JP2013210031A - Bearing device, pump, method for assembling bearing device, and method for adjusting position of oil drain groove - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an inexpensive bearing device having a simple configuration and capable of adjusting the positions of an oil supply groove and an oil drain groove according to a direction of a load applied to a rotary shaft changing according to use conditions.SOLUTION: A bearing member 11 is provided in a bearing housing 12 and a rotary shaft 5 is inserted into the bearing member 11. The bearing member 11 includes oil supply holes 19a and 19b for supplying lubricating oil 18 between the rotary shaft 5 and the bearing member 11 and an oil drain hole 21 for draining the lubricating oil 18 from between the rotary shaft 5 and the bearing member 11. An oil supply groove 23 communicated with the oil supply holes 19a and 19b and an oil drain groove 24 communicated with the oil drain hole 21 are formed on an inner peripheral surface of the bearing member 11. The bearing member 11 is rotatable in a peripheral direction of the rotary shaft 5 in relation to the bearing housing 12 and a positioning means 32 is provided to position the bearing member 11 in the bearing housing 12 in the peripheral direction.

Description

  The present invention relates to a bearing device used for a pump and the like, a pump including the bearing device, a method for assembling the bearing device, and a method for adjusting an oil drain groove position.

  Conventionally, as this type of bearing device, for example, as shown in FIG. 18, the split surface 102 of the bearing 101 is set in the same direction as the displacement direction with respect to the horizontal plane in accordance with the amount of displacement of the load point from the vertical surface. An inclined journal bearing 103 is disclosed. Thereby, the oil supply groove | channel 104 and the oil drain groove | channel 105 can be provided in an optimal position. Such a journal bearing 103 is described in, for example, Patent Document 1 below.

JP-A-2-159411 JP-A-8-128441

  However, in the above-described conventional type, it is assumed that the load F applied to the rotating shaft 106 is in a specific direction S. Therefore, when the same pump is used at different rotational speeds, the pressure loss of the piping, or the water level of the water tank When the load F is applied in another direction different from the specific direction S due to a change in the use condition of the pump, such as a change in the above, there is a problem that the above conventional example cannot sufficiently cope with it.

  On the other hand, Patent Document 2 discloses a configuration in which the bearing metal 111 is rotated by a pinion 112 and the position of the oil supply pocket 113 can be adjusted as shown in FIG. In this case, a support member (bearing or the like: not shown) for rotatably supporting the bearing metal 111, a motor 114 for rotationally driving the pinion 112, and the like are further required. Since it is necessary to form a plurality of teeth that mesh with the pinion 112, there is a problem that the configuration becomes very complicated and the cost increases.

  The present invention can adjust the positions of the oil supply groove and the oil discharge groove according to the direction of the load applied to the rotating shaft that changes depending on the use conditions, and has a simple structure and an inexpensive bearing device and pump, and a method for assembling the bearing device It is another object of the present invention to provide an oil drain groove position adjusting method.

In order to achieve the above object, according to the first invention, a bearing member having a shaft hole is provided in a bearing housing,
A bearing device in which a rotating shaft is inserted into and supported by a shaft hole of a bearing member,
The bearing member is provided with an oil supply hole for supplying lubricating oil between the rotating shaft and the bearing member, and an oil draining hole for discharging the lubricating oil from between the rotating shaft and the bearing member,
An oil supply groove communicating with the oil supply hole and an oil discharge groove communicating with the oil discharge hole are formed on the inner peripheral surface of the bearing member.
The bearing member is rotatable in the circumferential direction of the rotation shaft with respect to the bearing housing,
Positioning means for positioning the bearing member on the bearing housing in the circumferential direction is provided.

  According to this, the direction of the load applied to the rotating shaft is assumed in advance, and by rotating the bearing member in the circumferential direction of the rotating shaft according to the direction of the load, the oil supply groove and the oil draining groove can be easily formed. An optimal position can be obtained. Further, thereafter, the positions of the oil supply groove and the oil discharge groove can be easily changed.

  At this time, by positioning the bearing member on the bearing housing by the positioning means, the bearing member does not rotate carelessly, and the positions of the oil supply groove and the oil discharge groove do not deviate from the optimum positions.

In the bearing device according to the second invention, the positioning means is a pin,
The pin is engaged with the bearing member and the bearing housing in the circumferential direction of the rotating shaft.
According to this, since the bearing member can be positioned on the bearing housing with the pin, the configuration of the bearing device is simplified and the cost is reduced.

