Elastic driving plate supporting structure in turbocharger

Abstract

The utility model discloses a driving plate elastic supporting structure in a turbocharger. The elastic supporting structure is arranged in a radial gap between a driving plate and a mounting plate; the elastic supporting structure is an integrated annular elastic piece, and the elastic piece is provided with an outer supporting position making contact with the inner surface of the drive plate and further provided with an inner supporting position making contact with the outer surface of the installation protruding ring on the installation plate. In the application, the elastic piece is arranged between the driving plate and the mounting convex ring, so that the elastic force can be continuously provided, and the elastic force can ensure that the driving plate and the mounting plate are concentric, so that deflection is avoided, and the adjustment states of all the blades can be kept consistent to the greatest extent when the angles of the blades are adjusted.

Description

Technical Field

[0001] The utility model belongs to the technical field of nozzle ring structures in turbochargers, and in particular relates to a dial elastic support structure in a turbocharger. Background Art

[0002] Turbochargers are a crucial component of current automotive engine systems, allowing more air to enter the cylinders for a more complete mixing and combustion with fuel, significantly increasing engine power and torque. Turbochargers with adjustable nozzle ring vanes feature a nozzle ring structure with a rotatable ring of vanes. A rotatable dial controls the vane rotation, adjusting the intake air volume.

[0003] Currently, in the nozzle ring of the existing technology, the dial is positioned axially and radially on the mounting plate. The radial positioning of the dial depends on the matching of the dial's inner diameter and the mounting plate's outer diameter. This gap has a significant impact on the consistency and performance of blade opening control. When the gap is small, the dial and mounting plate have good concentricity, accurately controlling the angles of multiple blades and achieving good blade opening consistency. However, due to high-temperature thermal deformation and the influence of engine particles, the dial is prone to jamming. When the gap is large, the concentricity of the dial and mounting plate is poor. During actual operation, the dial and mounting plate only contact on one side, resulting in different positions of the driven fork controlled by the dial slot, different blade opening sizes, and different sizes, directions, and positions of the channels formed by each two blades. As a result, the airflow angle and gas flow rate entering the turbine are also different, resulting in reduced turbine performance and affecting engine performance.

[0004] Therefore, based on the above problems, the present application further designs and improves the structure in the nozzle ring. Utility Model Content

[0005] In response to the above deficiencies in the prior art, the present invention provides an elastic support structure for a dial in a turbocharger, which can well achieve accurate centering between the dial and the mounting plate, so that the opening angle of each blade is controlled to be consistent when the dial rotates.

[0006] The utility model solves the problem through the following technical solutions.

[0007] A dial elastic support structure in a turbocharger is provided in a radial gap between the dial and a mounting plate; the elastic support structure is an integral annular elastic member having an outer support position in contact with the inner surface of the dial and an inner support position in contact with the outer surface of a mounting cam on the mounting plate.

[0008] In the present application, an elastic member is provided between the dial and the mounting protrusion ring to continuously provide elastic force, which can ensure that the dial and the mounting plate are concentric, avoid deflection, and ensure that when the blade angle is adjusted, the adjustment state of all blades can be kept consistent to the greatest extent possible.

[0009] In a preferred embodiment, the radial gap is an annular gap between the dial and the mounting protruding ring, and the elastic member is arranged in the annular gap, so that the assembly structure is compact.

[0010] In a preferred embodiment, the outer support positions and the inner support positions on the elastic member are alternately arranged. The supporting force distribution of this structure is stable, the elastic supporting force is evenly distributed, and the radial support and centering performance are good.

[0011] In a preferred embodiment, the outer support position is an arc-shaped protruding segment, the protruding apex of which contacts the inner surface of the dial. Specifically, the arc-shaped protruding segment can be squeezed and provide an outward elastic force for elastic support.

[0012] In a preferred embodiment, the inner support position is an arc segment, the inner surface of the arc segment matches the contour of the outer surface of the mounting convex ring, can fit well on the outer surface of the mounting convex ring, and can also slide relative to each other when necessary. At the same time, the surface support between the two can provide good supporting force and improve the support strength.

[0013] In a preferred embodiment, the elastic member is an integrated flat metal elastic ring belt, which has a simple structure, is easy to process and assemble, and has good elastic support.

[0014] Compared with the prior art, the present invention has the following beneficial effects: it provides an elastic support structure for a dial in a turbocharger, which can well achieve accurate centering between the dial and the mounting plate, so that the opening angle of each blade is controlled to be consistent when the dial rotates. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is the front view of the elastic member in the utility model.

