KR100221860B1 - Bearing device for connecting rod of crank press - Google Patents

Abstract

[purpose]

Minimize the amount of movement in the press load direction while increasing the load capacity.

[Configuration]

The sliding bearing 31 in which the inner diameter center 0b (axis Z11) is eccentrically mounted by a predetermined amount e2 with respect to the axis Z1 of the eccentric portion 2, and the inner diameter center 0j (axis Z12) are eccentric portions. It consists of a pair of rolling bearings 41 and 41 which coincide with the axis Z1 of (2) and are mounted on both sides thereof, and the position of the minimum distance ho of the sliding bearing 31 is maximized in the press load direction. At the same time, the minimum distance ho is determined by the residual radial direction clearance of the rolling bearing 41 and the static load rating of the rolling element 43. It formed below the sum total (delta C + delta r) with the deformation | transformation amount (delta r) based on.

Description

Bearing device for connecting rod of crank press

The present invention relates to a bearing device for a connecting rod of a crank press.

In the conventional general crank press 50, as shown in FIG. 9, the slide which connects the crown 51 and the bed 52 with the several column 53, comprises a frame, and installs an upper mold | type. 54 is attached to the upper and lower reciprocating movement.

The bolster 55 for installing the lower die is fixed to the bed 52. In the crown 51, the crankshaft 1 held rotatably about the axis Z0 by the several press bearing apparatus 10P is arrange | positioned, and the eccentric part 2, 2 and the slide 54 are arrange | positioned. It is connected by a pair of connecting rods (3, 3).

Moreover, the center (axis Z1) of the eccentric part 2 is eccentrically by the predetermined amount in the axis Z0.

Therefore, when the crankshaft 1 is rotated, press work can be performed, making the slide 54 reciprocate up and down. Here, 30P is a bearing device for the connecting rod, 57 is a flywheel, 58 is a clutch, 59 is a brake.

Here, the conventional press bearing apparatus 10P has the inner diameter center (axis Z01) concentric with the center of the crankshaft 1 (axis Z0) and simultaneously with the outer peripheral surface of the crankshaft 1 as shown in FIG. Cylindrical sliding bearings 11 provided with a constant clearance C1 for supplying lubricating oil OIL, and the inner diameter center (axis Z02) as shown in FIG. 11, as the center of the crankshaft 1 (axis line). It consists of a pair of rolling bearing 21 arrange | positioned concentrically with Z0).

Therefore, in the no-load state in which the crankshaft 1 is rotated to move the slide 3 up and down, the weight of the slide 54 or the like is lowered in the press bearing device 10P as shown in FIG. It is applied as the rated load (W). On the other hand, at the time of press working, the press load F which applies also to upward 100TON or more as reaction force of a press load is applied.

Thus, since the press bearing apparatus 10P of the crankshaft 1 has severe load-bearing conditions, when the sliding bearing 11 is used, the clearance and oil supply condition of a bearing inner diameter and the crankshaft outline are lubricated. And groove grooves and the like, and when the rolling bearing 21 is used, it has a very rigid structure compared to the general one.

However, when the single sliding bearing 11 of FIG. 10 is adopted, when the oil film thickness, that is, the clearance C1 is increased in order to increase the load carrying capacity, the crankshaft 1 with respect to the sliding bearing 11 The relative position of the up-down direction fluctuates, and the bottom dead center position precision of the slide 54, in other words, die height changes. Such a change in die height is difficult to allow in the present time when high precision is expected. On the other hand, in the case of using the pair of rolling bearings 21 shown in FIG. 11, the load capacity of a large crank press alone cannot be tolerated in many cases. Moreover, even if it is applied to a small crank press, cost will become very high.

In this way, the present applicant has developed and proposed the so-called composite bearing device 10P1 in which the sliding bearing 11 and the pair of rolling bearings 21 are installed side by side as shown in FIG. -89425).

That is, the composite bearing 10P1 mainly has a pair of rolling bearings 21 for the purpose of regulating the amount of movement of the crankshaft 1 within a certain range, and a sliding bearing mainly for the purpose of increasing the load capacity. 11) the centers of the inner diameters (axis lines Z02 and Z01) are arranged in the same manner as the center of the crankshaft 1 (axis line Z0). Therefore, the moving amount of the crank side 1 is regulated by the pair of rolling bearings 21, and at the same time, the load bearing capability of the sliding bearings 11 can be increased.

