A transducer head suspension assembly

Abstract: A flanged load beam (10;20) in a transducer head suspension assembly is provided with reinforcement means (7;8) which does not increase the height of the load beam. The reinforcement means can be in the form of longitudinal ribs (7) disposed between the flanges (6). The reinforcement means can also be provided by bending over the flanges (6) to form wings (8). Alternatively, the flanges can be bent over towards the centre of the load beam. Provision of such reinforcement means enables the overall height of the load beam to be reduced.

Description: This invention relates to a transducer head suspension assembly. In almost all present record disk data storage devices, both small and large, a transducer head suspension assembly of the form shown in Fig. 4 of the accompanying drawings and disclosed in EP-A- 0007401 is used. Figs. 4(a) and (b) show a perspective view and a side view, respectively, of that prior art head suspension assembly. The head suspension assembly 40 consists of a slider 1 having a coil for writing and reading data relative to a magnetic disk 30, a flexure 2 or a gimbal spring for supporting the slider 1, a load beam 3 for holding the flexure 2, and a mounting block 4 for fixing the load beam 3 on an accessing arm 9. The slider is held by the head suspension assembly so that the slider can travel stably over the disk at a constant distance therefrom. In particular, the slider must be held in operation at a constant distance from the disk regardless of the distortion of the disk surface or external vibrations. If the distance between the slider and the disk cannot be held constant, write failure and/or read error may occur. In the worst case, the head will collide against the disk causing a head crash. Once a head crash occurs, written data cannot be read any more. In order to hold the slider at a constant distance from the disk, the load beam among the components of the head suspension assembly is provided with the required mechanical characteristics such as natural frequency and rigidity by bending the edges 6 upwards as shown in Fig. 4. That is, the load beam has a structure consisting of a long, narrow plate-like base 5, and edges 6 bent upward from the base 5. Although the height h of the load beam (i.e., the height of the edges 6) depends on the material of the load beam, it cannot be reduced below a certain value, or its mechanical characteristics will be degraded. The reason for that is that if the height h is lower than a certain value, the natural frequency of the load beam decreases and affects the sampling cycle of a head positioning servo operation, and the resistance of the load beam against bending weakens, thus affecting the head access operation. In JP-A-61-222020 there is disclosed a support mechanism for a magnetic head which is adapted to reduce external noise. A hollow support arm which is earthed surrounds the lead wires of the magnetic head. The hollow part of the support arm is shown as comprising a lower plate and an upper plate interconnected by side walls. In magnetic disk devices, particularly in small hard disk devices, increases in both head access speed and storage capacity are required as improvements are made in the performance of personal computers in which such disk devices are incorporated. When the speed of the head access operation is increased, the natural frequency of mechanical parts involved in such an operation, especially of a head suspension load beam must be high; and therefore, the rigidity of each part must be high. On the other hand, two approaches are employed for increasing storage capacity: an increase in the amount of information stored on a disk, and an increase in the number of disks used in a disk device. For the former, the amount of information has been considerably increased by the use of thin film magnetic disks, thin film heads, and MIG (Metal In Gap) heads. For the latter, the external dimensions, especially the height, of disk devices are limited because they are incorporated in personal computers. Therefore, it is difficult to increase the numbers of disks and heads without increasing the height of the disk devices. In fact, although the disk thickness has been decreased by replacing the aluminum substrate with glass, it is impossible to further decrease disk thickness because of problems relating to magnetic properties as well as the mechanical strength of the disk. Also, decreasing the height of a load beam lowers its natural frequency in the primary vibration mode, causing problems in the head access operation. Accordingly, the Applicants tried to find a means of decreasing the height of a load beam without degrading its mechanical properties. First, the applicants considered making a load beam out of a material of high rigidity to decrease its height. However, such a material was difficult to machine precisely, and the high rigidity of the material made it difficult for the slider to travel properly. Also, the use of such a special material led to an increase in production costs. Therefore, desirable effects cannot be expected from the selection of such a material. Next, experiments to minimise the influence of reducing the height of the load beam on its mechanical properties were carried out by increasing the thickness of the load beam. As the thickness of the load beam was increased, its natural frequency increased. However, the spring constant of the load beam was also increased significantly. The