阅读说明：本技术 驻车锁止器 (Parking lock ) 是由 本尼迪克特·施赖伯 托尔斯滕·凯勒 诺伯特·盖尔 汉尼斯·施莱尔 于 2019-03-21 设计创作，主要内容包括：提出一种用于平衡内燃机惯性力和/或惯性矩的不平衡轴,所述不平衡轴包含支撑轴(1)和固定在其外圆周上的不平衡质量(2)。所述不平衡质量在所述支撑轴上的固定应当借助一个包围所述支撑轴和所述不平衡质量的夹紧环(3)进行,所述夹紧环径向对着所述支撑轴夹紧所述不平衡质量。(An unbalanced shaft for balancing the inertial forces and/or moments of inertia of an internal combustion engine is proposed, comprising a support shaft (1) and an unbalanced mass (2) fixed to the outer circumference thereof. The unbalanced mass is fixed to the support shaft by means of a clamping ring (3) which surrounds the support shaft and the unbalanced mass and clamps the unbalanced mass radially against the support shaft.)

1. An unbalance shaft for balancing the inertia forces and/or moments of inertia of an internal combustion engine, comprising a support shaft (1) and an unbalance mass (2) fixed on its outer circumference, characterized in that the unbalance mass (2) is fixed on the support shaft (1) by means of a clamping ring (3) surrounding the support shaft (1) and the unbalance mass (2), which clamping ring clamps the unbalance mass (2) radially against the support shaft (1).

2. The imbalance shaft according to claim 1, characterized in that the securing of the imbalance mass (2) on the support shaft (1) is effected by means of two clamping rings (3) which surround the support shaft (1) and the end segments of the imbalance mass (2) in a form-fitting manner.

3. An unbalance shaft according to claim 1, characterized in that the unbalance mass (2) is mirror-symmetrical with respect to the unbalance plane spanned by the rotation axis (6) of the unbalance shaft and its mass center of gravity (7) and is arranged completely on the side of the rotation axis (6) with respect to the unbalance direction.

4. The imbalance shaft according to any one of the preceding claims, characterized in that the support shaft (1) is designed as an internal high-pressure profiled hollow profile in the fixing region of the imbalance mass (2).

5. Unbalance shaft according to claim 4, characterized in that the clamping ring(s) (3) and the unbalance mass (2) are fixed in a form-fitting manner both in the circumferential direction and in the axial direction of the unbalance shaft on a profiled hollow profile.

6. An unbalance shaft according to any of the preceding claims, characterized in that the unbalance shaft comprises a needle ring (11) surrounding the support shaft (1), wherein one or more of the clamping rings (3) each have an end face (13) serving as a needle axial contact face.

Technical Field

The invention relates to an unbalanced shaft for balancing the inertia forces and/or moments of inertia of an internal combustion engine. The unbalanced shaft includes a support shaft and an unbalanced mass fixed to an outer circumference thereof.

Background

A manufactured unbalanced shaft with an unbalanced mass connected thereto is known, for example, from DE 102012216418 a1, DE 102008060084 a1, DE 102009036794 a1, DE 102010035181 a1, DE 102012210171 a1, DE 102012217476 a1 and DE 102013200166 a 1.

Disclosure of Invention

The object of the invention is to provide an unbalanced shaft of the type mentioned at the outset which is as modular as possible.

The solution to the task is derived from the features of claim 1. The unbalance mass should therefore be fixed to the support shaft by means of a clamping ring which surrounds the support shaft and the unbalance mass and clamps the unbalance mass radially against the support shaft. The blocking of the unbalance shaft is achieved by fixing the unbalance mass by means of a clamping ring, and the size of the unbalance mass can be adjusted relatively easily in accordance with different unbalance quantities when the proportion of common parts in the unbalance shaft is different.

Advantageous refinements and embodiments of the invention can be gathered from the dependent claims. In particular, the support shaft should be designed as a hollow profile by internal high-pressure forming (IHU or hydroforming) in the region of the fastening of the unbalanced masses. The IHU shaping allows the clamping ring and the unbalanced mass to be fixed to the shaped hollow profile of the support shaft in a form-fitting manner both in the circumferential direction and in the axial direction of the unbalanced shaft.

Drawings

Further features of the invention can be derived from the following description and the drawing, in which an embodiment of the unbalanced shaft according to the invention is shown in a simplified manner.