As described above, the press bearing device is improved to (10P1, 10P1), respectively, from the viewpoint of minimizing the die height change due to the amount of movement of the crankshaft 1 and increasing the load capacity. There was little interest in the apparatus 30P.

That is, the conventional bearing device 30P for connecting rod has clearance C2 between the eccentric part 2 (axis Z1) and the large end part 3U of the connecting rod 3, as shown in FIG. It is formed of the cylindrical sliding bearing 31 arrange | positioned. Therefore, the same problem as the conventional press bearing apparatus 10P shown in FIG. 10 concerning the crankshaft 1 exists. Also, as shown in FIG. 14, even when a pair of rolling bearings 41P are disposed to form the connecting rod bearing device 30P, the conventional press bearing device 10P shown in FIG. The same problem occurs.

Here, if the press load F on the slide 54 side is transmitted to the crankshaft 1 via the connecting rod 3 and the eccentric part 2, no matter what method the press bearing apparatus is researched and connected, If a large amount of movement that affects the die height occurs in the bearing device 30P for rods, it is difficult to further increase the processing accuracy of the crank press 50 as a whole. In particular, when the direction and magnitude of the load applied to the connecting rod bearing device 30P are changed at a viewing angle, in consideration of inherent circumstances, minimizing the amount of movement of the connecting rod bearing device to minimize the press bearing device 10P. It is no exaggeration to say that it is equal to or more important than that. The same applies to the load carrying capacity.

In addition, if the load carrying capacity of the connecting rod bearing device can be further improved and the movement amount can be further reduced, the press bearing device can be further improved to significantly improve the press working precision compared to the conventional method. do. In other words, also in the composite bearing apparatus 10P1 shown in FIG. 12 which is considered the best conventionally,

(1) The hydraulic pressure generated in the sliding bearing 11 is constant over the entire circumference. This is because the clearance C1 is uniform in the entire circumference. Moreover, the press load F is significantly larger than the weight W at the time of driving. Therefore, since it is necessary to raise a hydraulic value so that it can endure press load F, there exists many wastes, such as having to supply the lubricating oil OIL with a high pressure large capacity.

(2) Since the load bearing capacity of the rolling bearing 21 is increased by measures such as an increase in the deformation amount of the rolling bearing 21, a special rolling bearing must be employed, thereby increasing the cost. In addition, in the case where the large deformation amount of the rolling element is visually recognized, it is impossible to satisfy the further higher precision requirement of clearance. That is, it is because the amount of movement of the crankshaft 1 in the up-down direction will appear as a change of die height as it is.

(3) Problems to be solved, such as causing excessive device, because countermeasures must be taken in the entire circumferential direction even when the load capacity of the cranks shaft 1 is increased in the specific radial direction and the movement amount is reduced. Because it remains.

It is an object of the present invention to provide a bearing device for a connecting rod for a crank press that can actively suppress the overall circumferential movement of the shaft due to the press load while actively increasing the oil film pressure to enhance the load capacity.

1 is an overall configuration diagram showing an embodiment of the present invention.

2 is a longitudinal sectional view of the bearing device for the connecting rod of FIG.

3 is an enlarged cross-sectional view of the main portion of the rolling bearing of FIG.

4 is a cross-sectional view of the sliding bearing of FIG.

5 is a view for explaining the principle of oil film pressure of the sliding bearing of FIG.

6 is a view for explaining a method of obtaining the pressure coefficient of FIG.

7 is a longitudinal sectional view of the press bearing device of FIG.

8 is a cross-sectional view of the press bearing device of FIG.

9 is an overall configuration diagram for explaining a conventional example.

10 is a longitudinal sectional view for explaining a conventional press bearing device (sliding bearing type).

11 is a longitudinal sectional view for explaining a conventional press bearing device (cloud bearing type).

12 is a longitudinal sectional view for explaining a conventional press bearing device (compound bearing type).

