CN213017249U - Crankshaft supporting structure of high-speed press - Google Patents

Abstract

A crankshaft support structure for a high-speed press has a crankshaft supported at least at both ends thereof by bearings on a body of the high-speed press. And at the positioning supporting end and the telescopic supporting end, the bearings are respectively formed by a main rolling bearing and a main sliding bearing in parallel, wherein the inner rings of the two main rolling bearings are in interference fit with the crankshaft, and the outer rings of the two main rolling bearings are in clearance fit with the body of the high-speed press. In the no-load running state, the two main rolling bearings simultaneously support the crankshaft, and the two main sliding bearings are in a suspended state. In a stamping state, the two main rolling bearings and the two main sliding bearings support the crankshaft together, wherein the two main sliding bearings support the impact load on the crankshaft in a dynamic pressure oil film mode. Adopt the utility model discloses, can effectively solve the unstable problem of high-speed press bottom dead center precision, improve the reliability.

Description

Crankshaft supporting structure of high-speed press

Technical Field

The utility model relates to a press technical field, in particular to high-speed press crankshaft support structure.

Background

The high-speed press is an automatic press capable of realizing high-speed continuous stamping and is widely applied to stamping processing of punching, blanking, stretching, calendering and the like of metal plates. With the development of the technology, people have higher and higher requirements on the efficiency of the high-speed press, however, the higher the running speed of the high-speed press is, the more difficult the reliability is to be improved. Therefore, on the premise of high efficiency, how to improve the reliability of the high-speed press is a problem which is solved by scientific research institutions, and the main factor causing the problem is that the crankshaft support of the high-speed press generates heat to cause the precision of a bottom dead center to change.

In the prior art, the crankshaft support of the high-speed press only adopts a sliding bearing or a rolling bearing singly, and the arrangement has certain disadvantages. For the high-speed press crankshaft only adopting the sliding bearing, the sliding bearing is in surface contact, the rigidity is high, and the stability is high, but the sliding bearing is heated seriously by the stress when the crankshaft runs at a high speed, so that the crankshaft can be burnt or fall off by fatigue, the abrasion of the crankshaft is caused, and the precision of the bottom dead center of the high-speed press is changed finally. For a high-speed press crankshaft only adopting a rolling bearing, although the friction coefficient formed by point contact or line contact is small, the rigidity is weak, the impact resistance and the service life are low, so that the lower dead center precision is easy to be unstable and the reliability is poor when the crankshaft is subjected to heavy load.

In view of the above, the present invention is to provide a crankshaft supporting structure of a high speed press, which can effectively solve the problem of poor reliability caused by the change of the bottom dead center precision due to the heat generated by the crankshaft of the high speed press.

Disclosure of Invention

The utility model provides a high-speed press bent axle supporting structure, its purpose is to solve the poor problem of reliability that the high-speed press bent axle generates heat and leads to.

In order to achieve the above purpose, the utility model adopts the technical scheme that: a high-speed press crankshaft support structure, has a bent axle, this bent axle adopts bearing support on the high-speed press fuselage at least at its both ends, wherein, one end is defined as the location support end, and the other end is flexible support end, its innovation lies in: at the positioning and supporting end, the bearing is formed by a first main rolling bearing and a first main sliding bearing in parallel, wherein the inner ring of the first main rolling bearing is in interference fit with the crankshaft, and the outer ring of the first main rolling bearing is in clearance fit with the body of the high-speed press; and at the telescopic supporting end, the bearing is formed by a second main rolling bearing and a second main sliding bearing in parallel, wherein the inner ring of the second main rolling bearing is in interference fit with the crankshaft, and the outer ring of the second main rolling bearing is in clearance fit with the body of the high-speed press. In the no-load running state, the first main rolling bearing and the second main rolling bearing simultaneously support the crankshaft, and the first main sliding bearing and the second main sliding bearing are in a suspended state. In a stamping state, the first main rolling bearing, the first main sliding bearing, the second main rolling bearing and the second main sliding bearing support the crankshaft together, wherein the first main sliding bearing and the second main sliding bearing support the impact load applied to the crankshaft in a dynamic pressure oil film mode.

The relevant content in the above technical solution is explained as follows:

1. in a no-load running state, the main sliding bearing is in clearance fit with the crankshaft; the inner ring of the main rolling bearing is in interference fit with the crankshaft, and the outer ring of the main rolling bearing is in clearance fit with the body of the high-speed press; in a stamping state, the crankshaft is deformed, a sufficient relative movement speed exists between the journal and the bearing bush, the lubricant has proper viscosity, and a gap between two surfaces of the journal and the bearing bush is converged, so that a dynamic pressure oil film is formed between the main sliding bearing and the crankshaft. Through the structural design, the bearing parts are the sliding bearing and the rolling bearing during crankshaft blanking, and the bearing parts are the rolling bearing during no-load operation.