The bearing device according to the third aspect of the present invention is provided with first engaging portions that can engage with one end of the pin at a plurality of locations in the circumferential direction of the bearing member,
A second engaging portion that can engage with the other end of the pin is provided in the bearing housing.

  According to this, the bearing member is positioned on the bearing housing via the pin by engaging one end portion of the pin with the first engaging portion and engaging the other end portion of the pin with the second engaging portion. Can do. At this time, according to the direction of the load applied to the rotating shaft, the first engagement portion at the optimum position is selected from the plurality of first engagement portions, so that the oil supply can be performed even when the load direction is different. The groove and the oil drain groove can be adjusted to the optimum positions.

In the bearing device according to the fourth aspect of the invention, the positioning means is an interference fit of the bearing member by the bearing housing.
According to this, since the bearing member is positioned in the bearing housing by tightly fitting the bearing member with the bearing housing, the angle of the bearing member can be adjusted more finely than when positioning with a pin or the like, and The structure of the bearing device is simplified and the cost is reduced.

In the bearing device according to the fifth aspect of the invention, the bearing member is divided into one and the other bearing piece by a cut surface that vertically cuts the rotating shaft,
The bearing housing is divided into one and the other housing part by a cut surface that vertically cuts the rotating shaft.

The sixth invention is a pump characterized in that a rotating shaft is supported by the bearing device according to any one of the first to fifth inventions.
In the seventh aspect of the present invention, a splittable bearing member having a shaft hole is provided in a fitting portion in a splittable bearing housing,
The rotating shaft is inserted and supported in the shaft hole of the bearing member,
The bearing member is provided with an oil supply hole for supplying lubricating oil between the rotating shaft and the bearing member, and an oil draining hole for discharging the lubricating oil from between the rotating shaft and the bearing member,
An assembly method of a bearing device in which an oil supply groove communicating with an oil supply hole and an oil discharge groove communicating with an oil discharge hole are formed on an inner peripheral surface of the bearing member,
Dividing the bearing housing into one and the other housing part,
Dividing the bearing member into one and the other bearing piece;
One bearing piece is rotated in the circumferential direction of the rotation shaft, and is fitted between the rotation shaft and the fitting portion in one housing portion,
By assembling the bearing member by joining the other bearing piece to the one bearing piece, the bearing member is externally fitted to the rotating shaft,
The bearing member is rotated in the circumferential direction of the rotating shaft and positioned by positioning means,
A bearing housing is assembled by joining the other housing part to one housing part.

According to this, when assembling the bearing device, it is possible to easily adjust the oil supply groove and the oil discharge groove to the optimal positions according to the direction of the load applied to the rotating shaft that is assumed in advance.
The eighth aspect of the present invention is a method for adjusting the oil drain groove position of the bearing device in the pump described in the sixth aspect of the present invention,
By combining the vertical load obtained from the weight of the rotating body having the rotating shaft and the discharge reaction force obtained from the planned operating point of the pump, the direction of the operating load acting on the rotating body during operation is obtained,
Operating load angle from the vertical straight line passing through the axis of the rotating shaft to the operating load direction, and the position of the minimum oil film thickness at which the oil film thickness between the rotating shaft and the bearing member is minimum from the operating load direction Find the minimum oil film angle and discharge reaction force fluctuation angle until
The bearing member is rotated in the circumferential direction of the rotating shaft, and the angle from the vertical straight line to the oil drain groove in the rotating direction of the rotating shaft is the sum of the operating load angle, the minimum oil film angle, and the discharge reaction force fluctuation angle. Position the oil drain groove at an angle,
At this position, the bearing member is fixed by positioning means.

  According to this, the angle from the straight line in the vertical direction to the oil drain groove is an angle obtained by adding the operating load angle, the minimum oil film angle, and the discharge reaction force fluctuation angle, thereby forming between the rotating shaft and the bearing member. It is possible to prevent the pressure distribution of the oil film to be cut off at the oil drain groove of the bearing member. As a result, the maximum pressure of the oil film is kept low to ensure a sufficient thickness of the oil film, and the oil film can be surely interposed between the bearing member and the rotating shaft. It is possible to prevent the rotating shaft from coming into direct contact with the bearing member due to interruption.