13 is a longitudinal sectional view for explaining a conventional bearing device for a connecting rod (slide bearing type).

14 is a longitudinal sectional view for explaining a conventional bearing device for rolling rods (cloud bearing type).

* Explanation of symbols for main parts of the drawings

1: crankshaft 2: eccentric part

3: connecting rod 3U: large end

10: press bearing device 11, 11A-11B: sliding bearing

21: rolling bearing 30: bearing device for connecting rod

31: sliding bearing 32: eccentric deformation bush

33: round bush 35: wedge membrane action zone

36: reverse wedge membrane action zone 41: rolling bearing

42: inner race 43: rolling element

44: retainer 45: outer race

50: crank press 51: crown

52: bed 53: column

54: Slide 55: Bolster

56: main motor 57: flywheel

58: clutch 59: brake

Z0: Axis of the crankshaft (center) Z1: Axis of the eccentric part

Oj: Center of eccentric (center of inner diameter of rolling bearing)

Ob: inner diameter center of the sliding bearing

P: oil film pressure ho: value of minimum distance

δc: residual radial direction clearance after assembly

δr: deformation based on static load rating of rolling elements

F: press load

In the conventional connecting rod bearing device 30P shown in FIG. 13, the center (axis Z1) of the eccentric part 2 swings at a speed smaller than the swinging speed of the sliding bearing 31, so that it can be rotated. , The oil film pressure generated by the action of the wedge film is extremely small, so it is difficult to have a large load capacity, and at the same time, the thickness of the oil film is changed by the press speed (rotational speed of the crankshaft 1) and the inertia force of the brake drove. Therefore, it has a big influence on die height and becomes a factor which reduces the press working precision.

Therefore, the present invention actively strengthens the wedge membrane action of the lubricating oil by using the rotational movement of the crankshaft (eccentric portion), while the sliding bearing is eccentrically disposed so that the maximum oil pressure generated thereby coincides with the press load direction. At the same time, the center of the inner diameter is located in the rotational direction by the eccentric angle, and at the same time, the value of the minimum distance of the sliding bearing on the press load side is determined by the amount of deformation caused by the static load of the rolling element of the rolling bearing and the residual radial direction clearance after the rolling bearing is assembled. The said object is achieved by forming smaller than a total value. Here, the maximum oil film pressure in the present invention means a pressure approximating the maximum oil film pressure or the maximum oil film pressure.

That is, the connecting rod bearing device of the crank press according to the present invention connects the eccentric portion of the rotationally supported crankshaft of the plurality of press bearing devices and the slide through the connecting rod, and rotates the crankshaft to reciprocate the slide up and down. A bearing device for a connecting rod of a crank press, comprising: a slide bearing having an inner diameter center eccentrically mounted with respect to an axis of the eccentric portion, and a pair of inner diameter centers coinciding with an axis of the eccentric portion and simultaneously mounted on both sides of the sliding bearing; Consists of rolling bearings, the minimum distance formed between the eccentric portion by the eccentric mounting of the sliding bearing is determined as the position where the maximum oil film pressure can be generated in the press load direction using the rotational movement of the crankshaft. At the same time, the value of the minimum clearance is The remaining radicals formed as a total value or less of the amount of deformation based on the corrected dynamic load rating of the Al direction clearance and the rolling element after characterized.

[Action]

In the bearing device for connecting rods of the crank press according to the above configuration, the pair of rolling bearings regulate the relative movement amount in the entire circumferential direction between the eccentric portion of the crankshaft and the large end portion of the connecting rod within a predetermined range. On the other hand, since the sliding bearing is eccentric with the inner diameter center of the rolling bearing and at the same time the minimum distance is determined at the position where the maximum oil film pressure can be generated in the press load direction, the load bearing capacity against the press load can be greatly increased. have. In addition, since the value of the minimum spacing is less than or equal to the amount of deformation based on the residual radial direction clearance after the rolling bearing assembly and the static load rating of the rolling element, the amount of movement that may affect the die height can be minimized.

EXAMPLE

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

1 is an overall configuration diagram, FIG. 2 is a longitudinal sectional view, and FIG. 3 is an enlarged sectional view of the main portion.

