CN107882903A - A kind of arc cluster spring of the avette tail end connection of goose - Google Patents

Abstract

The invention discloses an arc-shaped combined spring for a dual-mass flywheel, which includes an outer spring and an inner spring, wherein the outer spring includes an outer spring connecting ring and an outer spring movable ring, and the outer spring connecting ring is arranged on the end side of the outer spring. The spring at the connecting ring of the outer spring is wound into a circular dead ring; the inner spring includes the connecting ring of the inner spring and the movable ring of the inner spring, the connecting ring of the inner spring is arranged at the end side of the inner spring, and the spring at the connecting ring of the inner spring is wound into an oval shape Dead ring; the outer spring and the inner spring are fit and connected by snapping the elliptical major axis side of the inner spring connecting ring into the gap of the outer spring connecting ring. The invention reduces the stress in the connecting area of the outer spring and the inner spring, the inner spring no longer falls into the outer spring, significantly enhances product performance and quality stability, and avoids spring failure. Compared with the products in the prior art, the operation procedure is reduced and the cost is reduced.

Description

An arc-shaped composite spring connected at the end of an oval

technical field

The invention relates to an arc-shaped composite spring for a double-mass flywheel, in particular to a composite spring whose tail end is connected in an oval shape.

Background technique

Dual-mass flywheel torsional vibration damper, referred to as dual-mass flywheel, is a very effective device for reducing the torsional vibration of the automobile power transmission system. On the engine flywheel, a dual-mass flywheel type torsional vibration damper is formed, so that the engine flywheel has multiple functions, not only has its original function, but also has the function of a torsional vibration damper, and because of its damping spring The installation radius is larger, the stiffness of the spring is smaller, the relative torsion angle is larger, and the vibration reduction effect is more ideal. In addition, due to the uniqueness of its structure, the change of its mass and stiffness can be used to adjust the torsional vibration inherent characteristics of the drive train, reduce the resonance speed of the drive train, and use its damping to attenuate the vibration amplitude of the system.

With the improvement of engine power, the single arc shock absorbing spring can no longer meet the technical requirements. At the same time, corresponding spring stiffnesses (Nm/°) are required in different driving states. The combined inner and outer spring can provide a solution to the above problems. The outer spring provides primary stiffness, which can meet the stiffness requirements of the engine starting and low-speed section, and the high-speed section is acted by the inner and outer combined springs at the same time. The difference between the arc spring and other straight springs is that the pitch between the inner and outer sides of the spring is inconsistent, resulting in unstable surface stress of the spring, with the inner side being larger and the outer side being smaller. Therefore, relatively speaking, the design and processing requirements of the spring are relatively high.

Due to the harsh working environment and unstable stress of the double-mass arc spring, it is easier to break than a straight spring. In particular, the inner spring must be fixed with the outer spring. If the inner spring is not firmly fixed and slides into the outer spring, it will easily squeeze into the gap of the outer spring, which will accelerate the breakage of the spring.

In the prior art, the inner spring is interfering with the cover, and then the inner spring is inserted into the outer spring. Two levels of stiffness are achieved and the inner and outer springs are fixed. However, under this technical solution, the part where the cover is connected to the spring is an interference fit, and there are static and dynamic stresses during operation, so it is easy to break in this area. At the same time, the installation of the cover and the spring requires additional machines and tooling, which increases the process and increases the manufacturing cost. The automotive industry has high quality and stability requirements, and the failure of core power components will lead to product recalls from the market, damage to the company's reputation, and even personal safety accidents. Therefore urgently need to solve above-mentioned technical problem.

Contents of the invention

In view of the above-mentioned defects in the prior art, the technical problem to be solved by the present invention is how to reduce or avoid the stress in the connection area of the outer spring and the inner spring, reduce the production and assembly process of the arc spring, and reduce the cost.

