CN112994337A - Fluid machinery rotating part stress self-adaptation structure - Google Patents
Fluid machinery rotating part stress self-adaptation structure Download PDFInfo
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- CN112994337A CN112994337A CN202110194399.1A CN202110194399A CN112994337A CN 112994337 A CN112994337 A CN 112994337A CN 202110194399 A CN202110194399 A CN 202110194399A CN 112994337 A CN112994337 A CN 112994337A
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/28—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures
- H02K1/30—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures using intermediate parts, e.g. spiders
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- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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- Power Engineering (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Hydraulic Turbines (AREA)
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Abstract
The invention discloses a stress self-adaptive structure of a fluid machinery rotating part, which comprises a connecting disc, a rotating shaft connected to the center of the disc and a cylindrical magnetic yoke ring, wherein the edge of the connecting disc is connected to the axial middle position of the inner side of the magnetic yoke ring, a stress compensation mechanism is arranged between the two ends of the magnetic yoke ring and the connecting disc, when the fluid machinery rotating part rotates, the stress compensation mechanism generates a compensation acting force towards the axis of the magnetic yoke ring on any one end part of the magnetic yoke ring, and the compensation acting force forms an inward-turning compensation torque on the end part of the magnetic yoke ring. The invention can effectively improve the bending strength of the magnetic yoke ring and ensure the uniformity of the magnetic gap between the rotor and the stator on the basis of not obviously increasing the weight and the manufacturing cost of the magnetic yoke ring.
Description
Technical Field
The invention relates to the technical field of hydraulic generators, in particular to a self-adaptive structure for stress of a rotating part of a fluid machine.
Background
With the enhancement of energy conservation and environmental protection awareness of people, large-scale fluid machines such as hydraulic power generation machines and high-temperature environment coolant delivery pumps as green energy sources are being developed vigorously. The rotor of the rotary fluid power equipment generally comprises a connecting disc arranged on a rotating shaft and a cylindrical yoke ring arranged at the edge of the connecting disc, and the middle of the inner side of the cylindrical yoke ring is connected with the connecting disc, so that a magnetic gap is formed between the yoke ring and the stator, wherein the axial section of the rotor is in an I shape. When the unit moves, the rotor can rotate at a high speed, and the yoke ring can generate great centrifugal force due to great weight, the two suspended ends of the yoke ring can be outwards inclined and turned under the action of the centrifugal force, so that the magnetic gap can be changed well, and the yoke ring and the stator can generate friction interference even in severe conditions.
In order to avoid the bending deformation of the yoke, the following technical means are generally adopted: the first solution is to increase the size of the yoke coil to increase its strength and rigidity, but it has drawbacks of increased weight and cost, and increased centrifugal force; the second solution is to arrange a reinforcing rib at the joint of the connecting disc and the yoke ring to improve the bending strength thereof, and the solution has the following defects: it can be understood that the reinforcing rib mainly has the effect of increasing the strength of the joint of the connecting disc and the yoke ring, and the effect of improving the strength of the two ends of the yoke ring far away from the joint is extremely small, and the two ends of the yoke ring are the parts most prone to bending, so that the technical problem that the bending deformation of the two ends of the yoke ring and the change of the magnetic gap between the rotor and the stator are difficult to effectively eliminate by the scheme.
Disclosure of Invention
The invention aims to solve the problem that a magnetic yoke ring of a rotor is easy to bend and deform due to centrifugal force and further magnetic gaps between the rotor and a stator are difficult to be uniform in the conventional bulb through-flow turbine, and provides a stress adaptive structure of a fluid machinery rotating part, which can effectively improve the bending strength of the magnetic yoke ring and ensure the uniformity of the magnetic gaps between the rotor and the stator on the basis of not obviously increasing the weight and the manufacturing cost of the magnetic yoke ring.
