EP1820941A1 - Guide vane assembly - Google Patents

Abstract

Each adjustable turbine blade (2,3) has a lever mechanism linked to an adjusting device. Turbine blades have one end (9) lying opposite an arrangement of bearings on the side of a driving mechanism. This end of the turbine blades opposite the driving mechanism has a peg (33) fitted in a drilled hole on a element (31) for controlling flow.

Description

The invention relates to a nozzle with adjustable blades, which are mounted on the drive side, wherein each blade has a lever mechanism which is connected to an adjusting device, and wherein the blades have a drive-side bearing opposite end.

The DE 103 11 227 B4 discloses a nozzle for a radial turbine with arranged in a housing, adjustable for flow control by means of an actuator blades, a collar with outwardly open recesses, each bounded by two parallel, extending in the radial direction abutment surfaces. There are levers provided which each engage with a circular end portion in a respective recess and are rotatably coupled at the other end with a respective blade shank. The mutual distance of the contact surfaces is chosen so that the circular end portions of the adjusting lever slidably engage in the recesses, wherein the recesses are dimensioned so that with cold collar between the bottom of the recesses and the end portions of the lever a correspondingly sized gap remains free, so that upon heating of the adjusting ring, the end parts can dive into the column, wherein the recesses are dimensioned to be wider than the thickness of the end portions of the adjusting lever. For the adjusting ring and / or the adjusting lever a dry lubrication in the form of sliding inserts is provided.

Diaphragms of the type mentioned are known and are eg in large machines such as compressors or compressors and / or turbines to control the map and to reduce the starting power used. Usually, the nozzles are mounted in a flow channel of the compressor or compressor, so that the nozzles can also be referred to as Eintrittsleitapparate. To adjust the blades, the nozzles have an adjusting device or the adjusting device, which must be performed relatively free of play, in order to avoid hysteresis and uncontrolled blade movements. In particular, high temperature differences, large dimensions and coefficients of thermal expansion of materials in the design must be taken into account.

In the case of an inlet guide device of the relevant size, the high temperature differences (-105 ° C. to + 300 ° C.) result in extremely large thermal expansions, which can impair operation. This impairment occurs in particular on moving components of the inlet guide. Specifically, it may cause undesirable vibrations and rattling of the moving components due to differential thermal expansion. In particular, the unwanted vibrations can damage the loose components. In addition, it is also conceivable that components at least temporarily lose their mobility as a result of terminals. When starting the machine, it may therefore happen that the inlet guide jammed and the guide grid can not be opened.

It is known that a movement play of the components to be moved is dimensioned sufficiently large, so that in this way a clamping is necessarily prevented. As the size increases, this design philosophy results in unacceptably large games that result in rattling, vibration, malfunction and eventual damage to the moving components.

The invention has for its object to improve a diffuser of the type mentioned in particular for large machines with simple means to go that the Susceptibility to vibrations and rattling is reduced, at the same time a mobility of the components to be moved should be ensured.

According to the invention, the object is achieved by a control device associated with the blades, which has a circumferentially extending sliding bearing, wherein radially opposite sliding bearing surfaces are elastically braced against each other.

The Eintrittsleitapparat is substantially annular, wherein the adjusting device extends along a circumferential direction.

Advantageously, by means of the inventive design of the adjusting device, on the one hand, a certain position of the common adjusting device is achieved without a tendency to rattling or swinging occurs. On the other hand, a reliable mobility without clamping is achieved. Easily follows the exposed to the strong thermal influences slide bearing the outer temperature gradients and ensures the mobility due to the elastically biased but sliding slide bearing surfaces.