FIG. 1a is a side view of an unbalanced shaft segment, including an unbalanced mass engaged on a support shaft;

FIG. 1b is a top view of the fragment shown in FIG. 1 a;

FIG. 1c is a longitudinal section A-A of the fragment shown in FIG. 1 d;

FIG. 1d is a cross-sectional view B-B of the fragment shown in FIG. 1 c;

FIG. 2a is a top view of the clamp ring shown in FIG. 1;

FIG. 2b is a longitudinal section of the clamping ring;

FIG. 3a is a side view of the unbalanced mass of FIG. 1;

FIG. 3b is a longitudinal section through the unbalanced mass;

FIG. 3c is a top view of the unbalanced mass;

FIG. 4a is a longitudinal cross-section of the shaft segment shown in FIG. 1 in the IHU mold prior to molding;

FIG. 4b is a cross-sectional view of the shaft segment shown in FIG. 4 a;

FIG. 5a is a view of the formed shaft segment shown in FIG. 4a in an IHU tool;

FIG. 5b is a view of the formed shaft segment shown in FIG. 4b in the IHU tool;

FIG. 6a illustrates the shaft segment of FIG. 5 a;

FIG. 6b the shaft segment shown in FIG. 5 b;

FIG. 7 is a longitudinal sectional view of a portion of an unbalanced shaft where a rolling bearing is supported.

Detailed Description

The unbalanced shafts shown in sections in fig. 1a to 1d serve to balance the free inertial forces of the internal combustion engine. The unbalanced shaft is formed from parts, namely a support shaft 1, one or more unbalanced masses 2 and clamping rings 3, wherein two clamping rings are required for each unbalanced mass 2. The unbalanced shaft is of modular design, wherein different shaft configurations can be generated by only changing the number and size of the unbalanced masses 2. The unbalanced shaft is in a preassembled state in which the supporting shaft 1, the unbalanced mass 2 and the clamping ring 3 have been plugged together, but the supporting shaft 1 has not yet been plastically molded.

As can be seen from the longitudinal and cross-sectional views of the imbalance shaft shown in fig. 1c or 1d, the support shaft 1 is designed at least in the axial fixing region of the imbalance weight 2 as a hollow profile which is formed in the IHU method according to fig. 4 and 5 described below. The unbalanced mass 2 is fixed to the support shaft 1 by means of two clamping rings 3, which surround the support shaft 1 and the end sections of the unbalanced mass 2 and, after shaping, clamp the unbalanced mass 2 radially against the outer circumference of the support shaft 1.

The inner contour of the clamping ring 3, which is illustrated as a part in fig. 2a and 2b, is substantially complementary to the outer contour enclosed by the clamping ring 3, which is formed by the outer cylindrical hollow profile of the support shaft 1 and the journal 4 projecting axially on the respective end section of the unbalanced mass 2, see fig. 3. The segment of the unbalanced mass 2 extending between the clamping rings 3 abuts against the hollow profile of the support shaft 1 via the semicylindrical recess 5.

As shown in fig. 1 and 3, the unbalanced mass 2 is mirror-symmetrical with respect to the plane of the imbalance spanned by the axis of rotation 6 of the imbalance shaft and its mass center of gravity 7. The imbalance mass 2 is arranged completely on the side of the axis of rotation 6 with respect to the imbalance direction-see fig. 3. This completely eccentric mass arrangement allows the shaft mass to be minimized at a given shaft unbalance.

Alternatively, the unbalanced masses can also be non-mirror-symmetrical, in order to ensure the required clearance with the adjacent rotating crankshaft, for example with circumferential grooves.

Fig. 4 and 5 show the plastic deformation of the support shaft 1 at the time of internal high-pressure molding. The IHU-die design allows a radial clearance between the undeformed hollow profile of the support shaft 1 outside the unbalanced mass 2 and the clamping ring 3 and the die halves 8 and 9, see fig. 4a and 4 b. When high pressure is subsequently applied, the plastically deformed hollow profile comes to bear completely against the mold halves 8, 9, wherein it encloses both the clamping ring 3 and the unbalanced mass 2 at the axial ends. The unbalanced mass 2 and the clamping ring 3 are thereby fixed to the hollow profile formed therewith both in the circumferential direction of the support shaft 1 and in the radial direction thereof in a force-and form-fit manner — see fig. 5a and 5b and fig. 6 which shows the formed unbalanced shaft as a segmented part.

The radial bearing of the unbalanced shaft may be a rolling bearing comprising a needle ring 10 and an outer ring 11 as shown in fig. 7. The inner guide for the needle rollers is formed by an inner ring 12 which is pressed onto the support shaft 1 between the two unbalanced masses 2, wherein the optionally finished end faces 13 of the clamping rings 3 facing one another are used as axial contact faces for the needle rollers.

List of reference numerals

1 supporting shaft

2 unbalanced mass

3 clamping ring

4 journal

5 groove

6 rotating shaft

7 center of mass

8 half mould

9 half mould

10-needle ring

11 outer ring

12 inner ring

13 end face