In order to achieve the above object, the present invention provides an arc-shaped combined spring for a dual-mass flywheel, including an outer spring and an inner spring, wherein the outer spring includes an outer spring connecting ring and an outer spring movable ring, and the outer spring connecting ring is arranged on the outer On the end side of the spring, the spring at the connecting ring of the outer spring is wound into a circular dead ring. The inner spring includes the connecting ring of the inner spring and the movable ring of the inner spring. It is wound into an elliptical dead loop, and the outer spring and the inner spring are matched and connected by snapping the elliptical major axis side of the inner spring connecting ring into the gap of the outer spring connecting ring.

Further, the diameter of the major axis of the ellipse of the connecting ring of the inner spring is larger than the diameter of the movable ring of the inner spring, and the diameter of the minor axis of the ellipse of the connecting ring of the inner spring is smaller than the diameter of the movable ring of the inner spring.

Further, the end face of the connecting ring of the inner spring is not higher than the end face of the connecting ring of the outer spring.

Further, the number of turns of the outer spring connecting ring is 3 to 4, and the gap between the rings is 0 to 0.5 mm.

Further, the number of turns of the inner spring connecting turns is 3-4 turns.

Further, the wire diameter of the outer spring is 4.0mm, the middle diameter of the spring is 23.5mm, the free angle is 158°, the stiffness is 2.5Nm/°, and the pressing angle is 103°.

Further, the wire diameter of the inner spring is 3.5mm, the diameter of the major axis of the elliptical area of the inner spring connecting ring is 16mm, the diameter of the minor axis is 14mm, the free angle is 127°, the steel degree is 6.6Nm/°, and the pressing angle is 93 °.

Further, when the outer spring is compressed between 158° and 127°, the inner spring is in a free state; when the outer spring is compressed less than 127°, the inner spring begins to be compressed; when the combined spring is compressed to 103°, the outer spring When the compression angle is reached, the combined spring is compressed to the maximum.

Further, the arc-shaped composite spring has a primary stiffness when only the outer spring works, and a secondary stiffness when the outer spring and the inner spring work at the same time. By adjusting the lengths of the outer spring and the inner spring, the primary stiffness and the secondary stiffness can be adjusted. The intersection point and stiffness value.

Further, the material of the arc-shaped combined spring is TD SiCr, VD SiCr, VD SiCrV.

The beneficial effects of the present invention are:

The invention reduces the stress in the connecting area of the outer spring and the inner spring, the inner spring no longer falls into the outer spring, significantly enhances product performance and quality stability, and avoids spring failure. Compared with the products in the prior art, the operation procedure is reduced and the cost is reduced.

The idea, specific structure and technical effects of the present invention will be further described below in conjunction with the accompanying drawings, so as to fully understand the purpose, features and effects of the present invention.

Description of drawings

Fig. 1 is a schematic structural view of an arc-shaped spring connected to an oval tail end according to a preferred embodiment of the present invention.

Fig. 2 is a schematic structural view of an inner and outer spring connection area of an arc spring with a goose-oval tail end connection according to a preferred embodiment of the present invention.

Fig. 3a is a cross-sectional structural schematic view of an inner spring connecting ring of an arc spring connected at an oval-shaped end according to a preferred embodiment of the present invention.

Fig. 3b is a schematic structural view of an inner spring connecting ring of an arc spring connected at a goose-shaped end according to a preferred embodiment of the present invention.

Fig. 4 is a test diagram of inner and outer spring torsional stiffness of an arc spring connected with a goose-shaped tail end according to a preferred embodiment of the present invention.

Fig. 5 is a schematic diagram of the torsional stiffness required to squeeze the inner spring into the outer spring in an arc spring with a goose-oval end connection according to a preferred embodiment of the present invention.

Explanation of reference signs

Outer spring 1

inner spring 2

Outer spring connecting ring 3

Inner spring connecting ring 4

Outer spring active ring 5

Inner spring active ring 6

Detailed ways

The invention relates to an arc-shaped composite spring for a double-mass flywheel, in particular to a composite spring whose tail end is connected in an oval shape. Preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings.