For radial guidance of the adjusting device is advantageously provided that the adjusting device is seen in cross-section U-shaped with a base web and two U-legs, wherein in the base web at least one recess is introduced, in which at least one actuator or a guide element is added , The adjusting device is preferably formed in two parts from a cross-sectionally L-shaped and an I-shaped component, which are connected to each other, preferably screwed. In this case, a transverse web of the L-shaped component preferably forms the base web, with which the I-shaped component can be connected. The I-shaped component and a longitudinal web of the L-shaped component form the U-legs. The guide element causes the radial guidance of the adjusting device and forms one of Sliding bearing surfaces, wherein a second sliding bearing surface is arranged radially opposite. The recess may be introduced radially circumferentially in the base web. Preferably, the recess can also be introduced circumferentially interrupted in the base web, so that a plurality of guide elements are arranged in the plurality of recesses, which will be discussed in more detail below.

In order to achieve that the adjusting device is thermally independent (temperature difference, thermal expansion coefficient), it is expediently provided that the guide element is formed from a force accumulator, ie an elastic element, a guide sleeve and a sliding element, wherein the guide element sufficiently compliant with the base web of Adjusting device is connected, which is achieved in particular with the energy storage or with the elastic element. Advantageously, the actuator is thus quasi thermally decoupled to the housing, whereby a thermally independent guidance of the lever mechanism and the common actuating device is ensured. The radial guidance of the adjusting device, which can also be referred to as an adjusting ring, takes place with the guide elements or the respective force accumulator, the respective guide sleeve and the respective sliding element, with which the adjusting device is able to follow extreme thermal influences without the functioning of the Eintrittsleitapparates or diffuser to affect.

The guide sleeve is pressed by means of the elastic element or the energy accumulator in the circumferential direction, preferably radially against a counter sliding or against the second sliding bearing surface, so that the radially opposite sliding bearing surfaces are formed, which are braced against each other by means of the force accumulator.

Favorable in the context of the invention is when the sliding bearing provides a plurality of sliding in the radial direction normal to the sliding surface sliding bearing surfaces, which by means of elastic elements or the energy storage are clamped in the direction of the mobility against the second sliding bearing surface. The elastic elements or energy storage can preferably be designed as disc springs.

The sliding elements are preferably arranged on a head region of the guide sleeve which is opposite the force accumulator. It is expedient for the purposes of the invention if the movable sliding bearing surfaces or the guide sleeve, which is prestressed by means of the force accumulator, have a particularly low coefficient of static friction or good sliding properties, wherein the sliding surfaces can be Teflon-coated or provided with a plastic or a bronze. Particularly useful is a use of graphite or Teflon as a sliding element. Of course, instead of the guide sleeve associated sliding element, the second sliding bearing surface can be coated or executed accordingly. It is also possible to use sliding elements and at the same time a coating of the second sliding bearing surface.

Appropriately, the lever mechanism of each blade is accommodated in a common, separate housing wherein the lever mechanism of the radially encircling in the housing adjusting device is assigned such that at least one of the blades is driven by a drive and the other blades are forcibly driven.

Thus, a lever mechanism, in particular for a Eintrittsleitapparat, for example, for radial compressors, in particular for turbo compressors, arranged as a module in a separate housing, so that a Kennfeldbeeinflussung or throttling by means of the adjusting device adjustable blades can be achieved. By means of the lever mechanism, which on the one hand has a drive mechanism and on the other hand an output mechanism, it is advantageously possible at least one of To drive blades with a drive, wherein the other blades via the output mechanism, which is connected to the actuator and a respective blade shank of the positively driven blades inevitably take along.

Favorable in the context of the invention is when the housing is designed in two parts, wherein the two housing parts are frictionally connected with each other, and wherein the housing in its interior a contact surface, so the second sliding bearing surface for the adjusting device or for the sliding element or for the guide element having. Advantageously, therefore, one of the housing parts can first be connected to the housing of the inlet guide apparatus in order to install the lever mechanism and the adjusting device. To close the housing, the other housing part is then screwed only with the already connected to the housing of the diffuser housing part.

To drive the driven blade, this is connected with its blade shank with a drive. It is therefore expedient for the purposes of the invention that the lever mechanism of the driven blade, ie the drive mechanism, has a drive lever connected to the drive, to which a transmission lever is connected, wherein the transmission lever is connected to a coupling lever, which is connected to the actuating device , The drive lever is preferably congruent with its center line to the center line of the drive and the blade to be driven or their blade shank. Preferably, it is provided that the drive lever is simultaneously designed as a drive shaft. It is of course possible to run drive lever and drive shaft as separate components.