In FIG. 1, the basic configuration of the crank press 50 is similar to that of the conventional example (FIG. 9), but the crankshaft 1 is held by four press bearing devices 10, and the axis Z0 is maintained. It is rotated about the center. In addition, the eccentric portions 2 and 2 and the large ends 3U and 3U of the connecting rods 3 and 3 are connected via the present bearing devices 30 and 30 for connecting rods. The center (axis line Z1) of each eccentric part 2 is eccentrically by the predetermined amount E with respect to the center (axis line Z0) of the crankshaft 1. Here, 56 is a main motor with a belt fastened to the flywheel 57.

As shown in FIG. 2, the connecting rod bearing device 30 includes a sliding bearing 31 having an inner diameter center (axis Z11) eccentrically mounted with respect to the center of the eccentric portion 2 (axis Z1), and an inner diameter. The center (axis Z12) coincides with the center (axis Z1) of the eccentric portion 2 and is composed of a pair of rolling bearings 41, 41 mounted on both sides of the sliding bearing 31 at the same time. In other words, each rolling bearing 41 is concentric with the center of the eccentric portion 2 in order to regulate the relative amount of movement in the entire circumferential direction between the large end 3U and the eccentric portion 2 of the connecting rod 3. have. One sliding bearing 31 is formed with both rolling bearings 41 and 41 so as to generate a large oil film pressure against the press load F by using the rotational movement of the crank shaft 1 (eccentric portion 2). Eccentric excretion.

In this embodiment, the sliding bearing 31 has an eccentrically deformed bush 32 fitted to the eccentric portion 2 shown in FIG. 4 for convenience of manufacture, assembly and eccentric excretion, and the eccentrically deformed bush 32. It is formed of the round bush 33 which is fitted and is fitted to the large end 3U at the same time.

Each of the rolling bearings 41 has an inner race 42 fitted to the eccentric portion 2 as shown in FIGS. 2 and 3, a plurality of rolling elements 43 held by the retainer 44, and It is formed of the outer race 45, and is assembled by securing the radial direction clearance (δ c). Here, the deformation amount due to the static load rating of the rolling element 43 is defined as δ r.

Here, the eccentric direction of the sliding bearing 31 and the minimum spacing ho formed by this eccentric excretion are determined by the following technical basis.

That is, in FIG. 4 and FIG. 5, when the eccentric part 2 is eccentrically rotated by the rotation of the crank side 1, the oil film pressure P which generate | occur | produces in each site | part of the sliding bearing 31 is It is obtained from Equation 1.

P = kp ( U r / c ² ) ..... Equation 1

However, each symbol means the following.

: Viscosity of lubricant

U: circumferential speed of the eccentric part (axis) (2)

r: radius of eccentric part (axis) 2

c: Radial spacing, which is a variable depending on each part of the circumference represented by (D-d) / 2.

kp is the pressure coefficient, which is determined by the bearing angle θ and the eccentricity ε (= e2 / c) as shown in FIG.

e2: eccentricity

Moreover, the oil film shape (oil film thickness) h is calculated | required by h = c (1+ (epsilon) * COS (theta)). If the value of the minimum interval is ho, the value h1 of the maximum interval on the opposite side becomes h1 = 2C-ho. Therefore, the wedge film | membrane action (oil film pressure rise) area | region 35 shown in FIG. 5 deforms between the largest distance h1 to the minimum distance ho in the rotation direction of the eccentric part 2. 36 is a reverse wedge action (oil film pressure drop) region.

Here, the eccentric amount e2 and the eccentric angle ø (e.g., 15 degrees) to determine the position of the minimum gap ho so that the maximum oil film pressure P can be generated in the direction of the press load F. 45 degrees) is set. This amount of eccentricity e2 is staggered with respect to the center oj of the eccentric portion 2 (axis Z1), upwardly in FIG. 4 by e11, and at the same time by e12 to the right with respect to the vertical axis passing through the center oj. Obtained by staggering positions.

Specifically, this is performed by adjusting the assembling angle of the eccentrically deformed bush 31.

