TW201631263A - Rotating machine - Google Patents

Abstract

A rotating machine provided with a sliding bearing, wherein relative rotation between a shaft and a bearing sleeve is suppressed with a simple configuration and without any problems. The rotating machine is provided with: a bearing sleeve; a shaft inserted into a sleeve through-hole formed in the bearing sleeve, the shaft having formed therein a shaft through-hole that passes through the shaft in a direction intersecting the center axis of the shaft; and a rod-shaped member inserted into the shaft through-hole, both ends of the rod-shaped member protruding to the exterior of the shaft. In the bearing sleeve, two notches are formed partially in the circumferential direction, diametrically outward from the bearing sleeve through-hole. The respective protruding portions of both ends of the rod-shaped member are accommodated within the two notches.

Description

Rotating machine

This invention relates to a rotating machine, and more particularly to a sliding bearing.

In the multi-stage pump for small deep wells, in order to support the shaft, there is a case where a sliding bearing is used. Further, in order to prevent the shaft from being worn due to the sliding between the sliding bearing and the shaft, the outer peripheral surface of the shaft is in a state in which the bearing sleeve is mounted. The bearing sleeve rotates together with the shaft when the shaft rotates, and the outer peripheral surface of the bearing sleeve slides on the sliding surface of the sliding bearing as the shaft rotates. In such a deep-stage multi-stage pump, the shaft and the bearing sleeve are prevented from rotating relative to each other around the shaft from the side of the bearing sleeve by locking the nut in the direction of pressing the bearing sleeve. However, in this method, the strength of the fixed shaft and the bearing sleeve is weak, so if the sliding resistance between the outer peripheral surface of the bearing sleeve and the sliding surface of the sliding bearing is increased for some reason, the bearing sleeve is rotated when the shaft rotates. The shaft will have a relative rotation. Such relative rotation is the main cause of failure.

Here, in order to surely prevent relative rotation between the bearing sleeve and the shaft, a pump provided with a stopper mechanism has been developed. For example, in the following Patent Document 1, some stopper mechanisms are disclosed. The first example is a keyway structure provided in the bearing sleeve and the shaft. The second example is a structure in which a pin formed in a non-through hole extending in the radial direction of the shaft is engaged with the bearing sleeve. In this case, a portion of the pin that protrudes from the shaft is housed in a notch formed in the bearing sleeve so as to penetrate the radial direction (that is, to reach the outer edge portion in the radial direction).

[Previous Technical Literature] [Patent Literature]

[Patent Document 1] Japanese Unexamined Publication No. SHO 60-114296

However, in the first conventional example described above, the standard size is limited due to the specification of the key. Therefore, if a key corresponding to the small diameter of the shaft is to be selected, the selection is also considerably limited. Moreover, the processing of the keyway is relatively complex. Further, the second conventional example described above is difficult to apply to a shaft having a small diameter (for example, a diameter of 6 mm). For example, in the case where the diameter of the shaft is small, the depth (depth) of the non-through hole needs to be shortened, but such a non-through hole at a short depth makes it difficult to manage the machining accuracy. Moreover, due to the processing accuracy, the depth of the non-through hole becomes smaller than the design value. For example, when the shaft rotates, the pin is deformed and it is difficult to pull out from the non-through hole. Further, since the notch formed in the bearing sleeve is penetrated in the radial direction, the outer circumferential surface of the bearing sleeve that moves on the sliding surface of the sliding bearing is reduced as much as the notch. As a result, in order to secure a sufficient sliding area, the demand for the bearing sleeve to become large in the center axis direction is generated, resulting in an increase in size of the apparatus. These problems are not limited to the multi-stage pump for deep wells, and are common to all rotating machines with sliding bearings. Due to such a situation, a structure in which the shaft and the bearing sleeve are integrally rotated is required without requiring a simple structure. Moreover, such a structure is intended to be widely applied to various shafts such as a shaft having a small relative diameter. Moreover, such a structure is intended to be easy to process and can be easily manufactured in a short time. Moreover, such a structure is intended to be cheap. Furthermore, it is desirable to provide a rotating machine with a good rotational balance. Also, you want to miniaturize the rotating machine.