Advantageously, it is now provided that the lever mechanism of the positively driven blades, ie the output mechanism, one with the adjusting device connected output coupling lever which is connected to a driven lever, which is connected on the other side with the blade shank of the positively driven blade.

Conveniently, it is provided that the respectively interconnected lever are rotatably connected to each other and that the coupling lever or output coupling lever is rotatably connected to the adjusting device. Of course, the respective rotating surfaces may have suitable sliding coatings or sliding elements, for example plastic coatings or liners.

Advantageously, a lever mechanism, that is to say a drive mechanism, is thus made available in which the drive takes place via the drive lever, which is mounted radially and axially in the separate housing. By means of the transmission lever and the coupling lever, which is connected to the adjusting device, so the blade is driven, wherein the driven blade is preferably mounted with its blade shank in the drive lever.

The output of the positively driven blades is advantageously via the adjusting device, which acts by means of the respective output coupling lever on the respective output lever, on the other hand connected to the radially and axially mounted in the separate housing positively driven blades, or their respective blade shank.

The power flow is advantageously carried out perpendicular to the respective axes of rotation of the lever mechanism to avoid lateral forces or moments.

It is possible that it may come due to the alternating flow of the blades to vibration excitations. Depending on the situation (certain width of the blades, installation requirements) it is therefore necessary to flow-guiding element to be arranged on the drive-side storage opposite end of the blades. This flow-guiding element serves for example for gap reduction between the blade end and the inlet channel. Here, too, high temperature differences, large dimensions and thermal expansion coefficients of materials must be taken into account in the design.

According to the invention, the object is therefore also achieved in that the drive opposite the end of the blades, ie the guide vanes, each having a pin which is mounted in a bore of a flow-guiding element, wherein at least one ring element is provided which radially in the pin the bore clamped. The ring element may also be referred to as a radial fixing component.

Appropriately, the ring member has a radial elasticity and in addition good sliding properties, wherein preferably plastic can be used and / or Teflonoberflächen are provided.

Favorable in the context of the invention is when the ring member has a V-shaped cross-section, so that preferably a resilient ring member is formed, with its two V-legs approach in elastic deformation substantially each other or remove each other.

It is expedient for the purposes of the invention if the end of the blades, ie the guide vanes, which faces the drive side, is assigned in each case at least one flow-guiding element which can be connected to the blades via a centering element.

The centering causes on the one hand a centering of the flow-guiding element on each blade in the radial direction, wherein the centering element is associated with the ring element, and wherein the respective centering element is designed such that it is capable of extreme to follow thermal influences, without affecting the operation of the inlet guide. The centering causes on the other hand a positioning or holding the flow-guiding element in the axial direction.

Advantageously, in each case a centering element with a double function is provided, which can act in the axial and in the radial direction, wherein in particular a radial vibration damping and a thermal decoupling of the flow-guiding element to the associated blade end is achieved. The centering element therefore preferably has radial fixing components or the ring element and axial fixing components. The centering element or its axial and radial fixing components are preferably arranged on the pin which is assigned to the opposite end of the blades to the drive. The pin is preferably congruent with its center line to the center line of the blades.

It is expediently provided that the centering element preferably has spring rings, for example a steel disk, as the axial fixing component on the blade side, a thrust washer being disposed opposite thereto. The steel disc and the thrust washer are spaced apart in the axial direction by means of a cylindrical body or a sleeve body. By means of the axial fixing components or the preferred spring washers, the arrangement is also capable of damping bending vibrations.