  As described above, according to the present invention, the positions of the oil supply groove and the oil discharge groove of the bearing device can be adjusted according to the direction of the load applied to the rotating shaft, and the bearing device can be made simple and inexpensive. it can.

It is a figure of the pump provided with the bearing apparatus in the 1st Embodiment of this invention. It is a sectional view of the bearing device. FIG. 3 is an XX arrow view in FIG. 2. It is a partially cutaway front view of the bearing member of the same bearing device. It is a XX arrow line view in FIG. It is a YY arrow line view in FIG. It is a ZZ arrow line view in FIG. FIG. 3 is a partially cutaway front view of the bearing housing of the bearing device. It is a XX arrow line view in FIG. It is a figure which shows the assembly method of a bearing apparatus equally. It is a figure which shows the assembly method of a bearing apparatus equally. It is a figure which shows the assembly method of a bearing apparatus equally. It is a figure which shows the assembly method of a bearing apparatus equally. It is a figure which shows the assembly method of a bearing apparatus equally. It is the schematic which shows the optimal position of the oil groove of a bearing apparatus when the discharge amount of a pump is 100% similarly. It is the schematic which shows the optimal position of the oil groove of a bearing apparatus when the discharge amount of a pump is reduced from 100% similarly. As a reference example, it is the schematic which shows the inappropriate position of the oil groove of a bearing apparatus when the discharge amount of a pump is 100%. It is a figure of the conventional bearing apparatus. It is a figure of another conventional bearing apparatus.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
In the first embodiment, as shown in FIG. 1, reference numeral 1 denotes a horizontal-axis multistage pump, and a flow rate adjusting valve 3 for adjusting the discharge flow rate is connected to the discharge port 2 side. Further, the pump 1 includes an impeller 6 that can rotate integrally with a rotating shaft 5 that is disposed in a lateral direction in the casing 4, and a sliding bearing device 7 that supports the rotating shaft 5. The rotating shaft 5 and the impeller 6 constitute a rotating body 8.

The plain bearing device 7 has the following configuration.
As shown in FIGS. 2 and 3, the plain bearing device 7 includes a bearing member 11 having a shaft hole 10 and a bearing housing 12. The rotary shaft 5 has a shaft body 5a and a cylindrical sleeve 5b that is externally fitted to the shaft body 5a at the bearing location. Supported.

  The bearing housing 12 is detachably attached to the casing 4 of the pump 1. In the bearing housing 12, fitting holes 14 (an example of fitting portions) are formed that are open at both end surfaces in the axial direction A of the rotating shaft 5. The bearing member 11 is fitted in the fitting hole 14 and is provided in the bearing housing 12.

  As shown in FIGS. 4 to 7, the bearing member 11 includes an annular bearing back metal 16 and a bearing metal 17 provided on the inner periphery of the bearing back metal 16. The outer peripheral surface of the bearing member 11 and the inner peripheral surface of the fitting hole 14 are each formed in a spherical shape having the same diameter.

  As shown in FIGS. 2 and 4, the bearing member 11 includes two (a plurality of) lubricant oils 18 that are supplied between the outer peripheral surface of the sleeve 5 b of the rotating shaft 5 and the inner peripheral surface of the bearing member 11. Oil supply holes 19a and 19b and one (single) oil discharge hole 21 for discharging the lubricating oil 18 from between the outer peripheral surface of the sleeve 5b and the inner peripheral surface of the bearing member 11 are formed.

  The oil supply holes 19 a and 19 b and the oil discharge hole 21 are formed at positions separated by 180 ° in the circumferential direction B of the rotating shaft 5. Further, in the axial direction A, both the oil supply holes 19a, 19b are located at both ends of the bearing member 11, and the oil discharge hole 21 is located between the both oil supply holes 19a, 19b.

  As shown in FIGS. 4, 6, and 7, an oil supply groove 23 and an oil discharge groove 24 that are elongated in the axial direction A are formed on the inner peripheral surface of the bearing member 11. One end of one oil supply hole 19 a is open to one end of the oil supply groove 23. As shown in FIGS. 2 and 5, the other end of the one oil supply hole 19 a is open to one supply circumferential groove 26 a formed on the outer peripheral surface of the bearing member 11 over the entire circumference. Similarly, one end portion of the other oil supply hole 19 b opens to the other end portion of the oil supply groove 23. The other end of the other oil supply hole 19b is open to the other supply circumferential groove 26b formed on the outer peripheral surface of the bearing member 11 over the entire circumference.