In order to achieve the purpose, the invention adopts the following technical scheme:
a fluid machinery rotating part stress self-adaptive structure comprises a connecting disc, a rotating shaft connected to the center of the disc and a cylindrical magnetic yoke ring, wherein the edge of the connecting disc is connected to the axial middle position of the inner side of the magnetic yoke ring, a stress compensation mechanism is arranged between the two ends of the magnetic yoke ring and the connecting disc, when the fluid machinery rotating part rotates, the stress compensation mechanism generates a compensation acting force towards the axis of the magnetic yoke ring on any one end of the magnetic yoke ring, and the compensation acting force forms a compensation torque which turns inwards on the end of the magnetic yoke ring.
It should be noted that the fluid machine rotation member of the present invention preferably refers to a rotor of a hydro-generator, and similarly to the prior art, the fluid machine rotation member includes a yoke ring at the periphery, a connection disk (connection bracket) connected to an intermediate position inside the yoke ring, and a rotation shaft connected to the center of the connection disk (connection bracket). When the water turbine drives the rotor to rotate through the rotating shaft, hydroelectric power generation can be realized.
Because the yoke ring has a larger radius and mass, when the rotor rotates at a high speed, the front end and the rear end of the yoke ring which are suspended in the air generate a radial outward centrifugal force, and the centrifugal force can form a bending torque which enables the outer end of the yoke ring to bend and turn outwards, so that the magnetic gap between the rotor and the stator is influenced.
The invention arranges a stress compensation mechanism between the two ends of the magnetic yoke ring and the connecting disc, thus, when the fluid machinery rotating component (namely the rotor) rotates at high speed and forms huge centrifugal force, the stress compensation mechanism can generate a compensation acting force towards the axis of the magnetic yoke ring to any one end of the magnetic yoke ring, and the compensation acting force forms a compensation torque turning inwards to the end of the magnetic yoke ring, so as to effectively counteract the bending torque formed by the centrifugal force of the magnetic yoke ring, and further avoid the outward turning and the bending deformation of the two ends of the magnetic yoke ring.
Preferably, the stress compensation mechanism comprises a correction ring piece and a brake caliper capable of braking the inner side edge of the correction ring piece, the outer side edge of the correction ring piece is fixedly connected to the end part of the magnetic yoke ring, a plurality of reinforcing rib pieces uniformly distributed in the circumferential direction are arranged between the correction ring piece and the inner side of the magnetic yoke ring, one side of each reinforcing rib piece is fixedly connected to the correction ring piece, a deformation gap is arranged between each reinforcing rib piece and the inner side of the magnetic yoke ring, an outwards extending chute is arranged on each reinforcing rib piece, and a compensation block is arranged in each chute, forms an outwards centrifugal force when the fluid mechanical rotating part rotates, and forms an inwards-turned compensation torque on the end part of the magnetic yoke ring through each reinforcing rib piece and the correction ring piece.
The invention is provided with a correction ring piece at the end of a magnetic yoke ring and a brake caliper capable of braking the inner side edge of the correction ring piece. Thus, when the fluid machinery rotating parts need to be braked for maintenance, the rotating parts can be stopped quickly by the brake caliper, and therefore, the efficiency is improved.
Particularly, a plurality of reinforcing rib pieces which are uniformly distributed in the circumferential direction are arranged between the correcting ring piece and the inner side of the magnetic yoke ring, and the reinforcing rib pieces are provided with compensation blocks which can slide outwards. Thus, when the rotating part of the fluid machine rotates, the compensating block generates an outward centrifugal force which acts on the straightening ring via the reinforcing rib, thereby generating a bending moment which causes the inner side of the straightening ring to be inward, and the bending moment further generates an inward compensation torque for the end of the yoke ring.
It is understood that the higher the rotation speed of the fluid machine rotating component, the larger the centrifugal force of the compensating block, and accordingly, the larger the compensating torque acting on the end of the yoke ring, so that the stress adaptation of the fluid machine rotating component can be realized.
It should be noted that the invention is provided with the deformation clearance between the reinforcing rib sheets and the inner side of the magnetic yoke ring, thereby being beneficial to the compensation block communicating with the reinforcing rib sheets to generate slight overturn inwards relative to the magnetic yoke ring, and ensuring that the centrifugal force of the compensation block can be completely acted on the correction ring sheet.