The radial fixing component or the ring element is arranged on the one hand between mutually associated end faces of the steel disc and the cylindrical body and on the other between mutually associated end faces of the cylindrical body and the thrust washer. As already described, the ring element is seen in cross-section preferably designed V-shaped. In a favorable embodiment, the ring element is doing with his closed head region in each case in the direction of the cylindrical body and oriented with its head region opposite free leg ends in the direction of the respectively associated axial fixing, so that quasi a resilient ring member is formed, the two legs approach each other in elastic deformation or remove each other.

Appropriately, it is provided that the flow-guiding element has the bore which is slightly larger than the outer diameter of the pin of its inner diameter. Each end, the flow-guiding element in the region of the through hole has a stepped configuration, which is adapted to the configuration or dimension of the axial fixing components and the steel disc and the thrust washer.

It is expedient if only a single flow-guiding element is used, which is preferably designed as a ring plate and having a number of holes corresponding to the number of blades for supporting the respective pin. Of course, it is also possible that a large number of flow-conducting elements is used.

Overall, a thermally independent, radial and axial centering of a flow-guiding element with vibration damping properties is thus provided.

Fig. 1

einen Teilquerschnitt durch einen Eintrittsleitapparat,

Fig. 2

eine Vergrößerung aus Figur 1 zur Darstellung der Stellvorrichtung mit darin angeordneter Entkoppelungselemente,

Fig. 3

einen Teilquerschnitt aus einem Leitapparat durch ein der Antriebsseite gegenüber liegendes Schaufelende mit zugeordnetem strömungsführenden Element, und

Fig. 4

eine radiale Fixierkomponente aus Figur 3 als Einzelheit im Querschnitt.

Further advantageous embodiments are disclosed in the subclaims and the following description of the figures. Show it:

Fig. 1

a partial cross section through an inlet guide,

Fig. 2

1 is a magnification view of the adjusting device with decoupling elements arranged therein;

Fig. 3

a partial cross-section of a nozzle by a drive side opposite blade end with associated flow-leading element, and

Fig. 4

a radial fixing of Figure 3 as a detail in cross section.

In the different figures, the same parts are always provided with the same reference numerals, so that these are usually described only once.

1 shows a partial cross section through a distributor 1 with adjustable blades 2 and 3, respectively. The blades 2 and 3 are mounted on the drive side. The blade 2 is driven with the blade 3 forcibly driven, as shown in FIG. 1 so that the reference numeral 3 is put in parentheses.

The blades 2 and 3 have on the drive side in each case a blade shank 4 or 6, wherein the reference numeral 6 in Figure 1 is again set in parentheses to illustrate that this is assigned to each of the positively driven blades 3.

Each blade 2 or 3 has a lever mechanism 7, which is connected to an adjusting device 8. The blades 2 and 3 respectively have an end 9 which lies opposite the drive-side mounting, that is to say the blade shank 4 or 6 (FIG. 3).

The lever mechanism 7 of each blade 2 and 3 is accommodated in a common, separate housing 11, wherein the lever mechanism 7 arranged in the housing 11, radially Circumferential adjusting device 8 is assigned such that at least the driven blade 2 is driven by a drive 12 and the other blades 3 are forcibly driven, so that the blades 2.3 commonly associated adjusting device 8 on the blades 2.3 and on the vanes acts.

In the illustrated embodiment, a relatively large engine, preferably a radial compressor with eighteen blades is shown, with only one of the blades 2 driven, with the other seventeen blades 3 forcibly driven. In the following, therefore, the mechanism of the driven blade 2 and one of the positively driven blades 3 will be described by way of example.

The housing 11 is designed in two parts, wherein the two housing parts 13, 14 positively frictionally connected to each other, preferably are screwed together. The housing parts 13, 14 are preferably made in one piece. The housing 11 has in its interior a radially circumferential contact surface 16 for the adjusting device 8.

To mount the lever mechanism 7, a housing part 13 is first connected to the associated housing part of a compressor exemplified, preferably screwed to close the housing part 13 after mounting the lever mechanism 7 and the adjusting device 8 in the second housing part 14, so that Housing 11 is formed with the lever mechanism 7 arranged therein. To close the two housing parts 13,14 only one screw is required.