In order to solve at least a part of the above problems, the present invention can be realized as the following aspects.

According to a first aspect of the present invention, a rotary machine is provided. The rotating machine includes: a bearing sleeve; a shaft inserted into the sleeve through hole formed in the bearing sleeve, and formed with a shaft through hole penetrating the shaft in a direction crossing the central axis of the shaft; and a rod member inserted into the shaft through hole, the rod Both ends of the member protrude outside the shaft. In the bearing sleeve, two notches are partially formed in the circumferential direction from the bearing sleeve through hole to the outer side in the radial direction. The protruding portions at both ends of the rod member are respectively received in the two notches.

According to such a rotating machine, when the shaft rotates (except for the initial stage of rotation), the protruding portions at both ends of the rod-shaped member abut against the faces of the two notches forming the bearing sleeve, so that the shaft and the bearing sleeve can be integrally rotated. Moreover, the integral rotation can be realized in a simple structure as compared with the case of performing the key groove processing. Moreover, compared with the case where the key groove processing is performed, the shaft through hole can be easily machined, which is economical. Moreover, since the processing shape is simple, the processing time is also shortened. Moreover, the machining of the shaft through hole does not require the processing accuracy of the management hole depth as in the case of non-through hole machining. Furthermore, this structure can be widely applied without problems even in the shaft of a small diameter.

According to a second aspect of the present invention, in the first aspect, the shaft through hole is formed to extend in a direction perpendicular to the central axis. According to this aspect, the positioning (direction determination) of the machining tool for the shaft is facilitated during the shaft machining, so that the shaft through hole can be easily machined. Further, since the protruding portions of both ends of the rod-shaped member are disposed at the same position in the direction of the central axis, the notch positions of the bearing sleeves accommodating the protruding portions are also disposed at the same position in the central axis direction. From this point of view, it is easy to maintain the rotational balance of the rotating body (shaft, bearing sleeve, and rod-like member).

According to a third aspect of the present invention, in the first or second aspect, the shaft through hole is a through hole passing through a central axis of the shaft. According to this aspect, it is easy to maintain the rotational balance of the shaft, and it is easier to maintain the rotational balance of the rotating body (shaft, bearing sleeve, and rod-shaped member). By maintaining the rotational balance as described above, even in the case where the shaft is rotated at a high speed, occurrence of vibration or the like with unbalance can be suppressed.

According to a fourth aspect of the present invention, in the first aspect to the third aspect, the surface forming the notch of the bearing sleeve includes a surface extending in a direction in which the protruding portion of the rod member extends, and is formed to rotate when the shaft rotates The surface that the line or surface abuts with the protruding portion. According to this aspect, the rod-shaped member is less likely to be deformed than the case where the surface of the notch forming the bearing sleeve is in contact with the protruding portion.

According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the notch of the bearing sleeve is formed in a radial direction and is formed in a range that does not reach the outer circumferential surface of the bearing sleeve. According to this aspect, since the sliding surface of the bearing sleeve, that is, the outer peripheral surface, is not formed, the entire outer peripheral surface of the bearing sleeve can be utilized as a sliding surface. Therefore, the bearing sleeve can be miniaturized and the rotary machine can be miniaturized as compared with the case where the notch reaches the outer peripheral surface of the bearing sleeve.

According to a sixth aspect of the invention, in any one of the first to fifth aspect, the rod-shaped member is a parallel pin. Parallel pins are common standard components, so they are superior in terms of availability and economy.

20‧‧‧ pump

30‧‧‧Sliding bearings

31‧‧‧ bearing sleeve

32‧‧‧through holes

33, 34‧‧ ‧ gap

35, 36‧‧‧ face

37‧‧‧ outer perimeter

39‧‧‧ bearing support parts

40‧‧‧Axis

41‧‧‧ shaft through hole

45‧‧‧ nuts

50‧‧‧ parallel sales

51, 52‧‧‧ highlights

60‧‧‧ thrust bearing

80‧‧‧ motor

AL‧‧‧ center axis

The first figure shows a schematic view of a schematic configuration of a pump which is an embodiment of the present invention.