  As shown in FIGS. 2, 8, and 9, the bearing housing 12 has one oil supply passage 27a communicating with one supply circumferential groove 26a and the other oil supply passage communicating with the other supply circumferential groove 26b. 27b is formed. The oil supply passages 27a and 27b are connected to an oil supply pipe or the like (not shown) for supplying the lubricating oil 18 to the bearing device 7 using an oil supply pump or the like.

  Further, a discharge peripheral groove 29 is formed over the entire circumference on the inner peripheral surface of the fitting hole 14 of the bearing housing 12. Note that one end of the oil drain hole 21 opens at the center of the oil drain groove 24, and the other end of the oil drain hole 21 opens at the discharge peripheral groove 29. Further, the bearing housing 12 is formed with an oil discharge passage 30 communicating with the discharge peripheral groove 29. The oil drain passage 30 is connected to a recovery pipe or the like (not shown) for recovering the lubricating oil 18 discharged from the bearing device 7.

  As shown in FIG. 3, the bearing member 11 is rotatable in the circumferential direction B with respect to the bearing housing 12. Further, in the bearing housing 12, a pin 32 (an example of a positioning unit) that positions the bearing member 11 on the bearing housing 12 in the circumferential direction B is provided.

  As shown in FIGS. 4 and 5, a plurality of engagement holes 34 (an example of a first engagement portion) are formed at a plurality of locations in the circumferential direction B at predetermined angles on the outer peripheral portion of the bearing member 11. . As shown in FIGS. 3, 8, and 9, an engagement recess 35 (an example of a second engagement portion) recessed outward in the radial direction is formed on the inner periphery of the fitting hole 14 of the bearing housing 12. ing. One end of the pin 32 is inserted into the engagement hole 34 and the other end is fitted into the engagement recess 35, whereby the pin 32 is engaged with the bearing member 11 and the bearing housing 12 in the circumferential direction B. The bearing member 11 is prevented from rotating in the circumferential direction B and plays a role of positioning.

  As shown in FIGS. 4, 6, and 7, the bearing member 11 is divided into one and the other bearing pieces 11 a and 11 b by a cut surface that vertically cuts the rotating shaft 5 along the axial direction A. . Both the bearing pieces 11a and 11b are joined to each other by a plurality of screws 37 (an example of a joining tool) so as to be divided.

  Further, as shown in FIG. 8, the bearing housing 12 is divided into one and the other housing parts 12 a and 12 b by a cut surface that vertically cuts the rotary shaft 5 along the axial direction A, like the bearing member 11. Has been. Both the housing parts 12a and 12b are joined in a separable manner by a plurality of bolts 38 (an example of a joining tool).

Hereinafter, the operation of the above configuration will be described.
When the pump 1 is operated and the rotary shaft 5 is rotating, as shown in FIG. 2, the lubricating oil 18 passes through both supply circumferential grooves 26a, 26b from both supply passages 27a, 27b, The oil flows through the oil supply holes 19a and 19b into the oil supply groove 23, and is supplied from the oil supply groove 23 between the outer peripheral surface of the sleeve 5b and the inner peripheral surface of the bearing member 11.

  Further, the lubricating oil 18 between the outer peripheral surface of the sleeve 5 b and the inner peripheral surface of the bearing member 11 is collected in the oil drain groove 24 and passes from the oil drain groove 24 through the oil drain hole 21 to the drain peripheral groove 29. It flows in and is discharged from the bearing device 7 through the discharge peripheral groove 29 through the oil discharge passage 30. As a result, an oil film of the lubricating oil 18 is formed between the outer peripheral surface of the sleeve 5 b and the inner peripheral surface of the bearing member 11.

  At this time, as shown in FIG. 3, one end of the pin 32 is inserted into one of the engagement holes 34 and the other end is fitted into the engagement recess 35, so that the pin 32 is in the circumferential direction B. The bearing member 11 and the bearing housing 12 are engaged with each other, whereby the bearing member 11 is positioned with respect to the bearing housing 12 in the circumferential direction B, and the bearing member 11 is not inadvertently rotated in the circumferential direction B. The oil supply groove 23 and the oil discharge groove 24 do not deviate from the optimum positions.

Further, since the bearing member 11 can be positioned with respect to the bearing housing 12 by the pin 32, the configuration of the bearing device 7 is simplified, the cost is reduced, and the assembly can be easily performed.
Below, the assembly method of the bearing apparatus 7 is demonstrated.