The lever mechanism 7 has a drive mechanism and an output mechanism

The lever mechanism 7 of the driven blade 2, that is to say the drive mechanism, has one with the drive 12 connected to drive lever 17, with which a transmission lever 18 is connected, which is connected to a coupling lever 19. The coupling lever 19 is connected to the adjusting device 8. The drive lever 17 is in the illustrated embodiment at the same time a drive shaft. Of course, drive lever 17 and drive shaft can also be designed as separate components.

As can be seen from FIG. 1, the drive lever 17 with its center line X is congruent with the center line of the blade shank 4 and also congruent with the center line of a bearing 21 or a bearing cover of the drive lever 17 or the drive shaft.

The lever mechanism 7 of the forcibly driven blade 3, that is to say the output mechanism, likewise has an output coupling lever 20, which is connected to an output lever 22. The output lever 22 is now connected to the blade shank 6 of the forcibly driven blade 3. For ease of illustration, the components of the output mechanism with their reference numerals are again in parentheses.

The lateral forces in the drive lever 17 are received in the bearing 21 and the bearing cap. The transmission lever 18 has at its drive lever-side end Aufsteckauge and is so firm or rigid, so not rotatable, connected to the drive lever 17. To connect the transmission lever 18 with the coupling lever 19 and the output coupling lever 20 and the output lever 22, these levers at the respectively associated ends also have eyes in which a pintle can engage. Thus, the transmission lever 18 via the coupling lever 19 and output coupling lever 20 is also connected to the output lever 22. The coupling lever 19 or output coupling lever 20 engages on one side with his eye in the adjusting device 8 and is also rotatably connected to the adjusting device 8.

The adjusting device 8 is seen in cross-section U-shaped with a base web 23 and two U-legs 24 executed. The U-legs 24 are each oriented with their free end to the blade shank 4 or 6 and have a gap which is adapted approximately to the dimensions of the coupling lever 19 and the output coupling lever 20. The adjusting device 8 is formed in the illustrated embodiment in two parts of a seen in cross-section L-shaped component and an I-shaped component in cross-section. A transverse web of the L-shaped component forms the base web 23, to which the I-shaped component is connected, preferably screwed. A longitudinal web of the L-shaped component and the I-shaped component thus form the U-legs 24.

As can be seen from FIG. 2, a recess is made in the base web 23 in which a guide element 26 is received. The guide element 26 has a force accumulator 27 or an elastic element, preferably a cup spring package and a guide sleeve 28, to which a sliding element 29 is associated at the end or at its head region. The guide element 26 is sufficiently connected to the base web 23 on the inside. In FIG. 2, by way of example, a single guide element 26 is shown, wherein a multiplicity of guide elements are arranged circumferentially distributed on the adjusting device 8. In the illustrated exemplary inlet guide apparatus for a turbo-compressor, seven guide elements 26 are provided. The fact that not a single radially encircling guide element 26 is used, the costs for the production of the diffuser are further reduced because not the entire inner radial surface, in particular with the very expensive sliding element is provided.

The force storage element 27 causes a play-free guidance of the adjusting device 8 and compensates for differences in temperature differences and thermal expansion coefficients.

In the illustrated embodiment, the energy storage 27 is designed as a plate spring package but can also be designed as a helical spring or the like.

The guide sleeve 28 is seen in cross section designed as a cylindrical body having in its interior a through hole for receiving a connecting element. The sliding member 29 is executed in the illustrated embodiment as a plug, preferably as a round plug, wherein the design of the sliding element 29 is based on the finding that this must be as small as possible for cost reasons, while still a sufficiently high surface pressure to be achieved. The sliding member 29 has a particularly low coefficient of static friction or good sliding properties, with preference Teflon or graphite can be used.

By means of the guide member 26, which is spring-loaded with its sliding member 29 (power storage 27 and elastic element) on the contact surface 16 of the housing 11, the adjusting device 8 is guided radially, wherein a thermal decoupling of the adjusting device 8, which can also be referred to as a collar , is achieved.