[0016] Figure 2 It is a three-dimensional diagram of the elastic member in the present invention.

[0017] Figure 3 This is a front view of the nozzle ring in the present invention.

[0018] Figure 4 It is a three-dimensional diagram of the nozzle ring in the present invention.

[0019] Figure 5 This is a partial enlarged view of the nozzle ring in the present invention.

[0020] Figure 6 It is a partial enlarged view of the installation disk in the utility model.

[0021] Figure 7 It is a partial cross-sectional view of the nozzle ring in the present invention.

[0022] Figure 8 for Figure 7 Magnified view of area A in center. DETAILED DESCRIPTION

[0023] The present invention is described in further detail below with reference to the accompanying drawings and specific implementation methods.

[0024] In the following embodiments, the same or similar numbers throughout represent the same or similar elements or elements with the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be understood as limiting the present invention.

[0025] In the description of the present invention, it should be understood that the terms: center, longitudinal, transverse, length, width, thickness, up, down, front, back, left, right, vertical, horizontal, top, bottom, inside, outside, clockwise, counterclockwise, etc. indicating directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and therefore cannot be understood as limiting the present invention. In addition, the terms: first, second, etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features shown. In the description of the present invention, unless otherwise clearly specified and limited, the terms: install, connect, connect, etc. should be understood in a broad sense, and ordinary technicians in this field can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0026] See also Figures 1 to 8 , the present application relates to a nozzle ring, which has a dial elastic support structure.

[0027] Specifically, the nozzle ring in the present application includes: a mounting disk 2, a rotatable blade shaft 4 is provided on the mounting disk 2, one end of the blade shaft 4 is provided with a blade, and the other end is positioned on the dial 3; a dial 1, the dial 1 is fitted on the mounting disk 2 and can rotate relatively, the outer end of the dial 3 is limited to the dial 1, and the angle of the blade is adjusted as the dial 1 rotates; a concentric mounting convex ring 29 is provided on the mounting disk 2, and the blade shaft 4 is rotatably passed through the mounting hole on the mounting convex ring 29; the dial 1 is rotatably arranged on the radial outside of the mounting convex ring 29, and there is a gap 5 between the inner surface of the dial 1 and the outer surface of the mounting convex ring 29, and an elastic member 6 is provided in the gap 5, and the elastic force provided by the elastic member 6 makes the dial 1 concentric with the mounting disk 2.

[0028] Specifically, let's look at the dial elastic support structure in the present application. As shown in the figure, an elastic member 6 is provided between the dial 1 and the mounting protrusion 29, which can continuously provide elastic force. This elastic force can ensure that the dial 1 is concentric with the mounting plate 2, avoid deflection, and ensure that when the blade angle is adjusted, the adjustment state of all blades can be kept consistent to the greatest extent possible.

[0029] Specifically, in the present application, the gap 5 is an annular gap, and the elastic member 6 is an integrated annular elastic member disposed in the annular gap. This has a simple structure, and the integrated annular structure ensures uniform and consistent elastic force in all radial directions. In a preferred embodiment, the elastic member 6 is an integrated flat metal elastic ring band, which has a simple structure, is easy to process and assemble, and provides good elastic support.

[0030] Furthermore, in the present application, a stop boss 26 with a smaller protrusion height than the mounting ring 29 is provided on the outer side of the mounting ring 29. The elastic member 6 is disposed on the stepped surface between the mounting ring 29 and the stop boss 26, ensuring that the elastic member 6 is stably positioned after assembly and prevents it from falling out. The other side of the elastic member 6 is restrained by the dial 3. A radial gap exists between the radially outer surface 26 of the stop boss 26 and the inner surface 16 of the dial 1. This gap ensures that even small axial excursions of the dial 1 will not interfere with or become stuck.

[0031] Further, from the attached Figure 1 and attached Figure 2It can be seen that in the present application, the elastic member 6 has an outer support position 61 in contact with the inner surface of the dial 1 and an inner support position 62 in contact with the outer surface of the mounting convex ring 29, which are staggered. The support force distribution of this structure is stable, the elastic support force is evenly distributed, and the radial support and centering performance are good. In the specific structure, the outer support position 61 is an arc-shaped protruding segment, and the protruding vertex position of the arc-shaped protruding segment is in contact with the inner surface 16 of the dial 1. Specifically, the arc-shaped protruding segment can be squeezed and provide an outward elastic force for elastic support. The inner support position 62 is an arc-shaped segment, and the inner surface of the arc-shaped segment matches the contour of the outer surface 25 of the mounting convex ring 29, can fit well on the outer surface 25 of the mounting convex ring 29, and can also slide relative to each other when necessary. At the same time, the surface support between the two can provide good supporting force and improve the supporting strength.