Preferably, a sliding rod is arranged in the sliding groove, the compensation block is sleeved on the sliding rod, and two ends of the compensation block are respectively provided with a pressure spring sleeved on the sliding rod.
Because the two ends of the compensation block are respectively provided with the pressure springs sleeved on the sliding rods, the compensation block can be elastically positioned in the sliding groove. When the compensation block rotates at a high speed to generate centrifugal force, the compensation block can overcome the elasticity of the outer pressure spring and move outwards, and further the centrifugal force of the compensation block is increased. By reasonably designing the elastic coefficient of the pressure spring, the compensation block can stay at a proper position in the sliding groove, and the centrifugal force of the compensation block is matched with the required compensation torque.
Preferably, the stress compensation mechanism comprises a plurality of support rods, a reinforcing rod and a pull rope, wherein the inner end of each support rod is connected to the connecting disc and is close to the joint with the magnetic yoke ring, the inner end of each reinforcing rod is connected with the connecting disc, the outer end of each support rod inclines towards one side of the center of the connecting disc, the reinforcing rod inclines outwards from the inner end to the outer end and is connected with the outer end of each support rod, a pulley is arranged at the joint of each support rod and the corresponding reinforcing rod, a slidable compensation block is arranged on each support rod, one end of the pull rope is connected to the end portion of the magnetic yoke ring, the other end of the pull rope is connected with the compensation block after bypassing the pulley, and when the fluid mechanical rotating component rotates, the compensation block forms an outward centrifugal force and forms a compensation acting.
In this scheme, compensation mechanism includes the triangle-shaped support that connects into by bracing piece, stiffener to be equipped with the pulley in this triangle-shaped support's outer end. When the fluid machinery rotating part rotates, the compensation block connected to the support rod in a sliding mode forms an outward centrifugal force, and a compensation acting force F towards the axis of the yoke ring is formed on the end portion of the yoke ring through the pull rope.
It will be appreciated that the pulley is located close to the end face of the yoke ring, and that the pull cord connected between the yoke ring and the pulley is then located in the radial direction as much as possible, in order to minimise the weight of the compensating block whilst ensuring that there is a sufficient compensating force F.
Preferably, the support rod is sleeved with a limiting ring, the limiting ring is provided with a fastening screw which can enable the limiting ring to be fixed on the support rod, and one end, far away from the pulley, of the limiting ring abuts against the compensation block.
Because the support rod is sleeved with the limiting ring, and the compensation block abuts against the limiting ring, when the fluid machinery rotating part is static, the compensation block can be reliably positioned on the support rod, and meanwhile, when the fluid machinery rotating part rotates, the compensation effect of outward sliding of the compensation block is not influenced.
Preferably, the stress compensation mechanism comprises a plurality of radial pull rods, one ends of the radial pull rods are connected to one side of the end part of the magnetic yoke ring, the other ends of the radial pull rods are positioned on the other side of the magnetic yoke ring, compensation blocks are arranged at the other ends of the radial pull rods, the radial pull rods are attached to the front side of the rotation direction of the rotation shaft, when the fluid machinery rotation part rotates, the compensation blocks form outward centrifugal force, and compensation acting force F towards the axis of the magnetic yoke ring is formed on the end part of the magnetic yoke ring through the radial pull rods.
In this scheme, stress compensation mechanism includes a plurality of radial pull rods to radial pull rod's one end is connected on the yoke circle, and the other end of radial pull rod crosses the axis of rotation and is located yoke circle opposite side. Thus, when the rotating part of the fluid machine rotates, the compensating block arranged at the other end of the radial tie rod forms an outward centrifugal force and forms a compensating force F towards the yoke ring axis to the end of the yoke ring through the radial tie rod.
It will be appreciated that in this solution, since the radial tension rods are located substantially in the radial direction of the yoke, the centrifugal force of the compensation mass can be largely converted into a compensation force F acting on the yoke towards the yoke axis, which is beneficial for increasing the compensation force F with the same mass of the compensation mass.
In addition, since the radial tie rod is in contact with the front side of the rotation direction of the rotating shaft, when the fluid machinery rotating component rotates, the radial tie rod is always in close contact with the rotating shaft under the action of inertia.
