Damping unit

FIELD: mechanical engineering.

SUBSTANCE: damping unit comprises main damper and additional damper. The main damper is provided with movable member having bearing for the flexible support of the rotor and centering springs mounted in the top section. The damper is pivotally mounted in the tank filled with damping fluid. The additional damper has damping step cylinder whose bottom section of greater diameter is mounted in the space filled with damping fluid, and top section of smaller diameter receives the adjusting ring that embraces the semiaxle of the flexible support with a spaced relation. The damping cylinder is suspended in the space by means of additional centering springs secured to the top section of smaller diameter.

EFFECT: enhanced damping.

19 cl, 12 dwg

 

The invention relates to mechanical engineering and can be used in rapidly rotating rotors and machines, such as energy storage, centrifuges.

Known damping the reference node of a rapidly rotating vertical rotor [Japanese application No. 55-32927, CL F 16 C 27/00, 1974], made in the form of a cylindrical damping elements mounted in the tank with damping fluid, attached to one element of the bearing end supports. On the other cylindrical damping element installed between the axle and the first cylindrical element fixed spans with a certain radial clearance the axle adjustment ring, which is installed on a vertical helical spring and interacts with the axle at high amplitudes of oscillation of the rotor, campfire these oscillations under strong perturbations.

A disadvantage of the known construction is that the damping cylinders are interconnected through the damping gaps, which complicates the configuration of the damper for damping of multifrequency oscillations of the rotor.

Known damping site rapidly rotating vertical rotor [Japanese application No. 55-32928, CL F 16 C 27/00, 1974], made in the form of three cylindrical damping elements coaxially installed one in another tank with campfireusa the liquid, mounted on two bearing elements for end supports. Two cylindrical damping elements mounted covering, with some radial clearance the axle of the rotor adjustment ring which interacts with the axle at high amplitudes of oscillation of the rotor, campfire these oscillations under strong perturbations.

A disadvantage of the known construction is that the damping cylinders are interconnected through the damping gaps, which complicates the configuration of the damper for damping vibrations of the rotor of varying intensity and at different frequencies.

Closest to the invention, the technical solution is damping the node vectors of the vertical rotor [Russian Federation Patent RU 2044937, CL F 16 F 9/10, 15/023, 1992], which includes the main damper containing a movable element with a bearing for a flexible rotor supports and centering springs in the upper part, pivotally supported in the tank filled with damping fluid, and additional damper containing a damping cylinder with adjustment ring. The damping cylinder is made of stepped form, the bottom of which has a larger diameter and freely installed in the cavity with a damping fluid, and in the upper part of smaller diameter mounted adjustment ring, covering the gap of the m axis of the flexible support. At the lower end of the damping cylinder is made plot conical shape or the bottom of the cavity is made with a section of conical shape.

The design is known damping node does not provide a sufficiently stable and effective damping of vibrations of the rotor in emergency mode when interacting axis with an adjustment ring due to the displacement of the damping fluid in the damping gap and separation of the damping cylinder from the bottom of the cavity with intense vibrations. In addition, when the separation of the damping cylinder from the bottom of the cavity is hampered his self-centering on the bottom of the cavity, which delays the output of the rotor of the operation mode on the adjustment ring.

The problem to which the invention is directed, is to increase the efficiency of the damper and the stability of its characteristics.

The technical result of the invention is to provide a simple construction of the damper, ensuring reliable and efficient damping of vibrations of the rotor at high amplitudes of its movement and strong interactions.

For this damping in the node vectors of the vertical rotor, which includes a main damper containing a movable element with a bearing for a flexible rotor supports and centering springs in the upper part, pivotally supported in the tank filled with damping fluid and an additional damper, containing a damping cylinder of stepped form, the bottom of which has a larger diameter and placed in the cavity with a damping fluid, and in the upper part of smaller diameter mounted adjustment ring covering a gap axis of the flexible support, the damping cylinder is suspended in a cavity in the additional centering springs attached to the upper portion of smaller diameter.

Additionally, a damping node radial clearance between the damping cylinder and the housing is partially closed annular radial projection.

In addition, a damping node annular radial projection is made approximately at mid-length of the lower portion of larger diameter.

Additionally, a damping node radial clearance to the annular radial projection is 0,002-0,01 from the diameter of the ledge.

In addition, a damping node annular radial projection is made on the lower part of the damping cylinder.

Additionally, a damping node ledge made in the form of the outer ledge.

In addition, a damping node ledge made in the form of internal ledge.

Additionally, a damping node on the damping cylinder made additional internal annular radial projection.

In addition, a damping node annular radial projection is made on the surface the minute cavity.

Additionally, a damping node ledge performed on the convex surface of the cavity.

In addition, the damping of the node projection is performed on the concave surface of the cavity.