The second figure is an enlarged view of a portion of the pump shown in the first figure.

The third A diagram shows a diagram of the structure of the shaft.

The third B diagram shows a diagram of the structure of the shaft.

Figure 4A shows a diagram of the structure of the bearing sleeve.

Figure 4B shows a diagram of the structure of the bearing sleeve.

A. Example:

The first figure shows a schematic view of a schematic configuration of a pump 20 which is an embodiment of the present invention. In the present embodiment, the pump 20 is a multi-stage pump for deep wells. However, the pump 20 may be any pump having a sliding bearing. As shown in the first figure, the pump 20 includes a slide bearing 30, a shaft 40, a parallel pin 50, a thrust bearing 60, and a motor 80. One end of the shaft 40 is rotatably supported by the slide bearing 30, and the slide bearing 30 is provided on the front end side of the thrust bearing 60 (i.e., on the opposite side of the motor 80), and the other end of the shaft 40 is provided in the motor 80. The bearing (not shown) is supported to be rotatable. A bearing sleeve 31 is disposed around the shaft 40 between the sliding bearing 30 and the shaft 40. This bearing sleeve 31 rotates with the shaft 40 as the shaft 40 rotates. That is, the bearing sleeve 31 and the shaft 40 are integrally rotated while maintaining the same relative position of the shaft 40 (however, in the initial stage of the rotation of the shaft 40, the bearing sleeve 31 and the shaft 40 may rotate relative to each other only by a slight distance). The outer circumferential surface of the bearing sleeve 31 slides on the sliding surface of the sliding bearing 30 on the fixed side. As described above, by providing the bearing sleeve 31, the shaft 40 is slid with respect to the sliding surface of the sliding bearing 30 without being worn. Hereinafter, a structure for integrally rotating the bearing sleeve 31 and the shaft 40 will be described.

The second drawing is an enlarged view of the periphery of the sliding bearing 30 shown in the first figure. The third and third B diagrams show the structure of the shaft 40. The fourth and fourth B drawings show the structure of the bearing sleeve 31. As shown in the second, fourth, and fourth B drawings, the bearing sleeve 31 has a substantially cylindrical shape extending in the direction of the center axis of the shaft 40 (i.e., the central axis of rotation) in the direction of the AL. A sleeve through hole 32 penetrating the bearing sleeve 31 in the center axis AL direction is formed inside the bearing sleeve 31. As shown in the second figure, the nut 45 is attached to the front end of the shaft 40 in a state where the shaft 40 is inserted into the sleeve through hole 32 on the front end side of the thrust bearing 60. Thereby, the bearing sleeve 31 is attached to the shaft 40. A sliding bearing 30 on the fixed side is disposed around the bearing sleeve 31. The sliding bearing 30 is supported by a bearing support member 39 disposed above and below.

As shown in Figs. 4A and 4B, at the end portion on the motor 80 side of the bearing sleeve 31, two notches 33, 34 are formed partially in the circumferential direction (i.e., separated in the circumferential direction). The notches 33, 34 are formed at a position of 180 degrees rotational symmetry with respect to the central axis AL. The notches 33, 34 run through the sleeve The hole 32 extends outward in the radial direction. In the present embodiment, the notches 33 and 34 are formed in a substantially U-shape and are formed in the radial direction in a range that does not reach the outer peripheral surface 37 of the bearing housing 31. In other words, the outer peripheral surface 37 of the bearing sleeve 31 has no gap in any of the regions.