great change in the value of the spring constant affects the travelling characteristics of the slider, and the performance and reliability of the magnetic disk device are significantly lowered. Therefore, improved mechanical properties cannot be expected from such an increase in thickness. Further experiments were carried out to minimise the influence of reducing the height of the load beam on its mechanical properties by decreasing the length of the load beam. As the length of the load beam was decreased, its natural frequency increased moderately, and the change in the spring constant was small. In order to increase natural frequency to the desired value, however, the length of the load beam must be considerably shortened, resulting in a large increase of the spring constant. Therefore, a decrease in the length of the load beam will not improve its mechanical properties sufficiently. Since the selection of material, increase in thickness, or decrease in length will not reduce the height of the load beam effectively, for example, in a small 3.5-inch hard disk device, the maximum numbers of disks and heads are limited to 4 and 8, respectively, due to the limitation of the height. Nevertheless, in order to achieve an increase in the storage capacity of a magnetic disk device, the numbers of disks and heads used in the disk device must be increased. This invention seeks to provide a transducer head suspension assembly including a load beam having a small height and excellent mechanical properties. By using a head suspension load beam embodying this invention, a magnetic disk device with an increased number of disks and heads can be provided. This invention provides a transducer head suspension assembly including a load beam provided with reinforcing side flanges to form an open channel, which flanges determine the height of the load beam, the load beam being provided with further reinforcement means which does not increase the height of the load beam and does not close said open channel. The provision of reinforcement can be achieved by fixing rod-type ribs on the base portion, or by forming drawn ribs using a press. When drawn ribs are used, since a sheet metal such as a stainless steel sheet is simply drawn, the head suspension lead beam can be fabricated easily. The use of a structure providing the reinforcement member not higher than the side margin portion on the base portion, or a structure bending the side margin portion substantially parallel with the plane of the base portion or further toward the plane of the base portion enables the natural frequency of the primary vibration mode to be maintained at a practically required level without degrading the mechanical properties, especially rigidity, even if the height of the load beam is decreased to one-half of the conventional minimum value. How the invention can be carried out will now be described by way of example, with reference to the accompanying drawings, in which: Fig. 1a shows a perspective view of a head suspension assembly including a lead beam provided with reinforcing drawn ribs; Fig. 1b is a magnified cross-section taken on the line A-A' of Fig. 1a; Fig. 2a shows a perspective view of a head suspension assembly including a lead beam provided with reinforcing wings; Fig. 2b is a magnified cross-section taken on the line B-B' of Fig. 2a; Fig. 3 is a graph showing the relationship between natural frequencies and the widths of wings on a load beam; Figs. 4a and b show a perspective view and a side view, respectively, of a conventional head suspension assembly; Fig. 5 is a perspective view indicating the shape of the primary vibration mode of a load beam having a height half the height of conventional load beams; and Fig. 6 is a perspective view of a magnetic disk data storage device using a head suspension assembly embodying the invention. Referring to Fig. 1, a head suspension assembly includes a load beam 10 having a base 5 and side flanges 6. The base 5 is provided with drawn ribs 7 for reinforcement. The base 5 is made of a long, narrow piece of sheet metal. The side flanges 6 are almost perpendicular to the base 5. The drawn ribs 7 have a height not exceeding the height of the flanges 6, and are formed almost parallel to the flanges 6. The load arm 10 is connected to a head actuator arm 9 via a mounting block 4. Referring now to Fig. 2, a head suspension load beam 20 is reinforced by bending the upper part of the flanges almost parallel to the base so as to form wings 8 of a height not exceeding the height of the flanges 6. The wings 8 may be bent downwards in the head supporting direction as shown by the broken lines in Fig. 2(b). Although Fig. 2 shows an example of the load beam with the flanges bent outwards, the flanges may be bent inwards as shown by the broken lines in Fig. 2(b). Lead wires used to connect to the head are provided on the back side of the load beam, that is, the opposite side from the head supporting side, thereby the lead wires are not exposed to wind caused by the rotation of disks and the aerodynamic action of the wind on the load beam is not disturbed. Consequently, in head positioning, the occurrence of disturbance can be prevented. Although Figs. 1 and 2 show examples of load beams having upward-facing flanges, i.e., in the opposite direction to the head supporting side, the flanges may be bent downwards, i.e., towards the head supporting side. In such a case, reinforcing members are provided on the bottom of the