2. In this aspect, preferably, the first main rolling bearing is a cylindrical roller bearing; the second main rolling bearing is a double-row self-aligning roller bearing. The structure is provided with a rolling bearing with one end capable of adjusting the axial length, so as to relieve the negative influence generated by high temperature, deformation or displacement. The first main sliding bearing and the second main sliding bearing are dynamic pressure sliding bearings, and can form a dynamic pressure oil film.

3. In this aspect, it is preferable that the first main rolling bearing be located outside the first main sliding bearing in the crankshaft axial direction; the second main rolling bearing is located outside the second main sliding bearing in the crankshaft axial direction. This configuration is useful for optimizing the bearing distribution of the two types of bearings in the pressed state.

4. In this aspect, preferably, in the no-load operation state, the clearance between the first main sliding bearing and the crankshaft and the clearance between the second main sliding bearing and the crankshaft are both first clearances, and the first clearances range from 0.04 mm to 0.15 mm. This configuration is useful for optimizing the bearing distribution of the two types of bearings in the pressed state.

5. In this aspect, preferably, interference ranges of the inner ring of the first main rolling bearing and the inner ring of the second main rolling bearing in interference fit with the crankshaft are 0.03 mm to 0.13 mm, respectively. This configuration is also beneficial for optimizing the bearing distribution of the two types of bearings in the stamped condition.

6. In the scheme, the crankshaft is also provided with an auxiliary sliding bearing for auxiliary support; the secondary sliding bearing is a dynamic pressure sliding bearing. The crankshaft is also provided with an auxiliary rolling bearing which is arranged in parallel with the auxiliary sliding bearing, and the auxiliary rolling bearing is arranged close to the corresponding auxiliary sliding bearing; under the no-load running state, the inner ring of the auxiliary rolling bearing is in interference fit with the crankshaft, and the outer ring of the auxiliary rolling bearing is in clearance fit with the body of the high-speed press. The auxiliary support is used in a stamping state, the precision change of the bottom dead center caused by the heating of the crankshaft of the high-speed press is further relieved, and the reliability is improved.

7. In this embodiment, the high-speed press has at least one connecting rod, which is mounted on the crankshaft using a connecting rod slide bearing.

8. In this embodiment, it is preferable that the high-speed press body includes two main bearing seats, one of which is located at the positioning support end for positioning the first main rolling bearing and the first main sliding bearing, and the other of which is located at the telescopic support end for positioning the second main rolling bearing and the second main sliding bearing.

9. In the scheme, the first main sliding bearing and the second main sliding bearing are symmetrically arranged at two axial ends of the crankshaft, so that the balance is improved, and the design, the processing and the control are convenient.

The utility model discloses a design principle and beneficial effect are:

to the high-speed press, the utility model provides a antifriction bearing and slide bearing combined together's bearing structure: the main sliding bearing is in clearance fit with the crankshaft; the inner ring of the main rolling bearing is in interference fit with the crankshaft, while the outer ring is in clearance fit with the body of the high-speed press and is combined with a positioning bearing end and a telescopic bearing end. The bearing structure is used for realizing that the bearing parts are a sliding bearing and a rolling bearing in a stamping state, and the bearing parts are the rolling bearings in a no-load running state. The structure has the advantages of small friction coefficient of the rolling bearing and high rigidity of the sliding bearing, and avoids the defects of small rigidity of the rolling bearing and short service life of the sliding bearing, so that the problem of unstable precision of a bottom dead center of a high-speed press caused by heating of the sliding bearing in single use is solved, and the stress defect caused by single use of the rolling bearing is overcome. Meanwhile, the axial length of the rolling bearing is adjustable.

Therefore, the utility model discloses not only can guarantee blanking precision (especially heavy-duty blanking precision), be favorable to ensureing that high speed press bottom dead center precision is stable, still helps improving the reliability and the life of high speed press and mould to a certain extent.

Drawings

FIG. 1 is a schematic view of a crankshaft supporting structure of a high-speed press according to the present invention;

fig. 2 is a partially enlarged view of fig. 1.

In the above drawings: 1. a crankshaft; 2. a high-speed press body; 3. a first main rolling bearing; 4. a first main plain bearing; 5. a second main rolling bearing; 6. a second main plain bearing; 7. a secondary sliding bearing; 8. a connecting rod; 9. a connecting rod sliding bearing; 10. a main bearing seat.