As shown in Figure 1, the present invention provides an arc-shaped combined spring for a dual-mass flywheel, including an outer spring 1 and an inner spring 2, wherein the outer spring 1 includes an outer spring connecting ring 3 and an outer spring movable ring 5, The outer spring connecting ring 3 is arranged on the end side of the outer spring 1, and the spring at the outer spring connecting ring 3 is wound into a circular dead ring, the inner spring 2 includes an inner spring connecting ring 4 and an inner spring movable ring 6, and the inner spring connecting ring 4 is set On the end side of the inner spring 2, the spring at the inner spring connecting ring 4 is wound into an elliptical dead ring, and the outer spring 1 and the inner spring 2 snap the elliptical major axis side of the inner spring connecting ring 4 into the outer spring connecting ring 3. The gap fits the connection.

As shown in Figures 2 and 3, the connection between the outer spring 1 and the inner spring 2 is similar to the connection between screws and nuts. The 3 connecting rings of the outer spring are wound into a circular dead circle of 3 to 4 turns, and a gap of 0 to 0.5mm is reserved. gap. The inner spring 2 is also wound with 3 to 4 rounds of elliptical dead circle at the end, and the side of the long axis of the ellipse just fits into the gap of the dead circle of the outer spring, and the diameter of the long axis of the ellipse is larger than the diameter of the active circle 6 of the inner spring, and the short axis of the ellipse The diameter is less than the diameter of the movable ring 6 of the inner spring.

As shown in FIG. 3 , the diameter of the minor axis of the ellipse of the inner spring connecting ring 4 is smaller than the diameter of the inner spring movable ring 6 , which is designed to facilitate the inner spring 2 to be packed into the outer spring 1 . During the installation process of the outer spring 1 and the inner spring 2, the diameter of the ellipse major axis side of the inner spring connecting ring 4 is squeezed, and the diameter of the minor axis of the inner spring connecting ring 4 increases. The outer spring 1 can be installed only when the diameter of the shaft and the minor axis is less than the diameter of the inner ring of the outer spring 1 . After installation, the length and minor axis diameter of the inner spring connecting ring 4 return to the original size when no external force is applied. At this time, the ellipse major axis side of the inner spring is snapped into the gap of the outer spring connecting ring 3 .

Preferably, the number of connected turns of the outer spring 1 is 3-4 turns, and the gap between turns is 0-0.5mm. The number of turns of the inner spring 2 connecting turns is 3 to 4 turns.

The end face of the inner spring connecting ring 4 is not higher than the end face of the outer spring connecting ring 3 . The profiles of the inner spring 2 and the outer spring 1 are arc-shaped, so after the springs are installed, the inner spring 2 cannot rotate in the outer spring 1, so the phenomenon that the inner spring 2 slides into the outer spring 1 cannot occur.

As shown in Figure 4, the arc spring combined by the outer spring 1 and the inner spring 2 has the first-level stiffness when only the outer spring 1 works, and the second-level stiffness when the outer spring 1 and the inner spring 2 work simultaneously; Therefore, by adjusting the length and diameter of the outer spring 1 and the inner spring 2, the primary stiffness and the junction point and stiffness value of the combined spring in this embodiment can be adjusted.

In this embodiment, the wire diameter of the outer spring 1 is 4.0mm, the middle diameter of the spring is 23.5mm, the free angle is 158°, the stiffness is 2.5Nm/°, and the pressing angle is 103°. The wire diameter of the inner spring 2 is 3.5mm, the major axis diameter of the ellipse area of the inner spring connecting ring 4 is 16mm, the minor axis diameter is 14mm, the free angle is 127°, the steel degree is 6.6Nm/°, and the pressing angle is 93° .

When the outer spring 1 is compressed between 158° and 127°, the inner spring 2 is in a free state; when the outer spring 1 is compressed less than 127°, the inner spring 2 starts to be compressed; when the combined spring is compressed to 103°, the outer spring 2 is in a free state. Spring 1 reaches the compression angle and the combined spring is compressed to the maximum.

In order to ensure dimensional stability, the spring needs to be thermally set, that is, the spring is heated first, and then pressed with a mold until the spring is in a compressed state. The assembly process of the inner and outer springs is realized during the spring heat setting process, and no additional process is added.

