LONG-LIFE PENETRATING TOOTH - ADAPTER SYSTEM FOR EXCAVATORS

TECHNICAL FIELD

The invention is related to a long-life penetrating tooth-adapter system developed for excavators.

PRIOR ART

Excavators are construction machinery used for excavation and loading in excavation and pickling works in mining and construction sectors. They are manufactured in different types and shapes considering their needs and capacities. There are two types of excavators: crawler and wheel. Crawler or wheel excavators are selected according to the usage ground. The main element that performs excavation in excavators is the bucket of the machine and the most functional part of the main components of a bucket is bucket teeth.

The most prominent features sought in bucket teeth used in heavy working conditions, especially in mining sector are as follows:

• High Abrasion Resistance

• High Penetration and Breakout Capability

· High Strength and Toughness

High yield strength prevents the deformation of the teeth under load and high abrasion resistance affects the service life. The prolongation of the service life is also related to both the internal structure of the material and the design.

Teeth and Adapters vary in shape according to the ground to be used. For example, if the surface to be contacted by the tooth-adapter has a soft soil structure, it is desirable to have a large surface area. If the ground consists of hard rocks, it is desirable to have a narrow surface area.

The teeth wear more than adapters because they are in direct contact with the ground. Therefore, when a tooth changes 4-5 times, the adapters change 1 time. These teeth, which do the actual work on the machine, should be more durable than the adapters, working at higher performance and protecting the adapter by breaking and penetration the ground, supporting the breakout force of the machine, it does not lose its ability to penetrate in time, in other words it should be non-blunt (i.e. , the blunt; that the tooth loses it is sharpness and shortness by time) (penetration). Adapters mounted on the teeth have two most important tasks. The first is to protect the bucket from which it welded, and the second is to support the teeth.

BRIEF DESCRIPTION OF THE INVENTION

The invention consists of a long-life penetration tooth developed for excavator applications and an adapter developed in accordance with this tooth. The long-life penetration with wear-resistant material (WRM) has a higher wear life under medium and high impact conditions. It provides maximum plunge efficiency with self-sharpening feature as it works.

LIST OF FIGURES

Figure 1. Assembled View

Figure 2. Exploded View

Figure 3. Adapter Front View

Figure 4. Rear View of Tooth

Figure 5. Tooth Bottom Front View

Figure 6. Tooth Top Surface Front View

Figure 7. Tooth Interior View

Figure 8. Tooth Top View

Figure 9. Side View of Tooth

Figure 10. Tooth Bottom View

Figure 1 1. Section A-A Side View of Tooth

Figure 12. Adapter Side View The equivalents of the enumerations given in the figures are:

1. Adapter

1.1. Adapter Nose

1.2. Blade Gap

1.3. Stress Area

1.4. Welding Bent

1.5. Tooth Support Area

1.6. Adapter Nose Slopes

2. Tooth

2.1. Drop Shape

2.2. T Shape

2.3. Tooth Belt Area

3. Pin

4. Retainer

5. Blade

DETAILED DESCRIPTION OF THE INVENTION

The most common problem in these digger and protective parts is abrasive wear. Abrasive wear is caused by hard particles hitting or friction against the solid surface. Therefore, abrasion occurs when solid particles damage the surface and is generally observed as a decrease in material volume or weight. The hardness of the abrasive particles and the wear metal significantly affects the abrasion resistance. As the ratio of metal hardness to abrasive hardness increases, abrasive wear rate decreases. Abrasive wear is caused by the presence of hard foreign particles (metal oxide, metal particles, dust, etc.) between two friction surfaces. It is microscopic material removing of hard and sharp-edged particles and generally causes deep changes in the material.

The environments in which the machines are operated are generally environments that cause a high degree of abrasive wear. Since it is often not possible to change these environments, it is more appropriate to improve the wear resistance performance of the teeth and adapters exposed to wear. Two important methods can be applied for this. The first is to increase the hardness of the wear material, the second is to reduce friction by making appropriate design changes to the wear material. There is also a limit to increasing the hardness of the material, because fracture problems are seen in extremely hard materials. Optimum hardness limit and optimal design increase the abrasion resistance of the tooth, penetration-riper ability and service life.

Innovations have been made in our invention to reduce friction and wear. The sharpness of the tooth (2) is increased, it is easy to penetrate and more earthmoving is removed without forcing the engine of the machine. By means of the tooth support area (1.5) on the adapter (1 ), the adapter nose (1.1 ) and the slopes (1.6) on the adapter nose, the tooth (2) is supported and the adapter (1 ) is formed in the blade gap (1.2) in where stress area (1.3) distributes the loads on the tooth. Thus, pin (3) - retainer (4) fracture and tooth (2) fracture are prevented.