Preferably, the other end of the radial pull rod provided with the compensation block is connected to the other side of the magnetic yoke ring through a tension spring.
The other end of the radial pull rod provided with the compensation block is connected to the other side of the magnetic yoke ring through a tension spring, namely, both ends of the radial pull rod are connected to the magnetic yoke ring. Therefore, when the rotating part of the fluid machine is static, the radial pull rod can be reliably positioned, and the assembly is facilitated.
Preferably, the radial pull rod comprises a first section connected with the end part of the magnetic yoke ring and a second section provided with a compensation block, the first section is connected with the second section through a roller, the second section inclines from the roller to the radial direction, an included angle of 10-15 degrees is formed between the second section and the first section, and the roller is attached to the rotating shaft.
It can be understood that, because the first section and the second section form an included angle of 10-15 degrees, the compensation block on the second section and the connection point of the first section and the magnetic yoke ring can be approximately positioned on the same radial direction, so that the centrifugal force generated by the compensation block can be maximally improved. In addition, when the fluid machinery rotating part rotates, the roller arranged at the joint of the first section and the second section can form rolling friction with the rotating shaft, so that the friction resistance is greatly reduced, and the service life is prolonged.
Preferably, the mass of the yoke coil is m, the radius of the yoke coil is r, the rotation speed of the rotating component of the fluid machine is n, and the compensation force F and the rotation speed n form the following relationship: 2 pi2m×r×n2/3≤ F≤4π2m×r×n2/3。
It can be understood that, for a fluid machine rotating component, the mass m and the radius r of the magnetic yoke ring are fixed values. Furthermore, the rotating part of the fluid machine is subjected to an outward centrifugal force on the one hand and an inward pulling force of the coupling disk and an inward compensating force F at both ends of the yoke ring on the other hand during rotation, and the outward centrifugal force should be balanced with the inward pulling force of the coupling disk and the inward compensating force F at both ends of the yoke ring.
The invention controls the compensation acting force F and the rotating speed n within the following ranges:
2π2m×r×n2/3≤ F≤4π2m×r×n2/3，
thus, the sum of the compensating forces at both ends of the yoke is 4 pi2m×r×n 23 to 8 pi2m×r×n2In the range of/3, so as to ensure that the outward centrifugal force and the inward pulling force of the connecting disc and the inward compensating acting force F at the two ends of the magnetic yoke ring should be balanced, and further ensure that the two ends of the magnetic yoke ring are turned outwards due to the centrifugal forceThe compensation torque which is acted by the bending moment and stress compensation mechanism and overturns inwards at the two ends of the magnetic yoke ring maintains balance so as to ensure that the magnetic gap between the magnetic yoke ring and the stator is kept stable.
Therefore, the invention has the following beneficial effects: on the basis of not obviously increasing the weight and the manufacturing cost of the magnetic yoke ring, the bending strength of the magnetic yoke ring can be effectively improved, and the uniformity of magnetic gaps between the rotor and the stator is ensured.
Drawings
Fig. 1 is a schematic structural view of a rotating part of a conventional fluid machine.
Fig. 2 is a side view of fig. 1.
Fig. 3 is a schematic view showing a structure in which a conventional yoke coil is bent and inverted outward when it is subjected to a centrifugal force.
Fig. 4 is a schematic view of a first structure of the stress compensation mechanism of the present invention.
Fig. 5 is a schematic view of a second structure of the stress compensation mechanism of the present invention.
Fig. 6 is a schematic view of a third structure of the stress compensation mechanism of the present invention.
Fig. 7 is a side view of fig. 6.
In the figure: 1. the device comprises a connecting disc 2, a rotating shaft 3, a magnetic yoke ring 4, a correcting ring piece 41, a reinforcing rib piece 411, a sliding groove 42, a compensating block 43, a sliding rod 44, a pressure spring 5, a brake caliper 6, a supporting rod 61, a reinforcing rod 62, a pull rope 63, a pulley 64, a limiting ring 7, a radial pull rod 8, a roller 9 and a tension spring.
Detailed Description
The invention is further described with reference to the following detailed description and accompanying drawings.