Additionally, a damping node on the concave surface of the cavity is made additional annular radial projection.

In addition, a damping node on the convex cavity surface approximately opposite the tab on the damping cylinder made additional annular radial projection.

Additionally, a damping node on a concave cavity surface approximately opposite the tab on the damping cylinder made additional annular radial projection.

In addition, a damping node on the surface of the cavity is made additional annular radial projection located above the radial protrusion on the damping cylinder and limiting the axial displacement of the additional damper.

Additionally, a damping node on the damping cylinder made additional annular radial projection located under the radial projection on the surface of the cavity and limiting axial movement of the additional damper.

In addition, a damping node radial protrusion is made in the form prescribed in the groove circlips.

In addition, a damping node augment the performance communications annular radial projections made in the form prescribed in the groove circlips.

Additionally, a damping node a movable element pivotally supported on a flexible membrane mounted on its edge in the vessel with axial clearance from the floor.

1 schematically shows a vertical section of the rotor damping unit; figure 2 shows an embodiment of the damping node with an external annular radial projection on the damping cylinder; figure 3 shows an embodiment of a node with an internal annular radial projection on the damping cylinder; figure 4 shows an embodiment with the outer and inner annular radial projections on the damping cylinder; figure 5 shows an embodiment of a node with an annular radial projection on the concave surface of the cavity; figure 6 shows a variant of execution of the node with the radial projection on the convex surface of the cavity; 7 shows an embodiment of a node with the radial projections on the concave and convex the cavity surface; Fig shows an embodiment of a node with an outer radial ledge on the damping cylinder and a radial projection on the convex surface of the cavity; figure 9 shows an embodiment of a node with internal radial projection on the damping cylinder and a radial projection on the concave surface of the cavity; figure 10 shows an embodiment of a node with an outer radial ledge on the damping Qili is Dreux in the form of a spring ring; figure 11 shows an embodiment of a node with the radial projections in the form of spring rings on the concave and convex surfaces of the cavity and the damping cylinder; Fig shown embodiment of a damping node with an outer radial ledge on the damping cylinder, a spring ring on the concave surface of the cavity and a movable element pivotally supported on a flexible membrane.

Damping node includes a rotor 1 with radius 2, in which the elastic support in the form of needles 3, based on the thrust bearing 4 bearing support mounted in the upper part of the rolling element 5 of the main damper, lower part of which is installed on the hinge 6 in the tank 7 with the damping fluid in the housing 8. The movable element is held in the vertical position of the centering springs 9. Additional damper includes a damping cylinder 10 of stepped form, the lower part 11 which has a larger diameter and is installed in the cavity 12 with the damping fluid. In the upper part of the damping cylinder 10, which has a smaller diameter fixed adjustment ring 13, covering with a clearance of the axle 2. Damping cylinder 10 is suspended in the cavity 12 for additional centering springs 14. Spring 14 one end of the fixed upper part of the damping cylinder 10 of smaller diameter with the sleeve 15, the other end of the casing 8 so what damping cylinder 10 does not touch any of the walls or bottom of the cavity 12, or other stationary parts of the damping of the site. Under the influence of the weight of the damping cylinder additional SAG springs on a slight angle α.

In an embodiment of the damping node in figure 2 on the damping cylinder 10, approximately in the middle of the lower part 11 is made of the outer radial ledge 16. The annular radial projection 16 with a diameter of D overlaps with radial clearance Δformed in the cavity 12 between the lower part 11 of the damping cylinder 10 and the housing 8. This radial projection 16 on diameter D forms a small radial clearance δ from the concave wall of the cavity 12. Radial clearance δ to the annular radial projection 16 is 0,002÷0,01 from the diameter D of the projection 16, i.e. it is the ratio of δ=(0,002÷0,01)D.

In an embodiment of the damping node figure 3 on the damping cylinder 10, approximately in the middle of the lower part 11 internal radial projection 17 with a diameter D. the Annular radial projection 17 with a diameter of D overlaps with radial clearance Δformed in the cavity 12 between the lower part 11 of the damping cylinder 10 and the housing 8. When this radial protrusion 17 according to the diameter D forms a small radial gap 6 from the convex wall of the cavity 12.

In a variant of the implementation of the Oia damping node in figure 4 on the damping cylinder 10, approximately in the middle of the lower part 11 is made of the outer 16 and more, located in front of it, internal 17 radial projections, which are made with a small radial clearance from the concave and convex walls of cavity 12, respectively.

In an embodiment of the damping node figure 5 on the concave surface of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of a radial protrusion 18 of diameter D. the Annular radial projection 18 with a diameter of D overlaps with radial clearance Δformed in the cavity 12 between the lower part 11 of the damping cylinder 10 and the housing 8. When this radial protrusion 18 on the diameter D forms a small radial gap 6 with the outer wall of the bottom part 11 of the damping cylinder 10.

