19 | 2012-01-10 | United Technologies Corporation | Variable turbine vane actuation mechanism having a bumper ring |
EP2107217A1 (de) | 2008-03-31 | 2009-10-07 | Siemens Aktiengesellschaft | Verstellringanordnung für ein axiales Verdichtergehäuse |
DE102008033560A1 (de) * | 2008-07-17 | 2010-01-21 | Rolls-Royce Deutschland Ltd & Co Kg | Gasturbinentriebwerk mit verstellbaren Leitschaufeln |
US8414248B2 (en) | 2008-12-30 | 2013-04-09 | Rolls-Royce Corporation | Variable geometry vane |
GB2467153B (en) * | 2009-01-26 | 2010-12-08 | Rolls Royce Plc | A variable assembly |
US8864450B2 (en) | 2011-02-01 | 2014-10-21 | United Technologies Corporation | Gas turbine engine synchronizing ring bumper |
US20140064912A1 (en) * | 2012-08-29 | 2014-03-06 | General Electric Company | Systems and Methods to Control Variable Stator Vanes in Gas Turbine Engines |
US9932851B2 (en) * | 2013-12-30 | 2018-04-03 | Rolls-Royce North American Technologies, Inc. | Active synchronizing ring |
DE102016122639A1 (de) * | 2016-11-23 | 2018-05-24 | Rolls-Royce Deutschland Ltd & Co Kg | Leitschaufelbaugruppe mit Ausgleichseinrichtung |
FR3063779B1 (fr) * | 2017-03-07 | 2022-11-04 | Safran Aircraft Engines | Anneau de commande de calage d'un etage d'aube d'un stator |
CN107023511A (zh) * | 2017-05-19 | 2017-08-08 | 象州县科学技术情报研究所 | 一种叶片可调式离心风机叶轮 |
FR3082562B1 (fr) * | 2018-06-19 | 2020-06-12 | Safran Aircraft Engines | Anneau de commande de portes de decharge pour une turbomachine d'aeronef et turbomachine le comportant |
CN109129250B (zh) * | 2018-10-18 | 2020-05-19 | 北京动力机械研究所 | 一种涡轮发动机导向器流通能力调节工装 |
US11255214B2 (en) * | 2019-11-04 | 2022-02-22 | Raytheon Technologies Corporation | Negative thermal expansion compressor case for improved tip clearance |
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US2970808A (en) * | 1957-10-30 | 1961-02-07 | Westinghouse Electric Corp | Bimetallic shroud structure for rotor blades |
US3685920A (en) * | 1971-02-01 | 1972-08-22 | Gen Electric | Actuation ring for variable geometry compressors or gas turbine engines |
US4035101A (en) * | 1976-03-24 | 1977-07-12 | Westinghouse Electric Corporation | Gas turbine nozzle vane adjusting mechanism |
US4786232A (en) * | 1981-04-10 | 1988-11-22 | Caterpillar Inc. | Floating expansion control ring |
JPS5915605A (ja) * | 1982-07-15 | 1984-01-26 | Toshiba Corp | ガスタ−ビン |
FR2548733B1 (fr) * | 1983-07-07 | 1987-07-10 | Snecma | Dispositif d'etancheite d'aubages mobiles de turbomachine |
GB2206381B (en) * | 1987-06-30 | 1991-10-09 | Rolls Royce Plc | A variable stator vane arrangement for a compressor |
US4925364A (en) * | 1988-12-21 | 1990-05-15 | United Technologies Corporation | Adjustable spacer |
US5004402A (en) * | 1989-09-05 | 1991-04-02 | United Technologies Corporation | Axial compressor stator construction |
GB2264984A (en) * | 1992-03-12 | 1993-09-15 | Bmw Rolls Royce Gmbh | A device for adjusting gas turbine guide vanes. |
US5447411A (en) * | 1993-06-10 | 1995-09-05 | Martin Marietta Corporation | Light weight fan blade containment system |
US5516257A (en) * | 1994-04-28 | 1996-05-14 | United Technologies Corporation | Aircraft fan containment structure restraint |
-
1995
- 1995-05-04 DE DE19516382A patent/DE19516382A1/de not_active Ceased
-
1996
- 1996-05-01 EP EP96106866A patent/EP0741247B1/de not_active Expired - Lifetime
- 1996-05-01 DE DE59610160T patent/DE59610160D1/de not_active Expired - Lifetime
- 1996-05-03 US US08/642,340 patent/US5700129A/en not_active Expired - Lifetime
- 1996-05-07 JP JP8112703A patent/JP2703750B2/ja not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017124339B4 (de) | 2017-10-18 | 2023-03-02 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Verstellring, Verdichter und Verfahren zum Betreiben eines Verstellrings |
EP4130491A4 (de) * | 2020-03-31 | 2024-04-03 | Kawasaki Heavy Ind Ltd | Verstellring für gasturbinenmotor |
Also Published As
Publication number | Publication date |
---|---|
DE59610160D1 (de) | 2003-04-03 |
EP0741247A3 (de) | 1998-05-20 |
JP2703750B2 (ja) | 1998-01-26 |
DE19516382A1 (de) | 1996-11-07 |
EP0741247A2 (de) | 1996-11-06 |
US5700129A (en) | 1997-12-23 |
JPH08312593A (ja) | 1996-11-26 |
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