A fluid machine rotating part stress self-adaptive structure is disclosed, wherein the fluid machine in the embodiment is a hydraulic generator, and a rotating part is a rotor in the hydraulic generator. Similarly to the prior art, as shown in fig. 1 and 2, the fluid machine rotating part includes a connecting disc 1, a rotating shaft 2 connected to the center of the disc, and a cylindrical yoke ring 3, and the edge of the connecting disc is connected to the middle position of the inner side of the yoke ring in the axial direction. When the water turbine drives the rotor to rotate through the rotating shaft, hydroelectric power generation can be realized. Of course, a stator (not shown) should be disposed outside the rotor, and since the basic structure of the hydro-generator such as the rotor and the stator belongs to the prior art, the detailed description is omitted.
Since the yoke ring has a large radius and mass and is only pulled by the connecting disc at the middle position, when the rotor rotates at a high speed, the front and rear ends of the yoke ring suspended in the air generate a radial outward centrifugal force, which forms a bending torque that bends and turns the outer end of the yoke ring outward, as shown in fig. 3, and then affects the magnetic gap between the rotor and the stator.
To this end, the invention sets up the compensating mechanism of the stress between both ends of the magnetic yoke ring and connecting disc, when the fluid machinery rotating part rotates, the compensating mechanism of the said stress produces a compensation acting force towards the axis of magnetic yoke ring to any one end of the magnetic yoke ring, the said compensation acting force forms a compensation torque turned inwards to the end of the magnetic yoke ring, in order to offset the bending torque formed by centrifugal force of the magnetic yoke ring itself effectively, and then avoid turning up and bending deformation of both ends of the magnetic yoke ring, guarantee the magnetic gap between stator and the rotor maintains stably.
As a first preferred scheme, as shown in fig. 4, the stress compensation mechanism comprises a circular correction ring plate 4 and a brake caliper 5 capable of braking the correction ring plate, wherein the outer edge of the correction ring plate is fixedly connected with the end part of the magnetic yoke ring, and the brake caliper can be fixedly arranged on a base fixed on the generator so as to brake the inner hole edge of the correction ring plate. When the fluid machinery rotating parts need to be braked for maintenance, the rotating parts can be stopped quickly by the brake caliper, so that the efficiency is improved. That is, in this solution, the leveling ring simultaneously functions like an automobile brake pad.
In addition, a plurality of reinforcing rib pieces 41 which are uniformly distributed in the circumferential direction can be arranged between the correcting ring piece and the inner side of the magnetic yoke ring, one side of each reinforcing rib piece is fixedly connected to the correcting ring piece, and a deformation gap is arranged between each reinforcing rib piece and the inner side of the magnetic yoke ring. In addition, an outwardly extending runner 411 is provided in the rib piece, and a compensating block 42 is provided in the runner.
When the fluid machinery rotating part rotates at high speed, the compensating block forms outward centrifugal force, at the moment, the centrifugal force forms an inward torque to the straightening ring piece through the reinforcing rib piece fixed on the straightening ring piece, and further forms an inward-turning compensating torque to the end part of the magnetic yoke ring through the straightening ring piece fixed on the end part of the magnetic yoke ring, so as to fully offset the outward-turning bending torque caused by the centrifugal force of the magnetic yoke ring.
It can be understood that we can ensure that the magnetic gap between the rotor and the stator is maintained stable by properly designing the weight of the compensation block, the position on the reinforcing rib and the like, so that the compensation torque is enough to balance the bending torque of the yoke ring which is overturned outwards.
It should be noted that, a plurality of reinforcing ribs may be disposed between the straightening ring pieces and the inner side of the yoke ring, and the reinforcing ribs are disposed between adjacent straightening ring pieces at intervals to increase the connection strength and rigidity between the straightening ring pieces and the yoke ring, so that the straightening ring pieces can form sufficient compensation torque for the end of the yoke ring.
Furthermore, a sliding rod 43 extending along the length direction of the sliding chute can be arranged in the sliding chute, two ends of the sliding rod are connected to two ends of the sliding chute, the compensation block is movably sleeved on the sliding rod, and two ends of the compensation block are respectively provided with a pressure spring 44 sleeved on the sliding rod, so that the compensation block is elastically positioned in the sliding chute.