In this way, even if the maximum oil film pressure P is generated in the press load direction to increase the load carrying capacity, it is impossible to attain just one high precision by increasing the moving amount. Therefore, the value of the minimum interval ho is determined to be 0 <ho <δ r + δ c. This can be established by assembling the eccentrically deformed bush 32 by tilting it in the rotational direction by the eccentric angle ø and at the same time as the eccentricity e2. Incidentally, e2 = C + δ r.

Therefore, when the eccentric part 2 and the large end part 3U of the connecting rod 3 are connected using such a connecting rod bearing device 30, a pair of rolling bearings 41 and 41 are eccentric parts ( The entire circumferential movement amount of 2) is regulated within a predetermined range. In particular, it effectively controls the press load (F) at the time of breakthrough and the inertial force in the reverse direction. Moreover, based on the position of the minimum distance ho of the pair of rolling bearings 41 and 41 and the eccentric sliding bearing 31, the rotational direction of the crankshaft 1 is used to press load F direction. Since the maximum oil film pressure P is generated, the load capacity can be greatly increased, and the amount of movement in the press load direction can be made extremely small. In other words, the impact on die height variation can be minimized.

Furthermore, in this embodiment, the overall crank press is focused on the function and performance of increasing the load capacity of the present connecting rod bearing device 30 and at the same time reducing the total circumferential movement amount, in particular, the movement amount in the press load direction. In order to further improve the precision and load-resistance capability of each of the press bearing devices 10, a plurality of sliding bearing systems shown in FIGS. 7 and 8 are employed. That is, the press bearing apparatus 10 consists of three sliding bearings 11A, 11B, 11C arrange | positioned at the axis line Z0 direction of the crank side 1, and each sliding bearing 11A, 11B, 11C is cylindrical. It is.

Here, in order to reduce the amount of upward movement of the crankshaft 1 at the slide bottom dead center with respect to the press load F shown in FIG. 1, the intermediate bearing 11B is made wide, and at the same time, the space | interval C3 of the upper side The center of the inner diameter (axis Z02) of the bearing 11B is eccentrically downward by the predetermined amount e01 with respect to the center (axis Z0) of the crankshaft 1 in order to increase the space | interval C4 of the lower side by making () small. .

On the other hand, the inner diameter centers (axis Z01, Z03) of the other bearings 11A, 11C make the crankshaft 1 as shown in FIG. 8 while making the eccentricity e01 the same as the eccentricity e01 of the central shaft center 11B. The eccentric direction is set to another with respect to the center (axis Z0). In other words, the inner diameter centers Z01, Z02, Z03 of the respective sliding bearings 11A, 11B, 11C are eccentric in the other direction by the same amount.

In this embodiment, the hydraulic lifting portions 12A, 12B, and 12C causing the hydraulic rise from the relationship between the change in the gradually narrowing interval C3 due to the eccentric action and the rotational force of the crankshaft 1 are equally spaced 120. Each bearing 12A, 12B, 12C is eccentrically arrange | positioned so that FIG. Therefore, the load applied to the crankshaft 1 can be kept uniform in the whole circumferential direction. Moreover, since the center bearing 12B is eccentric so that the space | interval C3 of an upper direction may be made small, it is possible to exhibit necessary sufficient load capacity with respect to the largest load, namely press load F. As shown in FIG.

In the press bearing apparatus 10 of such a structure, it can have various characteristics by the eccentric direction of the inner diameter center (axis Z01-Z03) of sliding bearing 11A-11C. For example, in the case of the sliding bearing 11B, the amount of movement in the press load direction of the crankshaft 1 can be minimized by reducing the thickness C3 of the upper side, ie, the oil film thickness. In addition, since the oil pressure rises as the interval gradually narrows due to the rotational movement of the crankshaft 1, high pressure can be generated slightly ahead of the minimum interval C3. In other words, by reducing the interval C3, the supply hydraulic pressure can be increased and the load-bearing capacity can be significantly increased.