Assembly procedure 1
First, as shown in FIG. 10, one of the housing portions 12 b of the bearing housing 12 is attached to the casing 4 of the pump 1. In this case, in the case of a horizontal shaft pump or the like having a configuration in which the casing 4 is divided into two parts, the workability is good if one housing part 12b is attached to the divided lower casing side.

Assembly procedure 2
Next, the screw 37 is removed, the bearing member 11 is divided into one and the other bearing pieces 11a and 11b, and either one of the bearing pieces 11a is rotated in the circumferential direction B of the rotating shaft 5, and FIG. As shown in Fig. 5, the rotary shaft 5 is fitted between the rotary shaft 5 and the fitting hole 14 in the one housing portion 12b.

Assembly procedure 3
Then, as shown in FIG. 12, the other bearing piece 11b is joined to one bearing piece 11a using the screw 37. As a result, the bearing member 11 is assembled and fitted onto the rotary shaft 5.

Assembly procedure 4
Next, one end of the pin 32 is inserted into the engagement hole 34 at the optimum position, and the bearing member 11 is rotated in the circumferential direction B of the rotary shaft 5 as shown in FIG. The bearing member 11 is positioned on the bearing housing 12 by setting the oil groove 24 to an optimal position and fitting the other end of the pin 32 into the engagement recess 35.

Assembly procedure 5
Thereafter, as shown in FIG. 14, the bearing device 7 is attached to the pump 1 by joining the other housing portion 12 a to the one housing portion 12 b and assembling the bearing housing 12 using the bolts 38.

  During the operation of the pump 1, the discharge amount from the discharge port 2 is adjusted by the flow rate adjusting valve 3 as shown in FIG. At this time, the direction of the operating load F acting on the rotating body 8 composed of the rotating shaft 5 and the impeller 6 is the vertical load obtained from the weight of the rotating body 8, the discharge amount of the planned operating point of the pump 1, and This corresponds to the direction of the force combined with the discharge reaction force obtained from the lift.

Next, a method for adjusting the oil drain groove position of the bearing device 7 will be described.
For example, as shown in FIG. 15, when the flow rate adjustment valve 3 is opened and the discharge amount of the pump 1 is set to 100%, the load in the vertical direction and the discharge reaction force are combined as described above to obtain the operating load F. The operation load angle α1 from the vertical straight line D passing through the axis of the rotating shaft 5 to the operation load F is determined.

  Further, the minimum oil film angle β1 from the direction of the operating load F to the position P1 of the minimum oil film thickness at which the oil film thickness T between the outer peripheral surface of the rotating shaft 5 and the inner peripheral surface of the bearing member 11 is minimum is obtained. The minimum oil film angle is determined based on the fluid lubrication design. The inner diameter and width of the bearing member 11, the outer diameter of the journal, the specific heat, the density, the viscosity, the external heat radiation amount of the lubricating oil 18, the load of the bearing member 11, the journal It is calculated from the rotation speed. Further, the operating load F and the minimum thickness portion of the oil film are generated at positions shifted from the straight line D in the vertical direction in the rotational direction C of the rotary shaft 5.

  Further, the discharge reaction force fluctuation angle γ1 is obtained. The discharge reaction force fluctuation angle γ1 is an angle change caused by a change in the discharge reaction force caused by a change in the driving machine and discharge conditions when the pump 1 is operated. In this description, the rotation direction C of the rotary shaft 5 Let γ1 be the amount of change to. However, since the fluctuation occurs in both positive and negative directions, a change of −γ1 may occur in the opposite direction to the rotation direction C, and the full width of the discharge reaction force fluctuation angle is 2 × γ1.

  Here, the discharge reaction force fluctuation angle varies depending on the diameter of the pump 1 and the configuration of the plant. However, if the discharge reaction force fluctuation angle is too large, the position of the oil supply groove 23 is applied to the oil film, causing a problem. Set by range.

  After obtaining the operating load angle α1, the minimum oil film angle β1, and the discharge reaction force fluctuation angle γ1 as described above, the bearing member 11 is rotated in the circumferential direction B of the rotating shaft 5 in the same manner as in the assembling procedure 4. The oil drain groove 24 is such that the angle from the straight line D in the rotation direction C to the oil drain groove 24 is the sum of the operating load angle α1, the minimum oil film angle β1, and the discharge reaction force fluctuation angle γ1. Position.