When the compensation block rotates at a high speed to generate centrifugal force, the compensation block can overcome the elasticity of the outer pressure spring and move outwards, and further the centrifugal force of the compensation block is increased. By reasonably designing the elastic coefficient of the pressure spring, the compensation block can stay at a proper position in the sliding groove, and the centrifugal force of the compensation block is matched with the required compensation torque.
It should be noted that the length of the outer compression spring can be made larger than that of the inner compression spring, so as to facilitate the outward movement of the compensation block.
As a second preferred scheme, as shown in fig. 5, the stress compensation mechanism includes a plurality of support rods 6, a reinforcing rod 61, and a pull rope 62, wherein the inner ends of the support rods are connected to the connection disc near the connection with the yoke ring, the inner ends of the reinforcing rods are connected to the connection disc far from the yoke ring, the outer ends of the support rods incline towards one side of the center of the connection disc, and the reinforcing rods incline outwards from the inner ends to the outer ends and are connected to the outer ends of the support rods, so that the support rods and the reinforcing rods are connected to form a triangular bracket. In addition, a pulley 63 is arranged at the joint of the support rod and the reinforcing rod, a slidable compensating block 42 is arranged on the support rod, one end of a pull rope is connected to the end part of the magnetic yoke ring, and the other end of the pull rope is connected with the compensating block after passing through the pulley inwards.
When the fluid machinery rotating part rotates, the compensating block forms an outward centrifugal force, so that a compensating acting force F towards the axis of the yoke ring is formed on the end part of the yoke ring through the pull rope. Naturally, the pulley should be positioned as close as possible to the end face of the yoke so that the pull cord connected between the yoke and the pulley is positioned in the radial direction as possible, thereby minimizing the weight of the compensating block while ensuring a sufficient compensating force F.
Furthermore, a limit ring 64 can be sleeved on the support rod, a fastening screw capable of fixing the limit ring on the support rod is arranged on the limit ring, and one end of the limit ring, far away from the pulley, abuts against the compensation block.
Like this, when fluid machinery rotating part was static, the compensation piece received the effect of stay cord and was fixed a position reliably on the bracing piece, and the spacing ring then play the effect that makes the compensation piece location this moment, avoids the free removal of compensation piece, convenient assembly. When the fluid machinery rotating part is at high speed, the compensation block can freely slide outwards on the supporting rod to realize the compensation effect.
As a third preferred solution, as shown in fig. 6/7, the stress compensation mechanism includes a plurality of radial tie rods 7, one end of each radial tie rod is connected to one side of the end of the yoke ring, the other end of each radial tie rod crosses the rotating shaft in the middle of the connecting disc to be positioned on the other side of the yoke ring, and a compensation block is arranged at the other end of each radial tie rod.
When the rotating part of the fluid machine rotates, the compensating block forms an outward centrifugal force which, via the radial tension rods, forms a compensating force F on the end of the yoke ring towards the axis of the yoke ring. It will be appreciated that the other end of the radial tie should be brought as close as possible to the other side of the yoke so that the compensation mass has the largest radius of rotation, thereby increasing the compensation force F and advantageously reducing the mass of the compensation mass.
It should be noted that, the end of the radial tie bar connected to the end of the yoke ring is referred to as a connecting end, and the end of the radial tie bar provided with the compensating block is referred to as a free end. The radial pull rods are uniformly distributed at the end part of the magnetic yoke ring along the circumferential direction.
It will be understood that when the rotating part of the fluid machine rotates, the free end of the radial tie rod will swing back in the direction of rotation of the rotating shaft under the influence of inertia. For this purpose, the radial tie rod can be arranged in front of the direction of rotation of the rotating shaft, so that the radial tie rod can always be arranged in a tight manner on the rotating shaft and positioned when the rotating part of the fluid machine is rotating.