Advantageously, a control device 8 associated with the blades 2, 3 is accordingly formed, which has a sliding bearing extending in the circumferential direction, in which radially opposite sliding bearing surfaces (sliding element 29, contact surface 16) are elastically braced against each other by means of the force accumulator 27 (elastic element) ,

The Eintrittsleitapparat 1 is formed substantially annular, wherein the adjusting device 8 extends along a circumferential direction.

Advantageously, by means of the inventive design of the adjusting device 8 on the one hand, a certain position of the common actuator 8 achieved without a tendency to rattling or swinging is observed. On the other hand, a reliable mobility without clamping is achieved. The sliding bearing, which is exposed to strong thermal influences, easily follows the outer temperature curves and ensures mobility owing to the elastically prestressed but displaceable sliding bearing surfaces (sliding element 29, contact surface 16).

Thus, the radial guidance of the adjusting device 8 with the guide element 26, which preferably consists of the components of energy storage 27, guide sleeve 28 and sliding member 29, so that the adjusting device 8 is able to follow extreme thermal influences, without the operation of the Eingangsleitapparates. 1 to impair.

In the illustrated embodiment of Figures 1 and 2, a lever mechanism 7, for example, for radial compressors as a module in the separate housing 11 is arranged to achieve, for example, Kennfeldbeeinflussungen or throttling by means of the adjusting device 8 adjustable blades 2 and 3 respectively. The drive takes place via the drive lever 17 which is mounted radially and axially in the housing of the distributor and the housing 11, wherein the seen in cross-section U-shaped adjusting device 8, the transmission lever 18 and the coupling lever 19 including the blade 2 is driven ( drive mechanism).

The output is via the adjusting device 8, which acts by means of the output coupling lever 20 on the output lever 22, which are connected to the radially and axially mounted in the housing 11, forcibly driven blades 3 (output mechanism).

The power flow takes place perpendicular to the axes of rotation or

Center lines of the lever mechanism 7, to avoid lateral forces or moments.

Overall, therefore, a thermally independent guidance of the adjusting device 8 is provided.

Of course, the invention is not limited to the embodiment described. It is conceivable, for example, an arrangement in which a conventional gear transmission is provided with an internally toothed sun gear and various planetary gears, wherein the sun gear is provided with, according to the invention, elastically biased and extending in the circumferential direction radial sliding surfaces.

FIG. 3 shows a partial cross section through the distributor 1, the end 9 of the blades 2 or 3 opposite the drive side blade side in particular being illustrated here.

The drive 12 opposite end 9 of the blades 2 and 3, a single flow-guiding element 31 is assigned in the illustrated embodiment, which is connected via a respective centering element 32 with the blades 2 and 3 respectively. The flow-guiding element 31, which can also be referred to as a flow-guiding plate or ring plate, is necessary in order to ensure the distance to the flow channel after the installation of the inlet guide apparatus, wherein the flow-guiding element 31 is centered on the blades 2 and 3 respectively.

The end 9 of the blades 2 and 3 has a pin 33, wherein the flow-guiding element 31 has eighteen through-holes in the illustrated embodiment, which are designed by its inner diameter slightly larger than the outer diameter of the respective pin 33. The centering element 32 is used for radial Centering and axial positioning or axial holding the flow guiding element 31, wherein the centering axial fixing components 34,36 and 37 and radial fixing components 38 has.

For axial fixation, the axial fixing components 34, 36 and 37 are provided. The fixing component 34 is designed as a spring ring or as a steel disc and associated with the blade-side surface of the flow-guiding element 31. The fixing component 36 is also designed as a spring ring or as a thrust washer and arranged on one of the side facing the blade-side surface of the flow-guiding element 31. The fixing component 37 is designed as a hollow cylindrical body, which is adapted with its inner diameter approximately to the outer diameter of the pin 33. The axial fixing component 37 serves as a kind of spacer element for the two axial fixing components 34 and 36, respectively. The respective fixing components 34, 36, and 37 are arranged within the bore of the flow-guiding element 31 and each have a radial play for the latter.