Detailed Description

The invention will be further described with reference to the following drawings and examples:

example (b): crankshaft supporting structure of high-speed press

Referring to fig. 1, a crankshaft support structure of a high-speed press has a crankshaft 1, and the crankshaft 1 is supported at least at both ends thereof on a high-speed press body 2 by bearings, wherein one end is defined as a positioning support end and the other end is a telescopic support end.

Referring to fig. 2, at the positioning and supporting end, the bearing is formed by a first main rolling bearing 3 and a first main sliding bearing 4 in parallel, wherein the first main sliding bearing 4 is a dynamic pressure sliding bearing, an inner ring of the first main rolling bearing 3 is in interference fit with the crankshaft 1, and an outer ring of the first main rolling bearing is in clearance fit with the high-speed press body 2.

At the telescopic supporting end, the bearing is formed by a second main rolling bearing 5 and a second main sliding bearing 6 in parallel, wherein the second main sliding bearing 6 is a dynamic pressure sliding bearing, the inner ring of the second main rolling bearing 5 is in interference fit with the crankshaft 1, and the outer ring of the second main rolling bearing is in clearance fit with the high-speed press body 2.

In the idle state, the first main rolling bearing 3 and the second main rolling bearing 5 simultaneously support the crankshaft 1, while the first main sliding bearing 4 and the second main sliding bearing 6 are in the suspended state.

In the pressed state, the first main rolling bearing 3, the first main sliding bearing 4, the second main rolling bearing 5 and the second main sliding bearing 6 jointly support the crankshaft 1, wherein the first main sliding bearing 4 and the second main sliding bearing 6 form a support for the impact load to which the crankshaft 1 is subjected in the form of a hydrodynamic oil film.

In the present embodiment, as shown in fig. 1, the first main rolling bearing 3 is a cylindrical roller bearing; the second main rolling bearing 5 is a double-row self-aligning roller bearing. The first main rolling bearing 3 is located outside the first main sliding bearing 4 in the axial direction of the crankshaft 1; the second main rolling bearing 5 is located outside a second main sliding bearing 6 in the axial direction of the crankshaft 1.

In the present embodiment, as shown in fig. 1, in the no-load operation state, the clearance between the first main sliding bearing 4 and the crankshaft 1 and the clearance between the second main sliding bearing 6 and the crankshaft 1 are both first clearances, and the first clearances range from 0.04 mm to 0.15 mm. The interference range of the interference fit between the inner ring of the first main rolling bearing 3 and the inner ring of the second main rolling bearing 5 and the crankshaft 1 is 0.03 mm to 0.13 mm.

In the present embodiment, as shown in fig. 1, the crankshaft 1 is further provided with a secondary sliding bearing 7 for auxiliary support; the sub-sliding bearing 7 is a dynamic pressure sliding bearing. The high-speed press has at least one connecting rod 8, which connecting rod 8 is mounted on the crankshaft 1 by means of a connecting rod slide bearing 9.

In the present embodiment, as shown in fig. 1 and fig. 2, the high-speed press body 2 includes two main bearing seats 10 on the positioning support end for positioning the first main rolling bearing 3 and the first main sliding bearing 4, and on the telescopic support end for positioning the second main rolling bearing 5 and the second main sliding bearing 6.

In the present embodiment, as shown in fig. 1, the first main sliding bearing 4 and the second main sliding bearing 6 are symmetrically disposed at both axial ends of the crankshaft 1.

Other embodiments and structural changes of the present invention are described below as follows:

1. in the above embodiment, one of the two main rolling bearings is a cylindrical roller bearing, and the other is a double-row self-aligning roller bearing. However, the present invention is not limited thereto. In the stamping process, all can be applicable to the utility model discloses a can realize the antifriction bearing combination of one end location, the flexible one end, all fall into the utility model discloses in the protection range, this is that technical personnel in the field understand easily and accept.

2. In the above embodiment, the first main rolling bearing is located outside the first main sliding bearing in the crankshaft axial direction; the second main rolling bearing is located outside the second main sliding bearing in the crankshaft axial direction. However, the present invention is not limited thereto. For example, the two main rolling bearings may be located axially inside the two main sliding bearings, or the two main rolling bearings may be located axially on the same side of the two main sliding bearings. For these solutions only, the advantages of the pressure distribution of the two types of bearings are not optimized in the stamping state, which results in poor technical performance. As would be readily understood and accepted by those skilled in the art.