Furthermore, the free end of the radial tension rod, which is provided with the compensation block, is connected to the other side of the yoke ring by a tension spring 9, that is, both ends of the radial tension rod are connected to the yoke ring. Therefore, when the rotating part of the fluid machine is static, the radial pull rod can be reliably positioned, and the assembly is facilitated.
Furthermore, the radial pull rod comprises a first section connected with the end part of the magnetic yoke ring and a second section provided with a compensation block, the first section and the second section are connected through a roller 8, the roller is attached to the rotating shaft, and the connecting end and the suspension end of the radial pull rod are approximately symmetrically arranged in the magnetic yoke ring. That is, the first section and the second section of the radial pull rod are bent at the position corresponding to the rotating shaft in the middle. The included angle between the first section and the second section can be controlled within 10-15 degrees, so that the compensation block on the second section and the connection point of the first section and the magnetic yoke ring are approximately positioned in the same radial direction, and then the centrifugal force generated by the compensation block can be furthest increased, or the weight of the compensation block can be reduced as much as possible.
When the fluid machinery rotating part rotates, the roller arranged at the joint of the first section and the second section can form rolling friction with the rotating shaft. When the compensation block pulls the radial pull rod to enable the radial pull rod to elastically extend, the friction resistance between the radial pull rod and the rotating shaft can be reduced, and the service life can be prolonged.
For convenience of description, let us say that the mass of the yoke is m, the radius of the yoke is r, and the rotation speed of the rotating part of the fluid machine when operating is n. Since the mass m and radius r of the yoke are fixed values, the centrifugal force formed by the yoke is proportional to the square of the rotation speed n when the fluid machinery rotating component rotates according to the mechanics principle.
By reasonably designing the parameters such as mass and the like of the compensation block, the compensation acting force F and the rotating speed n form the following relation: 2 pi2m×r×n2/3≤ F≤4π2m×r×n2/3。
It will be understood that when the rotating part of the fluid machine is rotating, it is subjected on the one hand to an outward centrifugal force and on the other hand to an inward pulling force of the coupling disc and to an inward compensating force F at the ends of the yoke ring, and that the outward centrifugal force should be balanced by the sum of the inward pulling force of the coupling disc plus the inward compensating force F at the ends of the yoke ring.
When 2 pi2m×r×n2/3≤ F≤4π2m×r×n2And/3, the balance between the outward centrifugal force and the sum of the inward pulling force of the connecting disc and the inward compensating acting force F at the two ends of the magnetic yoke ring can be maintained, so that the bending moment of the two ends turning outwards caused by the centrifugal force of the magnetic yoke ring and the compensating torque of the stress compensating mechanism acting on the two ends turning inwards of the magnetic yoke ring are maintained, and the magnetic gap between the magnetic yoke ring and the stator is kept stable.
Claims (9)
1. A fluid machinery rotating part stress self-adaptation structure comprises a connecting disc, a rotating shaft connected to the center of the disc and a cylindrical yoke ring, wherein the edge of the connecting disc is connected to the axial middle position of the inner side of the yoke ring.
2. The adaptive structure of stress of a fluid machinery rotating part according to claim 1, wherein the stress compensation mechanism comprises a correction ring and a brake caliper capable of braking the inner side edge of the correction ring, the outer side edge of the correction ring is fixedly connected to the end of the yoke, a plurality of reinforcing ribs are uniformly distributed in the circumferential direction between the correction ring and the inner side of the yoke, one side of each reinforcing rib is fixedly connected to the correction ring, a deformation gap is formed between each reinforcing rib and the inner side of the yoke, an outwardly extending chute is formed in each reinforcing rib, and a compensation block is arranged in each chute, and forms an outward centrifugal force when the fluid machinery rotating part rotates and forms an inward-turning compensation torque to the end of the yoke through each reinforcing rib and each correction ring.
3. The adaptive structure for stress of rotating parts of fluid machinery according to claim 2, wherein a sliding rod is disposed in the sliding groove, the compensating block is fitted over the sliding rod, and compression springs fitted over the sliding rod are disposed at both ends of the compensating block, respectively.