By the way, according to this embodiment, the inner diameter center ob (axis Z11) is slidably mounted by the predetermined amount e2 with respect to the axis Z1 of the eccentric part 2, and the inner diameter center Oj. (Axis Z12) is constituted by a pair of rolling bearings 41 and 41 coincident with the axis Z1 of the eccentric portion 2 and simultaneously mounted on both sides thereof, and at the same time by the eccentric mounting of the sliding bearing 31. The minimum spacing (ho) to be formed is determined as the position where the maximum oil film pressure (P) can be generated in the direction of the press load (F) by using the rotational movement of the crankshaft (1), and the value of the minimum spacing ( ho) is the sum of the residual radial direction clearance δ c after the assembling of the rolling bearing 41 and the deformation amount δ r based on the static load load W of the rolling element 43 (δ c + δ r) Since the bearing device for the connecting rod 30 formed below, the total circumferential movement amount can be regulated within a predetermined range, and at the same time the load capacity is increased. It can be increased by, besides it is possible to minimize an amount of movement of the press load direction. Therefore, it is possible to reliably and smoothly perform high-precision press work with a constant die height.

In addition, since the sliding bearing 31 is formed of the eccentric deformation bush 32 and the round bush 33, fabrication and assembling are easy and the cost is low, and the position of the minimum spacing ho can be determined accurately.

In addition, since the sliding bearing 31 increases the load bearing capacity, both the rolling bearings 41 and 41 can be simplified and economical.

Furthermore, each press bearing device 10 has a predetermined amount of the inner diameter centers (axis Z01, Z02, Z03) of the three sliding bearings 11A, 11B, 11C with respect to the inner diameter center of the crankshaft 1 (axis Z0). Since the configuration is eccentric in different directions as in (e01), the load carrying capacity of the entire crank press can be increased. And since the movement amount can be made small, it is possible to perform a stable press operation with higher accuracy with an effect of the connecting rod bearing device 30. In addition, since the respective sliding bearings 11A, 11B, and 11C have a cylindrical shape, the assembly can be simplified at a low cost due to the ease of processing.

In addition, since the eccentric direction of the sliding bearing 11B in the center is smaller than the interval C3 on the upper side and the width dimension in the axial Z02 direction is larger than that of the other sliding bearings 11A and 11C, the press load is applied. The oil pressure generating capability of the part facing (F) can be increased. In other words, the crankshaft 1 is restrained by the sliding bearings 11A and 11C which differ in the eccentric direction by making the upward load carrying capacity of the crankshaft 1 sufficient at the bottom dead center of the slide. The amount of movement in all directions can be reduced.

According to the bearing device for a connecting rod according to the present invention, a sliding bearing in which an inner diameter center (axis) is eccentrically mounted by an eccentric amount with respect to an axis of an eccentric portion, and an inner diameter center (axis) coincide with an eccentric portion and an axis, Consisting of a pair of rolling bearings mounted at the same time, the minimum gap formed by the eccentric mounting of the sliding bearing is determined as the position where the maximum oil pressure can be generated in the press load direction by using the crank shaft rotational movement. Since the value of the minimum spacing is formed to be equal to or less than the sum of the residual radial direction clearance after assembly of the rolling bearing and the deformation amount based on the static load rating of the rolling element, the total circumferential movement of the shaft can be regulated within a predetermined range while Capability can be greatly increased, and the amount of movement in the press load direction can be minimized. The. Therefore, it is possible to reliably stabilize the press work with high die height.

Claims (1)

A bearing device for a connecting rod of a crank press configured to connect an eccentric portion of a crankshaft rotationally supported to a plurality of press bearing devices and a slide through a connecting rod, and to rotate the crankshaft to reciprocate the slide up and down. And a pair of rolling bearings eccentrically mounted with respect to the negative axis, and a pair of rolling bearings whose center of inner diameter coincides with the axis of the eccentric portion and are mounted on both sides of the sliding bearing, and the eccentric portion is mounted by the eccentric mounting of the sliding bearing. The minimum spacing formed between and is determined as the position where the maximum oil film pressure can be generated in the press load direction by using the rotational movement of the crankshaft, and the value of the minimum spacing after the assembling of the rolling bearing is measured. Edge based on egg direction clearance and static load rating of rolling elements A connecting rod of the crank bearing apparatus for a press, characterized in that the formation of a total value less than the amount.