base, i.e., on the head supporting side. Fig. 6 shows a magnetic disk device 60 having increased numbers of disks and heads by employing head suspension assemblies including load beams 20. The mechanical advantages of the head suspension assembly having a structure according to this invention will be described below. First, a conventional load beam 40 as shown in Fig. 4 was analysed. The natural frequency of the primary vibration mode was found to be about 2 kHz. Next a load beam having a height half the height of the conventional load beam was fabricated and analysed in the same manner. The result showed that the natural frequency of the primary vibration mode decreased to 1.2 kHz, and in this primary vibration mode, the load beam became deformed as shown in Fig. 5. Thus, it was found that reduction of height was not practical because of the decrease in natural frequency of the primary vibration mode. On the other hand, since natural frequencies of secondary or higher modes were 2 kHz or more, although they decreased slightly, no improvement was required. For the reduction of load beam height, therefore, it is sufficient to consider natural frequencies of the primary vibration mode. Then, a load beam having half the height of a conventional load beam, and provided with drawn ribs 7 as shown in Fig. 1 was analysed. It was found that the natural frequency of the primary vibration mode was about 1.6 kHz, about a 400 Hz increase from that without ribs. Since such a decrease in natural frequency causes no problems in practical use, the provision of drawn ribs has made it possible for the height of the load beam to be halved. A load beam having a height half the height of a conventional load beam, and provided with wings 8 as shown in Fig. 2 was also examined. The result showed that the natural frequency of the primary vibration mode was about 1.8 kHz, about a 600 Hz increase from that without wings. The halving of the height of the load beam has also been made possible by the provision of wings. With either the provision of drawn ribs or wings, natural frequencies of secondary or higher vibration modes were 2 kHz or more, causing no problems. Furthermore, by specifying the forms of drawn ribs or wings, the natural frequency of the load beam can be optimised. For example, the cross-section of a drawn rib may be quadrangular, triangular or semicircular. When a quadrangular, especially when a trapezoidal cross-section was used, the natural frequency of the primary vibration mode was found to be about 1.6 kHz, and about a 400 Hz increase was achieved. In the case of a triangular cross-section, the natural frequency was about 1.4 Hz, an increase of about 200 Hz. In this case, however, the edge of the triangular rib was difficult to bend accurately at an acute angle by pressing or bending. Fig. 3 shows the results of measurements on a stainless-steel load beam having a thickness of 76 µm and a length of 30 mm. As the width of the wings was increased, the natural frequency of the primary vibration mode increased, while the natural frequency of the secondary vibration mode decreased. From these results, the preferable wing width was found to be 0.2 to 0.5 mm. Although the above embodiments include a load beam having either drawn ribs or wings, a structure having both of them, or a combined structure with such reinforcement and a shortened beam length may also be used, thereby improving the natural frequency characteristics in the primary vibration mode.

Claims: A transducer head suspension assembly including a load beam (10;20) provided with reinforcing side flanges (6) to form an open channel, which flanges determine the height of the load beam, the load beam being provided with further reinforcement means (7;8) which does not increase the height of the load beam and does not close said open channel. An assembly as claimed in claim 1, in which, the further reinforcement means comprises at least one longitudinal rib (7) disposed between the flanges. An assembly as claimed in claim 2, in which the further reinforcement means comprises a pair of longitudinal ribs (7), an individual one of the ribs lying substantially parallel to each of the flanges. An assembly as claimed in claim 2 or claim 3, in which the rib or ribs is/are formed by a drawing operation on the material of the load beam. An assembly as claimed in claim 1, in which the further reinforcement means comprises bending over the edges (8) of the flanges so that the edges lie substantially parallel to or are inclined towards the base of the load beam. An assembly as claimed in claim 1, in which the further reinforcement means comprises the combination of at least one longitudinal rib disposed between the flanges and bending over the edges of the flanges so that the edges lie substantially parallel to or are inclined towards the base of the load beam. An assembly as claimed in any preceding claim, in which lead wires to the head are disposed on the opposite side of the load beam to the head. An assembly as claimed in any preceding claim, in which the load beam is flanged on the side which supports the head. An assembly as claimed in any of claims 1 to 7, in which the load beam is flanged on the opposite side to that which supports the head.

Inventors: AOYAGI AKIHIKO, ENDO TATSUYA, TERASHIMA HIROSHI, AOYAGI, AKIHIKO, ENDO, TATSUYA, TERASHIMA, HIROSHI
Applicants: IBM, INTERNATIONAL BUSINESS MACHINES CORPORATION
Application year: 1989
Main classification: G11B5
IPC codes: G11B5, G11B21