As shown in the second figure, in the shaft 40, a shaft through hole 41 penetrating the shaft 40 is formed in a direction crossing the center axis AL of the shaft 40 in the vicinity of the thrust bearing 60. As shown in the third A and third B diagrams, in the present embodiment, the shaft through hole 41 is formed to extend in a direction perpendicular to the central axis AL. Further, in the present embodiment, the shaft through hole 41 is formed to pass through the center axis AL.

As shown in the second figure, a parallel pin 50 as an example of a rod-shaped member is inserted into the shaft through hole 41. The parallel pin 50 is a common standard component, so if it is done, it is superior in terms of availability and economy. However, it is also possible to use any rod-shaped member instead of the parallel pin 50. For example, a spring pin can also be used instead of the parallel pin 50. The outer diameter of the parallel pin 50 is formed as large as possible within a range in which the parallel pin 50 can be inserted into the shaft through hole 41. That is, the gap between the parallel pin 50 and the shaft through hole 41 is set to be as small as possible. The parallel pins 50 are inserted at both ends to protrude outside the shaft 40. The protruding portions of both ends of this parallel pin 50 are referred to as protruding portions 51, 52, respectively. The protruding portions 51, 52 are respectively received in the notches 33, 34 formed in the bearing sleeve 31. In the present embodiment, even if one of the protruding portions 51, 52 abuts against the radial end surface of one of the corresponding notches 33, 34, the notches 33, 34 are formed at both ends of the parallel pin 50. The outer portion of the shaft 40 protrudes. Further, the notches 33 and 34 are formed such that the gap in the circumferential direction of the protruding portions 51 and 52 is as small as possible. Further, as shown in FIG. 4B, the notches 33 and 34 are provided with faces 35 and 36 extending in the extending direction of the protruding portions 51 and 52. Therefore, when the protruding portions 51, 52 and the faces 35, 36 abut each other, they are abutted by a line.

When the pump 20 thus constructed is driven by the motor 80 and the shaft 40 is rotated in the direction of the arrow A1 (refer to FIG. 4B), the parallel pin 50 inserted into the shaft through hole 41 also rotates integrally with the shaft 40. At this time, in the case where the gap between the parallel pin 50 and the faces 35, 36 exists, the parallel pin 50 and the bearing sleeve 31 rotate relative to each other only for a short time, and the parallel pin 50 abuts against the faces 35, 36. Thereafter, the rotational force of the shaft 40 is transmitted to the bearing sleeve 31 via the abutting portions of the protruding portions 51, 52 and the faces 35, 36, so that the shaft 40 and the bearing sleeve 31 are in a state where the relative positions of the shaft 40 and the bearing sleeve 31 are fixed. Will rotate in one. When there is no gap between the parallel pin 50 and the faces 35, 36, the shaft 40 and the bearing sleeve 31 rotate integrally from the initial stage of rotation of the shaft 40.

According to such a pump 20, the key groove is added to the bearing sleeve 31 and the shaft 40. In the case of the work, the integral rotation of the shaft 40 and the bearing sleeve 31 can be achieved by a simple structure. Further, machining the shaft through hole 41 in the shaft 40 can be carried out with a simple tool as compared with the case of performing the key groove processing, which is economical. Further, since the machining shape of the shaft 40 is simple, the machining time is also shortened. Moreover, the above structure is not problematic even for the shaft 40 having a small diameter, and can be widely used.

Further, according to the pump 20, the shaft through hole 41 is formed to extend in a direction perpendicular to the central axis AL. Therefore, when the shaft 40 is machined, the positioning (direction determination) of the machining tool of the shaft 40 becomes easy, so that the shaft through hole 41 can be easily machined. Moreover, since the shaft through hole 41 is formed to extend in a direction perpendicular to the center axis AL, the protruding portions 51, 52 are disposed at the same position in the direction of the center axis AL with respect to the positions of the notches 33, 34 formed in the bearing sleeve 31. It is also possible to have the same position in the direction of the central axis AL. Therefore, it is easy to maintain the rotational balance with respect to the entire rotating body (the shaft 40, the bearing sleeve 31, and the parallel pin 50). However, the shaft through hole 41 may be formed to extend in any direction crossing the center axis AL.

