CN220118491U

CN220118491U - Wear-resistant bushing

Info

Publication number: CN220118491U
Application number: CN202321509063.0U
Authority: CN
Inventors: 师雪燕; 张志峰
Original assignee: Miba Precision Components China Co ltd
Current assignee: Miba Precision Components China Co ltd
Priority date: 2023-06-14
Filing date: 2023-06-14
Publication date: 2023-12-01
Anticipated expiration: 2033-06-14

Abstract

The utility model belongs to the technical field of key parts of engines, and particularly relates to a wear-resistant bushing. The bushing is annular in whole, and the inner side of the bushing is provided with a bearing area and a non-bearing area which are connected end to form a ring; the surface of the bearing area is complete and continuous so as to uniformly bear pressure; an oil liquid distribution unit is respectively arranged at two ends of the bearing area and positioned in the non-bearing area; the oil distribution unit comprises a first oil distribution groove and a second oil distribution groove which are crossed with each other to form an X shape, and further comprises a first oil collecting groove connected to the tail end of the first oil distribution groove and a second oil collecting groove connected to the tail end of the second oil distribution groove; the first oil collecting groove and the second oil collecting groove are both connected to one end far away from the bearing area and are respectively arranged at two side edges of the non-bearing area. The wear-resistant bushing provided by the utility model has the advantages that the supply rate of lubricating oil is obviously improved when an engine runs, the establishment of hydraulic lubrication between the piston connecting pin and the bushing is promoted, the direct contact between the piston connecting pin and the bushing is reduced, and the possibility of failure of the bushing is obviously reduced.

Description

Wear-resistant bushing

Technical Field

The utility model belongs to the technical field of key parts of engines, and particularly relates to a wear-resistant bushing.

Background

The engine is energy conversion equipment for converting chemical energy into mechanical energy, is widely applied to the fields of automobiles, ships, airplanes, electric power, engineering machinery and the like, and drives a piston to reciprocate by combusting fuel such as gasoline, diesel oil and the like to drive a crankshaft to rotate through a connecting rod so as to apply work to the outside.

The engine work to the outside mainly involves the working cycle of suction-compression-ignition-expansion-exhaust, during which the connecting rod oscillates relative to the piston, causing wear between the bushing at the end of the connecting rod and the connecting pin of the piston. In particular, during the ignition-expansion phase, the severity of the relative movement between the bushing and the piston connecting pin increases considerably, the compression force between the two also increases considerably, a large amount of heat is generated, and a greater degree of wear is also caused.

In order to ensure safe operation of the engine, a sufficient flow of lubricating oil must be supplied between the bushing and the piston connecting pin to reduce friction and remove heat, which would otherwise cause severe wear of the bushing and even cause seizure failure of the bushing material under severe conditions, resulting in shutdown of the engine. Therefore, optimizing the bushing structure improves the oil supply as a key factor in ensuring safe operation of the engine.

Disclosure of Invention

Aiming at the defects existing in the prior art, the utility model provides a wear-resistant bushing, which aims to improve the supply of lubricating oil on the bushing, accelerate the transmission of heat generated by friction of the bushing, lighten the abrasion of the bushing, prolong the service life of the bushing and prevent the occurrence of failure faults of the bushing.

The wear-resistant bushing provided by the utility model is annular in whole, and the inner side of the wear-resistant bushing is provided with a bearing area and a non-bearing area which are connected end to form a ring; the surface of the bearing area is complete and continuous so as to uniformly bear pressure; an oil liquid distribution unit is respectively arranged at two ends of the bearing area and positioned in the non-bearing area; the oil distribution unit comprises a first oil distribution groove and a second oil distribution groove which are crossed with each other to form an X shape, and further comprises a first oil collecting groove connected to the tail end of the first oil distribution groove and a second oil collecting groove connected to the tail end of the second oil distribution groove; the first oil collecting groove and the second oil collecting groove are both connected to one end far away from the bearing area and are respectively arranged at two side edges of the non-bearing area.

Further, in the wear-resistant bushing, compared with the surface of the non-bearing area, the groove depths of the first oil distribution groove, the second oil distribution groove, the first oil collection groove and the second oil collection groove are 0.65 mm-1.25 mm; the groove widths of the first oil distribution groove and the second oil distribution groove are 0.85 mm-2.20 mm; the groove width of the first oil collecting groove and the second oil collecting groove is 0.50 mm-1.80 mm.