In an embodiment of the damping node figure 6 on the convex surface of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of a radial protrusion 19 of diameter D. the Annular radial projection 19 with a diameter of D overlaps with radial clearance Δformed in the cavity 12 between the lower part 11 of the damping cylinder 10 and the housing 8. When this radial protrusion 19 on the diameter D forms a small radial clearance δ to the inner walls of the lower part 11 of the damping cylinder 10.

In an embodiment of dempf the dominant node 7 on concave and convex surfaces of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of radial projections 18 and 19, respectively. The radial projections 18 and 19 are made with a small radial clearance from the inner and outer walls of the bottom part 11 of the damping cylinder 10, respectively.

In the embodiment, the damping of the node on Fig on the damping cylinder 10, approximately in the middle of the lower part 11 is made of the outer radial projection 16 and the convex surface of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of a radial protrusion 19. The radial projection 16 is made with a small radial clearance from the concave wall of the cavity 12, and the radial protrusion 19 is made with a small radial clearance from the inner wall of the lower part 11 of the damping cylinder 10.

In an embodiment of the damping node figure 9 on the damping cylinder 10, approximately in the middle of the lower part 11 internal radial projection 17 and the concave surface of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of a radial protrusion 18. The radial protrusion 17 is made with a small radial clearance from the convex wall of the cavity 12, and the radial protrusion 18 is made with a small radial clearance from the outer walls of the bottom part 11 of the damping cylinder 10.

In the embodiment, in the execution of the damping node figure 10 on the damping cylinder 10, approximately in the middle of the lower part 11 is made of the outer radial protrusion in the form of a spring ring 20 of circular cross section, is installed in the groove of the cylinder. Snap ring 20 is installed with a small radial clearance from the concave wall of the cavity 12.

In an embodiment of the damping node figure 11 on concave and convex surfaces of the cavity 12, about opposite the middle of the lower part 11 of the damping cylinder 10 is made of radial projections in the form of spring rings 21 and 22 respectively. Snap rings 21 and 22 are installed in grooves in the walls of the cavity with a small radial clearance from the inner and outer walls of the bottom part 11 of the damping cylinder 10, respectively. On the damping cylinder below the ring 22 is installed an additional snap ring 23.

In the embodiment, the damping of the node on Fig on the damping cylinder 10, approximately in the middle of the lower part 11 is made of the outer radial projection 16, above which the body is equipped with an additional snap ring 24. The radial projection 16 is made with a small radial clearance from the concave wall of the cavity 12. The movable element 5 hinge 6 is mounted on a flexible membrane 25. The membrane 25 on its edge inserted in the tank 7 with axial clearance from the floor.

The operation of the damping node is as follows.

the ri casting of the rotor 1 during the rotation of its low-frequency oscillations, for example, vibrations during acceleration from unbalance of the rotor, and the low-frequency and high-frequency fluctuations in the rotation speed at which the vibration amplitude is not very large, and the gap between the adjustment ring 13 and the axle 2 is not selected, transmitted through the sample needle 3 and the thrust bearing 4 bearing on the upper part of the rolling element 5 in the form of a cylinder, causing the movable element 5 tilts in the tank 7 with a damping fluid, swinging on the hinge 6. When such movements of the rolling element 5 arise elastic restorative force upon deformation of the centering springs 9 and the damping force when the displacement of the damping fluid, mainly in the radial gap between the movable element 5 and the housing 8. Elastic and damping forces stabilize the rotation of the rotor and prevent or dampen its vibrations.

With strong impacts on the spinning rotor 1, in which the amplitude is greater than the magnitude of the gap between the axle 2 and the adjustment ring 13, the axle 2 is in engagement with the ring 13 and rejects the upper part of the damping cylinder 10. Since the damping cylinder 10 is freely suspended in the cavity 12 for additional centering springs 14, he bends and the lower part 11 of the damping cylinder 10 is moved in the cavity 12 so that the top e is half of radially moved in one direction, and the bottom half is moved radially in the opposite direction. In the interaction of axis 2 with an adjustment ring 13 there are additional elastic force from the additional centering springs 14 and additional damping forces from movement of the damping cylinder 10 in the cavity 12 with the damping fluid acting on the rotor 1, which reduce the amplitude of vibrations of the rotor 1. When reducing the vibration amplitude of the rotor 1 axis 2 out of engagement with the adjustment ring 13, and the damping cylinder 10 is centered in the housing 8 under the action of elastic forces additional centering springs 14.

When working damping host of options complete with ledges 16-22 axis 2 rejects the upper part of the damping cylinder 10, resulting in a selected small gap δ between the diameter D of the projections 16, 20 or 17 on the cylinder or ridges 18, 21 or 19, 22 on the walls of the cavity, regardless of the execution.