[0032] The nozzle ring in the prior art does not have the elastic part structure of the present application. When this type of nozzle ring is working, especially at the maximum or minimum opening, the dial and the mounting plate do not rotate concentrically, but the dial rotates around the limit point between the inner diameter of the dial and the mounting plate. The farther the dial is from the limit point, the greater the angle of rotation of the dial around the limit point, resulting in a greater rotation angle of the dial-driven blade farther from the limit point than the rotation angle of the dial-driven blade closer to the limit point, thereby causing the dial to control the opening of each blade inconsistently, resulting in different sizes, directions, and positions of the channels formed by each two blades, and different airflow angles and gas flow rates entering the turbine, thereby reducing turbine performance and affecting engine performance.

[0033] In the present application, an innovative assembly structure is adopted and elastic parts are provided, which has the following advantages.

[0034] (1) A specially designed elastic member is used. The elastic member is installed between the inner hole of the dial and the outer diameter of the mounting plate. Multiple line contacts are used between the dial and the elastic ring. The elastic member can achieve accurate centering between the dial 1 and the mounting plate 3 through multiple line contacts, so that the opening angle of each blade is controlled to be consistent when the dial rotates. The position and direction of the blade controlled at each dial position are the same, so that the gas entering the turbine from the 360° circumference of the turbine outer diameter is uniform and consistent in direction relative to the turbine. The airflow loss that drives the turbine to work is small, the turbine efficiency is high, and it is consistent with the theoretical design.

[0035] (2) At the limit opening, the dial will not rotate around the limit point between the inner diameter of the dial and the mounting plate. The dial controls the opening of each blade to be consistent, resulting in the size, direction, and position of the channel formed by every two blades being the same. The airflow angle and gas flow entering the turbine are also the same, and the turbine performance is consistent with the design.

[0036] (3) When the engine calibration strategy requires the flow rate at the nozzle ring's extreme hard limit opening as the calibration starting point, this structure will evenly distribute each blade around the turbine, resulting in good flow consistency at the turbocharger calibration point and good engine performance consistency.

[0037] (4) Even if the inner hole of the dial increases under high temperature conditions, the dial can recover through pre-elastic deformation to make up for the gap, thereby achieving accurate centering under high temperature conditions.

[0038] (5) When the engine is running, vibration will be transmitted to the dial. The elastic ring structure between the dial and the mounting plate can absorb the vibration from the engine, and the dial will not move relative to the mounting plate, thereby reducing the wear between the dial and the shift fork, and reducing the wear between the dial and the mounting plate.

[0039] As described above, the present invention provides a nozzle ring for accurate flow control in a VNT supercharger. An elastic member is designed between the dial and the mounting plate, which can well achieve accurate centering between the dial and the mounting plate, so that the opening angle of each blade is controlled to be consistent when the dial rotates.

[0040] The protection scope of the present invention includes but is not limited to the above embodiments. The protection scope of the present invention is based on the claims. Any replacement, deformation, and improvement of the technology that can be easily thought of by technicians in this field fall within the protection scope of the present invention.

Claims

1. The dial elastic support structure in the turbocharger is characterized by: The elastic support structure is arranged in a radial gap (5) between the dial (1) and the mounting plate (2); The elastic support structure is an integrated annular elastic member (6), the elastic member (6) having an outer support position (61) in contact with the inner surface of the dial (1), and an inner support position (62) in contact with the outer surface of the mounting convex ring (29) on the mounting plate (2).

2. The dial elastic support structure in the turbocharger according to claim 1, characterized in that: The radial gap (5) is an annular gap between the dial (1) and the mounting convex ring (29), and the elastic member (6) is arranged in the annular gap.

3. The dial elastic support structure in the turbocharger according to claim 2, characterized in that: The outer support positions (61) and the inner support positions (62) on the elastic member (6) are arranged alternately.

4. The dial elastic support structure in the turbocharger according to claim 3, characterized in that: The outer support position (61) is an arc-shaped protruding segment, and the protruding vertex of the arc-shaped protruding segment contacts the inner surface (16) of the dial (1).

5. The dial elastic support structure in the turbocharger according to claim 3, characterized in that: The inner support position (62) is an arc segment, and the inner surface of the arc segment matches the contour of the outer surface (25) of the mounting convex ring (29).

6. The dial elastic support structure in a turbocharger according to any one of claims 1 to 5, characterized in that: The elastic member (6) is an integrated flat metal elastic ring band.

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