Between the respective end faces of the fixing component 37 and the fixing component 34 on the one hand and the fixing component 36 on the other hand, in each case the radial fixing component 38 is arranged, which can also be referred to as a ring element.

By means of the radial fixing component 38, the pin 33 is braced radially in the bore. The radial fixing component 38 is shown enlarged in detail in FIG. As can be seen from FIG. 4, the radial fixing component 38, viewed in cross-section, is oriented in a V-shaped manner with a closed head region 39 in each case in the direction of the hollow cylindrical body 37. With its free leg ends 41 opposite the head region, the ring element is oriented in the direction of the axial fixing components 34 and 36, respectively. Clearly removed from Figure 4 is an elastic mobility of the two V-leg ends 41 with elastic deformation, so that both V-legs can approach or remove each other. This mobility is shown by means of the double arrow 42. Advantageously, the radial fixing component 38 or the resilient ring element assumes a damping function in the radial direction and can also be referred to as a damping element.

For storage of the fixing components 34 and 36, the respective associated sides of the flow-guiding element 31 have step-shaped configurations which are adapted to the dimensions of the respective fixing components 34 and 36, respectively.

By means of the embodiment illustrated in FIG. 3 and the radial fixing component 38 shown in detail in FIG. 4, a thermally independent, radial centering of the flow-guiding element 31 with vibration-damping properties is made available, in particular natural frequencies being considerably reduced.

LIST OF REFERENCE NUMBERS

1.

diffuser

Second

driven shovel

Third

positively driven shovel

4th

Shovel shank v. 2

5th

6th

Shovel shank v. 3

7th

lever mechanism

8th.

locking device

9th

End of 2 or 3

10th

11th

casing

12th

drive

13th

Housing part v. 11

14th

Housing parts v. 11

15th

16th

contact surface

17th

drive lever

18th

transmission lever

19th

coupling lever

20th

Output coupling lever

21st

storage

22nd

output lever

23rd

Base bridge v. 8th

24th

U-thighs v. 8th

25th

26th

guide element

27th

power storage

28th

guide sleeve

29th

Slide

30th

31st

fluid guiding elements

32nd

centering

33rd

spigot

34th

axial fixing components v. 32 (steel disc)

35th

36th

axial fixing components v. 32 (thrust washer)

37th

axial fixing components v. 32 (hollow cylindrical body)

38th

radial fixing components v. 32

39th

Head area v. 38

40th

41st

Leg ends v. 38

42nd

Agility v. 41

Claims (5)

Diaphragm with adjustable blades (2, 3) which are mounted at least on the drive side, wherein each blade (2, 3) has a lever mechanism (7) which is connected to an adjusting device (8), and wherein the blades (2, 3) have an end opposite the drive-side bearing (9), in particular according to one of the preceding claims,
characterized in that
the opposite end of the drive (9) of the blades (2,3) each having a pin (33) which is mounted in a bore of a flow-guiding element (31), wherein the pin (33) associated with at least one radial fixing component (38) is. Diaphragm according to claim 1,
characterized in that
the radial fixing component (38) is designed as a ring element in cross-section V-shaped. Diaphragm according to claim 1 or 2,
characterized in that
the at least one flow-guiding element (31) is associated with the end (9) of the blades (2, 3) opposite the drive-side bearing, which can be connected to the blades (2, 3) via centering elements (32). Diaphragm according to claim 3,
characterized in that
the centering element (32) has axial fixing components (34, 36, 37) and the at least one radial fixing component (38). Guide device according to claim 3 or 4,
characterized in that
the centering element (32) on the blade side as an axial fixing (34) a steel disc and lying opposite as axial fixing (36) has a thrust washer, which are spaced apart in the axial direction by means of the axial fixing components (37), which is designed as a cylindrical body in that the radial fixing component (38) is arranged between the steel disc and the cylindrical body on the one hand and between the cylindrical body and the thrust washer on the other hand.

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