The bottom part 11 of the damping cylinder 10 is moved in the cavity 12 so that its upper half moves radially in one direction, and the bottom half is moved radially in the other side, leaning on the ledge, as the center of rotation. Because the tabs 16-22 made approximately in the middle of the lower part 11 of the damping cylinder 10, the efforts on the ledges minor because, if the cluster equilibrium damping forces in the upper and lower parts of the damping cylinder. The axial displacement of the damping fluid in the gap Δ between the cavity wall 12 and the bottom part 11 of the damping cylinder in these versions of the damping of the site is difficult annular projections and virtually absent in embodiments using two tabs at the same time. As a result of this damping forces are mainly due to the tangential flow of the damping fluid in the cavity 12, which provides stable characteristics of the site in different modes and prevents splashing of damping fluid from the housing 8 with intensive interactions.

The use of spring rings 20-22 to perform radial protrusions simplifies the manufacture of the damping of the node.

In the interaction of axis 2 with an adjustment ring 13 can be vertical forces that lead to the emergence of the lower part 11 of the damping cylinder 10 from the cavity 12. To limit this floating on the damping cylinder installed snap ring 23 (11), which limits the axial displacement of the damping cylinder when interacting with placed on it by a spring ring 22 mounted in the housing 8. In an embodiment in Fig snap ring 24 mounted in the housing 8, limits the axial displacement of the lower part 11 of the damping cylinder 10 when Samadashvili performed on him annular projection 16.

When the radial vibrations of the rotor inevitably arise axial load on the thrust bearing 4. These loads are effectively reduced by the axial displacement of the damping element 5 on the elastic membrane 25 mounted on its edge in the tank 7 filled with damping fluid, with axial clearance from the floor. When the deflection of the membrane 23 through the movement of the damping fluid between the membrane 23 and the housing 8 arise damping forces, which reduce the load on the thrust bearing 4 and reduce vibrations of the rotor 1.

1. Damping the site of a rapidly rotating vertical rotor, which includes a main damper containing a movable element with a bearing for a flexible rotor supports and centering springs in the upper part, pivotally supported in the tank filled with damping fluid, and additional damper containing a damping cylinder of stepped form, the bottom of which has a larger diameter and placed in the cavity with a damping fluid, and in the upper part of smaller diameter mounted adjustment ring covering a gap axis of the flexible support, wherein the damping cylinder is suspended in a cavity in the additional centering springs attached to the upper portion of smaller diameter.

2. Damping the node according to claim 1, characterized in that the radial clearance between the damping qi is Indra and the housing is partially closed annular radial projection.

3. Damping the node according to claim 2, characterized in that the annular radial projection is made approximately at the mid-length of the lower portion of larger diameter.

4. Damping the node according to claim 2, characterized in that the radial gap to the annular radial projection is 0,002-0,01 diameter of the ledge.

5. Damping the node according to claim 2, characterized in that the annular radial projection is made on the lower part of the damping cylinder.

6. Damping the node according to claim 5, characterized in that the protrusion is made in the form of the outer ledge.

7. Damping the node according to claim 5, characterized in that the protrusion is made in the form of internal ledge.

8. Damping the node according to claim 6, characterized in that the damping cylinder made additional internal annular radial projection.

9. Damping the node according to claim 2, characterized in that the annular radial projection is made on the cavity surface.

10. Damping the node according to claim 9, characterized in that the projection is made on the convex surface of the cavity.

11. Damping the node according to claim 9, characterized in that the projection is made on the concave surface of the cavity.

12. Damping the node of claim 10, characterized in that the concave surface of the cavity is made additional annular radial projection.

13. Damping the node according to claim 6, characterized in that on the convex surface of the cavity is ome opposite ledge on the damping cylinder made additional annular radial projection.

14. Damping the node according to claim 7, characterized in that the concave cavity surface approximately opposite the tab on the damping cylinder made additional annular radial projection.

15. Damping node in one of the pp.5-8, 13 and 14, characterized in that the cavity surface is made more annular radial projection located above the radial protrusion on the damping cylinder and limiting the axial displacement of the additional damper.

16. Damping node in one of PP-12, 13 and 14, characterized in that the damping cylinder made additional annular radial projection located under the radial projection on the surface of the cavity and limiting axial movement of the additional damper.

17. Damping node according to one of claim 2 to 14, characterized in that the radial protrusion is made in the form prescribed in the groove circlips.

18. Damping site PP or 12, characterized in that the additional annular radial projection made in the form prescribed in the groove circlips.

19. Damping host by clause 16, wherein the additional annular radial projection made in the form prescribed in the groove circlips.

20. Damping node according to one of claims 1 to 7, 12 and 13, characterized in that the moving element of the ball of the IRNA supported on a flexible membrane, set on its edge in the vessel with axial clearance from the floor.



 

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