Further, in the wear-resistant bushing, a central line on the inner wall of the bushing along the circumferential direction is marked as L, an included angle between the first oil distribution groove and the central line L is marked as < A, and an included angle between the second oil distribution groove and the central line L is marked as < B;55.0 DEG < A <68.0 DEG and 55.0 DEG < B <68.0 deg.

Further, in the wear-resistant bushing, the projection length of the X-shaped pattern formed by the first oil distribution groove and the second oil distribution groove crossing each other on the central line L is D1, and the projection lengths of the first oil collection groove and the second oil collection groove on the central line L are D2; d1/d2=0.95 to 1.05.

Further, in the wear-resistant bushing described above, the narrow ends of the middle section of the non-bearing region are widened to be consistent with the bearing region, and the first oil sump and the second oil sump are provided at each end of the narrower middle section.

Further, in the wear-resistant bushing, at least one oil inlet hole penetrating inside and outside is further formed in the non-bearing area, and the diameter of the oil inlet hole is 2.0 mm-3.5 mm.

Further, in the wear-resistant bushing, two oil inlet holes are formed, and each oil distribution unit corresponds to one oil inlet hole; each oil inlet hole is positioned on the central line L and is also positioned on a connecting line of one end of the first oil collecting groove and one end of the second oil collecting groove, which are far away from the bearing area.

The beneficial effects are that: compared with the prior art, the wear-resistant bushing provided by the utility model has the advantages that the oil distribution units used for splashing oil on two sides of the bushing are added on the basis of a traditional oil hole oil inlet mode, the space structure form and the size of the oil distribution units are subjected to deep optimization design, the supply rate of lubricating oil during engine operation is obviously improved, the establishment of hydraulic lubrication between a piston connecting pin and the bushing is promoted, the direct contact between the piston connecting pin and the bushing is reduced, the heat generated by friction is reduced, the migration of the heat is accelerated, and the possibility of failure of the bushing is obviously reduced.

Drawings

Fig. 1 is a schematic structural view of a wear-resistant bushing.

FIG. 2 is an expanded schematic view of the inner wall of the wear bushing.

Fig. 3 is a partial enlarged view of fig. 2.

In the figure, 1, a bearing area; 2. a non-load bearing region; 21. a first oil distribution groove; 22. a second oil distribution groove; 23. a first oil sump; 24. a second oil sump; 25. and an oil inlet hole.

Detailed Description

A wear-resistant bushing as shown in fig. 1 and 2 is generally annular, having a load-bearing zone 1 and a non-load-bearing zone 2 on the inside, joined end to form a ring. The bearing zone 1 is the zone mainly responsible for compression from the piston connecting pin during engine operation, so in this embodiment the bearing zone 1 is the widest zone, which distributes the pressure to reduce wear, whereas the narrower ends of the middle section of the non-bearing zone 2 are widened to coincide with the bearing zone 1. Furthermore, the surface of the bearing area 1 is a complete continuous smooth surface, so that local concentrated bearing is avoided, and friction between the bearing area and the piston connecting pin is reduced.

As shown in fig. 2, an oil distribution unit is respectively arranged at two ends of the bearing area 1 and positioned in the non-bearing area 2; the oil distribution unit includes a first oil distribution groove 21 and a second oil distribution groove 22 crossing each other to form an X-shape, and further includes a first oil sump 23 connected to an end of the first oil distribution groove 21 and a second oil sump 24 connected to an end of the second oil distribution groove 22; the first oil collecting groove 23 and the second oil collecting groove 24 are both connected at one end far away from the bearing area 1 and are respectively arranged at two side edge positions of the non-bearing area 2. Wherein the first oil sump 23 and the second oil sump 24 are provided at the edge of the bush and have a long length, and function to collect oil splashed in the casing when the engine is operated and guide the oil to the first oil distribution groove 21 and the second oil distribution groove 22; the first oil distribution groove 21 and the second oil distribution groove 22 have the functions of uniformly and well distributing oil in the width direction of the bushing, and the inner wall of the bushing and the surface of the piston connecting pin rotatably arranged in the bushing form circumferential friction movement to promote the oil to form an oil film in a gap between the piston connecting pin and the bushing, so that the oil film has obvious light abrasion.