Thanks to the design changes made in the present invention, the penetration- ripper and break off feature of the tooth (2) is enhanced and designed so that it does not lose its two important properties even if it is wear over time. When the lower part of the tooth (2) is examined, a gap is observed in the form of raindrops (2.1 ). By means of this gap, the tooth (2) is provided to be both light and prevent the problem of blunting. Thanks to its features such as light weight, easy penetration into the ground thanks to sharp recesses and protrusions, and easier excavation material from the ground (ripper), it does not force the engine of the machine, thus saves energy and fuel.

Unbalanced loads on the teeth (2) cause the pins (3) and sometimes the teeth

(2) to break. Thanks to the recesses and protrusions on the tooth (2) and the adapter (1 ), these unbalanced loads are distributed homogeneously and the loads are reduced and the pin (3) is prevented from fracture due to the loads on the pins (3). Further, the tooth support area (1.5), the adapter nose (1.1), and the adapter nose slopes (1.6) on the adapter nose (1.1 ) provide a support on which it can abut against the tooth (2). Internal pressures (loads) are applied to the tooth belt area (2.3) by the adapter. Due to these loads, fractures occur in the teeth (2). In order to prevent these fractures, the tooth belt area (2.3) is designed by giving more thickness than the other areas of the tooth (2). The tooth belt area (2.3) should be designed with suitable thickness and width as it must be resistant to both internal pressures and abrasion. Thanks to the design changes made on the tooth (2), the loads on the tooth are distributed in a homogeneous manner and the tooth (2) is worn without losing its sharpness. Thanks to the adapter (1 ) fully assembled with the tooth (2), the wear of the adapter nose (1.1 ) is reduced and the bending or fracture of the retaining pin (3) is prevented. If this assembly is not fully achieved, there will be a mismatch problem in the tooth (2) and adapter (1 ). Thus, both the pin (3) fracture is seen and materials such as earth, stone, and between the tooth (2) and the adapter (1 ) enter and as a result, the wear of the adapter nose (1.1 ), the tooth (2) and the adapter (1 ) are broken.

The welding bent (1.4) formed by expanding on the adapter (1) makes it easier to weld and hold the adapter (1 ) to the bucket. By means of the stress area (1.3), which has a radius of 30 millimeters (shown in figure 12 is shown with“R”), formed at the end of the cutting edge (1.2), the loads on the adapter (1) are distributed, thereby the adapter (1 ) is prevented by breaking the blade (2) (stress area (1.3) is never welded). As shown in figure 12, the adapter (1 ) has a penetration angle (x) of 10 degrees between the lower surface on which the blade (5) is located and the center line of the adapter nose (1.1 ). By means of this angle, the tooth (2) is provided to penetrate into the ground with greater force.

In order to achieve the aforementioned advantages, the tooth (2) is formed by taking certain dimensions and angles into account. These angles and dimensions are given below.

The length is 170 millimeters, which indicates by letter a that width of the inlet of the tooth (2) shown in Figure 8. The end-to-end length (b) of the tooth (2) is 385 millimeters. The length C is the part that forms the end part of the tooth (2) and is 91 millimeters. The length D is the width of the end part of the tooth (2) and is 122 millimeters. The width of the front of the tooth (2) is indicated by the letter e and is 68 millimeters. The letter F is the upper spring angle of the end part of the tooth (2) and is 35 degrees. The letter G is the spring angle of the protrusion at the upper part of the trunk and is 33 degrees. The area indicated by the letter J is the tooth belt area (2.3) and is 19.3 millimeters.

The part h indicated in figure 9 is the height of the part where the tooth (2) part joins the adapter (1 ) and is 166 millimeters. The inner wall height indicated by the letter I is 145 millimeters. The center of the pin housing (3) is 50 millimeters from the beginning of the outer wall, indicated by the letter k. The tooth (2) has a spring from the bottom to the top and is 21 degrees and shown by the letter m. The spring dimension for the tip of the tooth (2) from bottom to top is 28 degrees and indicated by the letter n. The end height of the tooth (2) is indicated by the letter o is 13 mm and the distance between the first elevations indicated by the p letter is 45 millimeters which prevents the tooth (2) that wears becomes blunt.

In Figure 10, the maximum radius (RR) of the drop shape 2.1 in the lower part of the tooth (2) is 22 millimeters and its width (r) is 44 millimeters. In the middle part of the drop shape (2.1 ), the edge-to-edge spring size is indicated by the letter s and is 25 degrees. The end-to-end length of the drop shape (2.1 ) is indicated by the letter t and is 173.5 millimeters. The end of the drop shape (2.1 ) to the end of the tooth (2) is indicated by the letter u and is 66.4 millimeters. In the section A-A of Figure 1 1 , depth size of recess on the top of tooth is formed T shaped is 40 millimeter and it is indicated by v letter. The length indicated by the letter W is 28 millimeters and the spring angle given by the letter y is 12 degrees. The flat surface Z length is 125 millimeters.