3. In the above embodiments, the crankshaft is provided with the auxiliary sliding bearing for auxiliary support, but the present invention is not limited thereto. The crankshaft can be further provided with an auxiliary rolling bearing arranged in parallel with the auxiliary sliding bearing, and the auxiliary rolling bearing is arranged close to the corresponding auxiliary sliding bearing; under the no-load running state, the inner ring of the auxiliary rolling bearing is in interference fit with the crankshaft, and the outer ring of the auxiliary rolling bearing is in clearance fit with the body of the high-speed press. As would be readily understood and accepted by those skilled in the art.

The above embodiments are only for illustrating the technical concept and features of the present invention, and the purpose of the embodiments is to enable people skilled in the art to understand the contents of the present invention and to implement the present invention, which cannot limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered by the protection scope of the present invention.

Claims (10)

1. A high-speed press crankshaft support structure having a crankshaft (1), the crankshaft (1) being supported at least at its two ends on a high-speed press body (2) using bearings, wherein one end is defined as a positioning support end and the other end is a telescopic support end, characterized in that:

at the positioning and supporting end, the bearing is formed by a first main rolling bearing (3) and a first main sliding bearing (4) in parallel, wherein the inner ring of the first main rolling bearing (3) is in interference fit with the crankshaft (1), and the outer ring of the first main rolling bearing is in clearance fit with the high-speed press body (2);

at the telescopic supporting end, the bearing is formed by a second main rolling bearing (5) and a second main sliding bearing (6) in parallel, wherein the inner ring of the second main rolling bearing (5) is in interference fit with the crankshaft (1), and the outer ring of the second main rolling bearing is in clearance fit with the high-speed press body (2);

in the no-load running state, the first main rolling bearing (3) and the second main rolling bearing (5) simultaneously support the crankshaft (1), and the first main sliding bearing (4) and the second main sliding bearing (6) are in a suspended state;

in the stamping state, the first main rolling bearing (3), the first main sliding bearing (4), the second main rolling bearing (5) and the second main sliding bearing (6) jointly support the crankshaft (1), wherein the first main sliding bearing (4) and the second main sliding bearing (6) form a support for impact load on the crankshaft (1) in the form of a dynamic pressure oil film.

2. The high speed press crankshaft support structure of claim 1, wherein: the first main rolling bearing (3) is a cylindrical roller bearing; the second main rolling bearing (5) is a double-row self-aligning roller bearing; the first main sliding bearing (4) and the second main sliding bearing (6) are dynamic pressure sliding bearings.

3. The high speed press crankshaft support structure of claim 1, wherein: the first main rolling bearing (3) is located outside the first main sliding bearing (4) in the axial direction of the crankshaft (1); the second main rolling bearing (5) is located outside the second main sliding bearing (6) in the axial direction of the crankshaft (1).

4. The high speed press crankshaft support structure of claim 1, wherein: in the no-load operation state, a clearance between the first main sliding bearing (4) and the crankshaft (1) and a clearance between the second main sliding bearing (6) and the crankshaft (1) are both first clearances, and the first clearances range from 0.04 mm to 0.15 mm.

5. The high speed press crankshaft support structure of claim 1, wherein: the interference range of the inner ring of the first main rolling bearing (3) and the interference range of the inner ring of the second main rolling bearing (5) in interference fit with the crankshaft (1) are 0.03 mm to 0.13 mm respectively.

6. The high speed press crankshaft support structure of claim 1, wherein: the crankshaft (1) is also provided with an auxiliary sliding bearing (7) for auxiliary support; the sub-sliding bearing (7) is a dynamic pressure sliding bearing.

7. The high speed press crankshaft support structure of claim 6, wherein: the crankshaft (1) is also provided with an auxiliary rolling bearing arranged in parallel with the auxiliary sliding bearing (7), and the auxiliary rolling bearing is arranged close to the corresponding auxiliary sliding bearing (7); under the no-load running state, the inner ring of the auxiliary rolling bearing is in interference fit with the crankshaft (1), and the outer ring of the auxiliary rolling bearing is in clearance fit with the high-speed press body (2).

8. The high speed press crankshaft support structure of claim 1, wherein: the high-speed press has at least one connecting rod (8), the connecting rod (8) being mounted on the crankshaft (1) by means of a connecting rod slide bearing (9).

9. The high speed press crankshaft support structure of claim 1, wherein: the high-speed press machine body (2) is provided with two main bearing seats (10), one main bearing seat is located at a positioning and supporting end and used for positioning the first main rolling bearing (3) and the first main sliding bearing (4), and the other main bearing seat is located at a telescopic and supporting end and used for positioning the second main rolling bearing (5) and the second main sliding bearing (6).

10. A high speed press crankshaft support structure according to any one of claims 1 to 9, wherein: the first main sliding bearing (4) and the second main sliding bearing (6) are symmetrically arranged at two axial ends of the crankshaft (1).

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