As described above, the oil distribution units are arranged at both ends of the bearing area 1, so that oil can be better uniformly distributed. Specifically, since the wrist pin is in a reciprocating oscillating motion relative to the bushing during engine operation, there is a relative motion of the wrist pin surface relative to the bearing zone 1 in two directions, as indicated by M1 and M2 in fig. 2. When the surface of the piston connecting pin moves in the direction M1 relative to the bearing zone 1, the oil distributing unit on the right side of the figure assumes a main oil distributing function, and similarly, when the surface of the piston connecting pin moves in the direction M2 relative to the bearing zone 1, the oil distributing unit on the left side of the figure assumes a main oil distributing function, so that no matter in which stage the engine is running, sufficient oil is always supplied to the bearing zone 1. If there is only a single oil distribution unit, then there must be relatively little oil supply at some stage, which is more likely to result in increased temperature and increased wear.

The first oil distribution grooves 21, the second oil distribution grooves 22, the first oil collection grooves 23 and the second oil collection grooves 24 have a groove depth of 0.65mm to 1.25mm, more preferably 0.75mm to 1.05mm, compared with the surface of the non-bearing region 2; the groove widths of the first oil distribution groove 21 and the second oil distribution groove 22 are 0.85mm to 2.20mm, and more preferably 0.95mm to 1.35mm; the groove widths of the first oil collecting groove 23 and the second oil collecting groove 24 are 0.50mm to 1.80mm, and more preferably 0.65mm to 1.25mm. The distribution and migration of oil can be accelerated by reasonably setting the groove depth and the groove width. Specifically, if the scale is too large, the capillary action of the oil in the oil distribution groove and the oil collection groove is weakened, resulting in a decrease in migration speed; if the size is too small, metal scraps generated in the running process of the engine gradually accumulate in the oil distribution groove and the oil collecting groove to cause oil groove blockage, and the distribution and migration of oil can be influenced.

As shown in fig. 2, the central line on the inner wall of the bushing along the circumferential direction is denoted as L, the included angle between the first oil distribution groove 21 and the central line L is denoted as +.a, and the included angle between the second oil distribution groove 22 and the central line L is denoted as +.b; 55.0 DEG < A <68.0 DEG and 55.0 DEG < B <68.0 deg. The arrangement of the angle A and the angle B has an important effect on the uniform distribution of the oil, when the surface of the piston connecting pin moves along the direction M2 relative to the bearing area 1, the oil distribution unit at the left side in the figure bears a main oil distribution function, taking the angle arrangement of the first oil distribution groove 21 as an example, the viscous force F of the oil on the surface of the piston connecting pin is multiplied by the cosine value cosA of the angle A to obtain the component force F cosA for driving the oil to flow along the first oil distribution groove 21, so that when the angle A is overlarge, the F cosA is obviously reduced, and the smooth migration of the oil is unfavorable; although the F & cosA value increases along with the decrease of the angle A, the path of the first oil distribution groove 21 increases obviously, which is unfavorable for smooth migration of oil, and the included angle occupied by the whole oil distribution unit in the circumferential direction increases along with the decrease of the angle A, thereby extruding the space of the bearing area 1. In consideration of the above aspects, the setting of the included angle within the range of 55.0-68.0 degrees is the best choice, so that the efficient and rapid migration of oil can be promoted, and the oil distribution unit is ensured to have a relatively compact structure.

As shown in fig. 3, as a more preferable scheme, the length of the projection of the X-shaped pattern formed by the first oil distribution groove 21 and the second oil distribution groove 22 crossing each other on the central line L is D1, and the length of the projection of the first oil collection groove 23 and the second oil collection groove 24 on the central line L is D2; the preferred value of D1/D2 is 0.70-1.65, most preferably 0.95-1.05. In the oil distribution unit, the reasonable ratio of D1/D2 depends on the balance between the oil collecting speed and the migration speed, when the ratio of D1/D2 is too large, the oil collecting speed is smaller than the oil migration speed, and the oil collecting speed becomes a control factor for limiting the oil supply; when the ratio of D1/D2 is too small, the oil collecting speed is larger than the oil migration speed, and the oil migration speed becomes a control factor for limiting the oil supply; when the D1/D2 is in a reasonable ratio range, the oil collecting speed is close to the oil migration speed, and the oil distribution groove and the oil collection groove both exert higher efficiency, and the D1/D2 is preferably 0.70-1.65 and optimally 0.95-1.05 based on the working state of a conventional engine.