Further, according to the pump 20, the shaft through hole 41 is a through hole passing through the center axis AL. Therefore, the parallel pin 50 does not have a condition in which it is disposed off the center axis AL. Therefore, the balance of rotation about the shaft 40 is easily maintained, and the rotational balance of the rotating body (the shaft 40, the bearing sleeve 31, and the parallel pin 50) is more easily maintained. However, the shaft through hole 41 may be a through hole that does not pass through the center axis AL.

Further, according to the pump 20, when the shaft 40 rotates, the faces 35, 36 of the bearing sleeve 31 abut against the protruding portions 51, 52 by wires. Therefore, the parallel pin 50 is difficult to deform as compared with the case of abutting with a dot. The faces 35 and 36 may be formed in a curved shape that follows the outer peripheral surface of the parallel pin 50. In this case, the faces 35 and 36 abut against the protruding portions 51 and 52, and the same effect is achieved. However, the faces 35, 36 and the protruding portions 51, 52 may also abut at a point.

Further, according to the pump 20, the notches 33 and 34 of the bearing sleeve 31 are formed in the radial direction in a range that does not reach the outer peripheral surface 37 of the bearing housing 31. That is, the outer peripheral surface 37 has no gap in any of the areas. Therefore, the entire outer peripheral surface 37 can be utilized as a sliding surface. Therefore, the bearing sleeve 31 can be miniaturized in the direction of the center axis AL, and the pump 20 can be miniaturized. However, the notches 33 and 34 may be formed to reach the outer peripheral surface 37 of the bearing sleeve 31 in the radial direction.

The structure of the above-described embodiment is not limited to the multi-stage pump for deep wells, and is suitable for any rotary machine having a sliding bearing. For example, the above embodiment can also be applied to a sliding bearing Any type of pump, blower, compressor, etc.

The embodiments of the present invention have been described above based on some embodiments, but the present invention is not intended to limit the present invention. The present invention can be modified and improved without departing from the spirit thereof, and the present invention naturally includes equivalents thereof. Further, in the range in which at least a part of the above problems can be solved, or in the range in which at least a part of the effects are achieved, the components of the claims and the constituent elements described in the specification may be arbitrarily combined or omitted.

30‧‧‧Sliding bearings

31‧‧‧ bearing sleeve

32‧‧‧through holes

33‧‧‧ gap

34‧‧‧ gap

37‧‧‧ outer perimeter

39‧‧‧ bearing support parts

40‧‧‧Axis

41‧‧‧ shaft through hole

45‧‧‧ nuts

50‧‧‧ parallel sales

51‧‧‧ highlight

52‧‧‧ highlight

AL‧‧‧ center axis

Claims (6)

A rotary machine comprising: a bearing sleeve; a shaft inserted into a sleeve through hole formed in the bearing sleeve, and formed with a shaft through hole that penetrates the shaft in a direction crossing a central axis of the shaft; and a rod Inserting the shaft through hole, the two ends of the rod member projecting outside the shaft; wherein the bearing sleeve is partially formed in the circumferential direction from the bearing sleeve through hole in the radial direction; The protruding portions at both ends of the rod-shaped member are housed in the two notches, respectively. The rotary machine according to claim 1, wherein the shaft through hole is formed to extend in a direction perpendicular to the center axis. The rotary machine according to claim 1 or 2, wherein the shaft through hole is a through hole passing through the aforementioned central axis of the shaft. The rotary machine according to the first or second aspect of the invention, wherein the surface of the bearing sleeve that forms the notch is provided with a surface extending in a direction in which the protruding portion of the rod member extends, and the surface is formed to be When the shaft rotates, the wire or the surface abuts against the protruding portion. The rotary machine according to claim 1 or 2, wherein the notch of the bearing sleeve is formed in a radial direction and is formed in a range that does not reach an outer circumferential surface of the bearing sleeve. The rotary machine of claim 1 or 2, wherein the rod member is a parallel pin.