4. The adaptive structure of stress of rotating parts of fluid machinery according to claim 1, the stress compensation mechanism comprises a plurality of supporting rods, reinforcing rods and pull ropes, the inner ends of the supporting rods are connected to the connecting disc and close to the joint of the supporting rods and the magnetic yoke ring, the inner ends of the reinforcing rods are connected with the connecting disc, the outer ends of the supporting rods incline towards one side of the center of the connecting disc, the reinforcing rods incline outwards from the inner ends to the outer ends and are connected with the outer ends of the supporting rods, a pulley is arranged at the joint of the support rod and the reinforcing rod, a slidable compensating block is arranged on the support rod, one end of the pull rope is connected with the end part of the magnetic yoke ring, the other end of the pull rope is connected with the compensation block after passing around the pulley, when the fluid machinery rotating part rotates, the compensating block forms an outward centrifugal force, and forms a compensating acting force F towards the axis of the yoke ring to the end part of the yoke ring through the pull rope.
5. The adaptive structure for stress of a rotating part of a fluid machine as claimed in claim 4, wherein a stop ring is fitted over the support rod, a fastening screw for fixing the stop ring to the support rod is provided on the stop ring, and an end of the stop ring remote from the pulley abuts against the compensation block.
6. The adaptive structure of stress of a fluid machinery rotor according to claim 1, wherein the stress compensation mechanism comprises a plurality of radial tension rods, one end of each radial tension rod is connected to one side of the end of the yoke ring, the other end of each radial tension rod is located at the other side of the yoke ring, a compensation block is arranged at the other end of each radial tension rod, the radial tension rods are attached to the front side of the rotation direction of the rotation shaft, when the fluid machinery rotor rotates, the compensation blocks form an outward centrifugal force, and a compensation acting force F towards the axis of the yoke ring is formed on the end of the yoke ring through the radial tension rods.
7. The adaptive structure for stress of rotating parts of fluid machinery according to claim 6, wherein the other end of the radial tension rod provided with the compensating block is connected to the other side of the yoke ring by a tension spring.
8. The adaptive structure of stress of rotating parts of fluid machinery according to claim 7, wherein the radial tension rod comprises a first section connected with the end of the yoke ring, a second section provided with a compensation block, the first section and the second section are connected through a roller, the second section is inclined from the roller to the radial direction and forms an included angle of 10-15 degrees with the first section, and the roller is attached to the rotating shaft.
9. The adaptive structure of stress of a rotating component of a fluid machine according to claim 4 or 6, wherein the mass of the yoke ring is m, the radius of the yoke ring is r, the rotating speed of the rotating component of the fluid machine is n, and the compensation force F and the rotating speed n form the following relationship: 2 pi2m×r×n2/3≤ F≤4π2m×r×n2/3。
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| CN202110194399.1A CN112994337B (en) | 2021-02-20 | 2021-02-20 | Fluid machinery rotating part stress self-adaptation structure |
| CN202210015278.0A CN114530979B (en) | 2021-02-20 | 2021-02-20 | Stress self-adaptive structure of fluid machinery rotating part |
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| CN203219037U (en) * | 2013-03-07 | 2013-09-25 | 重庆云河水电股份有限公司 | Generator rotor structure |
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| CN203617807U (en) * | 2013-10-25 | 2014-05-28 | 怀化沅江电力开发有限责任公司洪江水力发电厂 | Hydraulic turbine generator rotor spider with flange hub |
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| CN203219037U (en) * | 2013-03-07 | 2013-09-25 | 重庆云河水电股份有限公司 | Generator rotor structure |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN114530979A (en) | 2022-05-24 |
| CN114530979B (en) | 2023-12-12 |
| CN112994337B (en) | 2022-02-18 |
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Effective date of registration: 20220408 Address after: 311500 No. 99, Hongqi South Road, Fuchunjiang Town, Tonglu County, Hangzhou City, Zhejiang Province Patentee after: Hangzhou Zhefu Nuclear Power Equipment Co.,Ltd. Address before: 311504 Hongqi South Road, the Fuchun River Town, Tonglu, Hangzhou, Zhejiang 99 Patentee before: ZHEJIANG FUCHUNJIANG HYDROPOWER EQUIPMENT Co.,Ltd. |