The preferred locations of the first and second oil sumps 23 and 24 are described below: as described above, the narrow ends of the middle section of the non-carrying area 2 are widened to coincide with the carrying area 1, and at each end of the narrower middle section, the first oil sump 23 and the second oil sump 24 are provided.

As shown in fig. 1 to 3, in the non-bearing area 2, an oil inlet 25 penetrating inside and outside may be further added, and the diameter of the oil inlet 25 is 2.0 mm-3.5 mm; two oil inlets 25 are arranged, and each oil distribution unit corresponds to one oil inlet 25; each oil inlet hole 25 is located on the center line L and is also located on the line connecting the ends of the first oil sump 23 and the second oil sump 24 remote from the carrying area 1. After the oil inlet holes 25 are additionally arranged, oil entering through the oil inlet holes 25 spreads from the central line L to two sides, and the oil from the oil distribution unit migrates from two sides to the middle, so that complementation is formed between the oil and the oil, and the distribution of the oil is promoted, thereby achieving the effects of reducing temperature and reducing friction.

The above embodiments are illustrative for the purpose of illustrating the technical concept and features of the present utility model so that those skilled in the art can understand the content of the present utility model and implement it accordingly, and thus do not limit the scope of the present utility model. All equivalent changes or modifications made in accordance with the spirit of the present utility model should be construed to be included in the scope of the present utility model.

Claims

1. A wear resistant bushing, characterized by: the lining is annular, the inner side is provided with a bearing area (1) and a non-bearing area (2), and the bearing area and the non-bearing area are connected end to form a ring; the surface of the bearing area (1) is complete and continuous so as to uniformly bear pressure; an oil liquid distribution unit is respectively arranged at two ends of the bearing area (1) and positioned in the non-bearing area (2); the oil distribution unit comprises a first oil distribution groove (21) and a second oil distribution groove (22) which are crossed with each other to form an X shape, and further comprises a first oil collection groove (23) connected to the tail end of the first oil distribution groove (21) and a second oil collection groove (24) connected to the tail end of the second oil distribution groove (22); the first oil collecting groove (23) and the second oil collecting groove (24) are connected to one end far away from the bearing area (1) and are respectively arranged at two side edge positions of the non-bearing area (2).

2. The wear resistant bushing of claim 1 wherein: compared with the surface of the non-bearing area (2), the groove depths of the first oil distribution groove (21), the second oil distribution groove (22), the first oil collection groove (23) and the second oil collection groove (24) are 0.65 mm-1.25 mm; the groove widths of the first oil distribution groove (21) and the second oil distribution groove (22) are 0.85 mm-2.20 mm; the groove widths of the first oil collecting groove (23) and the second oil collecting groove (24) are 0.50 mm-1.80 mm.

3. The wear resistant bushing of claim 1 wherein: the central line of the inner wall of the bushing along the circumferential direction is marked as L, the included angle between the first oil distribution groove (21) and the central line L is marked as < A >, and the included angle between the second oil distribution groove (22) and the central line L is marked as < B;55.0 DEG < A <68.0 DEG and 55.0 DEG < B <68.0 deg.

4. A wear resistant bushing in accordance with claim 3 wherein: the length of projection of the X-shaped pattern formed by the first oil distribution groove (21) and the second oil distribution groove (22) crossing each other on the central line L is D1, and the length of projection of the first oil collection groove (23) and the second oil collection groove (24) on the central line L is D2; d1/d2=0.95 to 1.05.

5. A wear resistant bushing in accordance with claim 3 wherein: the narrow two ends of the middle section of the non-bearing area (2) are gradually widened to be consistent with the bearing area (1), and the first oil collecting groove (23) and the second oil collecting groove (24) are respectively arranged at each end of the narrower middle section.

6. A wear resistant bushing in accordance with claim 3 wherein: and at least one oil inlet hole (25) which is internally and externally communicated is further arranged in the non-bearing area (2), and the diameter of the oil inlet hole (25) is 2.0 mm-3.5 mm.

7. The wear resistant bushing of claim 6 wherein: two oil inlet holes (25) are formed, and each oil distribution unit corresponds to one oil inlet hole (25); each oil inlet hole (25) is positioned on the central line L and is also positioned on a connecting line of one end of the first oil collecting groove (23) and the second oil collecting groove (24) far away from the bearing area (1).