Figure 5 is a graph of the torque required to squeeze the inner spring into the outer spring. The push rod squeezes the end face of the spring at the connection end of the inner and outer springs, at this time the angle of the outer spring decreases and the torque increases. When the torque increases to 300Nm, the outer spring is in the state of compression, continue to increase the pressure, when the torque reaches 760Nm, press the inner spring into the outer spring, and the displayed torque drops rapidly at this time, that is, the inner spring and the outer spring slide into it. 300Nm is the maximum torque of the outer spring, and 760Nm is the force required to press the inner spring into the outer spring. 760Nm is greater than the maximum spring torque of 300Nm, so the inner spring will not be squeezed into the outer spring due to the operation of the spring itself.

Compared with the interference fit of capping, the oval-shaped end connection in this embodiment uses a mechanical structure to prevent the spring from moving. Under the same pull-out force standard, this design can effectively reduce the surface stress of the spring in the contact area with the cover.

The material of spring among the present invention is TD SiCr, VD SiCr, VD SiCrV.

The preferred specific embodiments of the present invention have been described in detail above. It should be understood that those skilled in the art can make many modifications and changes according to the concept of the present invention without creative effort. Therefore, all technical solutions that can be obtained by those skilled in the art based on the concept of the present invention through logical analysis, reasoning or limited experiments on the basis of the prior art shall be within the scope of protection defined by the claims.

Claims (10)

1. A kind of 1. arc cluster spring for double mass flywheel, it is characterised in that including outer spring, inner spring, wherein,

   The outer spring includes outer spring clamping ring and outer spring active ring, and the outer spring clamping ring is arranged on the outer spring Side, at the outer spring clamping ring spring wind into circular dead circle,

   The inner spring includes inner spring clamping ring and inner spring active ring, and the inner spring clamping ring is arranged on the inner spring Side, spring wind ovalisation is extremely enclosed at the inner spring clamping ring,

   The outer spring and inner spring are caught in the outer spring clamping ring by the transverse side of the inner spring clamping ring The mode in gap is connected.
2. 2. arc cluster spring according to claim 1, it is characterised in that the transverse of the inner spring clamping ring is straight Footpath is more than the diameter of the inner spring active ring, and the ellipse short shaft diameter of the inner spring clamping ring is less than inner spring activity The diameter of circle.
3. 3. arc cluster spring according to claim 1, it is characterised in that the end face of the inner spring clamping ring is not higher than The clamping ring end face of the outer spring.
4. 4. arc cluster spring according to claim 1, it is characterised in that the number of turns of the outer spring clamping ring is 3~4 Circle, ring gap is 0~0.5mm.
5. 5. arc cluster spring according to claim 1, it is characterised in that the number of turns of the inner spring clamping ring is 3~4 Circle.
6. 6. double mass flywheel shock-absorbing spring according to claim 1, it is characterised in that the spring filament diameter of the outer spring is 4.0mm, mean diameter of coil 23.5mm, free angle are 158 °, and rigidity is 2.5Nm/ °, press and angle is 103 °.
7. 7. double mass flywheel shock-absorbing spring according to claim 1, it is characterised in that the spring filament diameter of the inner spring is 3.5mm, inner spring clamping ring area elliptica major diameter are 16mm, and minor axis diameter 14mm, free angle is 127 °, and stiffness is 6.6Nm/ °, press and angle is 93 °.
8. 8. double mass flywheel shock-absorbing spring according to claim 1, it is characterised in that when the outer spring 158 °~ When being compressed between 127 °, the inner spring is in free state；When outer spring compression is less than 127 °, the inner spring is opened Begin to be pressurized；When the cluster spring is depressed into 103 °, the outer spring reaches pressure and angle, and the cluster spring is compressed into Maximum.
9. 9. arc cluster spring according to claim 1, it is characterised in that the arc cluster spring is in only outer spring There is one-level rigidity during work, there is two level rigidity when outer spring and inner spring work simultaneously, by adjusting the outer spring With the length of inner spring, one-level rigidity, the interface point and rigidity value of two level rigidity can adjust.
10. 10. double mass flywheel shock-absorbing spring according to claim 1, it is characterised in that the material of the arc cluster spring Expect for TD SiCr, VD SiCr, VD SiCrV.