  Thereafter, the oil supply groove 23 and the oil discharge groove 24 are easily fixed at the optimum positions by positioning the bearing member 11 on the bearing housing 12 using the pins 32 in the same manner as in the assembly procedure 4 described above. At this time, the engagement hole 34 at the optimum position is selected from the plurality of engagement holes 34 previously opened, and the pin 32 is inserted into the selected engagement hole 34. Here, the engagement hole 34 at the optimum position is larger than an angle obtained by adding the operation load angle α1 and the minimum oil film angle β1, and the operation load angle α1, the minimum oil film angle β1, and the discharge reaction force fluctuation angle γ1. This is the engagement hole 34 that is closest to the angle obtained by adding together.

Thereafter, in the same manner as in the assembling procedure 5, the other housing portion 12a is joined to the one housing portion 12b, and the bearing housing 12 is assembled.
Alternatively, as shown in FIG. 16, when the flow rate adjustment valve 3 is throttled to reduce the discharge amount of the pump 1 to less than 100%, the direction of the operating load F changes and the required operating load angle is obtained. The minimum oil film angle and the discharge reaction force fluctuation angle are α2, β2, and γ2, respectively.

  Also in this case, the bearing member 11 is rotated in the circumferential direction B of the rotating shaft 5 in the same manner as described above, and the angle from the straight line D in the rotating direction C to the oil drain groove 24 is the operating load angle α2 and the minimum oil film. The oil drain groove 24 is positioned so that the angle β2 and the discharge reaction force fluctuation angle γ2 are added together, and then the engagement hole 34 at the optimum position is selected, and the pin 32 is inserted and positioned. Thus, the oil supply groove 23 and the oil discharge groove 24 may be fixed at optimum positions. Thereby, even when the direction of the operating load F is different, the oil supply groove 23 and the oil discharge groove 24 can be easily adjusted to the optimum positions.

  As shown in FIGS. 15 and 16, even if the direction of the operating load F changes, the angle from the straight line D in the vertical direction to the oil drain groove 24 is accordingly changed to the operating load angles α1, α2 and the minimum oil film angle. By setting β1, β2 and the discharge reaction force fluctuation angles γ1, γ2 to an angle, the pressure distribution G of the oil film formed between the outer peripheral surface of the rotating shaft 5 and the inner peripheral surface of the bearing member 11 is increased. It is possible to prevent the oil drain groove 24 from being cut off. Thereby, the maximum pressure of the oil film is kept low to ensure a sufficient thickness T of the oil film, and the oil film can be reliably interposed between the outer peripheral surface of the rotating shaft 5 and the inner peripheral surface of the bearing member 11, It is possible to prevent the thinned oil film from being interrupted by the oil drain groove 24 or the like and the outer peripheral surface of the rotating shaft 5 to directly contact the inner peripheral surface of the bearing member 11.

  As a reference example for FIG. 15, as shown in FIG. 17, when the discharge amount of the pump 1 is set to 100%, the angle from the straight line D to the oil drain groove 24 is the minimum of the operating load angle α1. If the oil film angle β1 and the discharge reaction force fluctuation angle γ1 are significantly smaller than the sum of the oil film angle β1 and the discharge reaction force fluctuation angle γ1, the oil film pressure distribution G is cut off at the oil drain groove 24. As a result, the pressure of the oil film increases, the thickness T of the oil film decreases, the oil film is interrupted in the vicinity of the position P1 of the minimum oil film thickness, and the outer peripheral surface of the rotating shaft 5 directly contacts the inner peripheral surface of the bearing member 11. There is a fear.

  In the above embodiment, as shown in FIG. 4, the plurality of engagement holes 34 are provided in the bearing member 11 at a pitch of 45 °, but the pitch is not limited to a pitch of 45 °, and a finer pitch ( For example, the pitch may be 30 ° or 15 °. Alternatively, the engagement holes 34 may be provided at fine pitches at positions (positions with high frequency) that are likely to be positioned, rather than at equal pitches.

(Second Embodiment)
In the first embodiment, the pin 32 is used as an example of the positioning means. However, in the second embodiment, as another example of the positioning means, the bearing member 11 is fitted into the fitting hole 14 by an interference fit. And positioned in the bearing housing 12.

Hereinafter, the operation of the above configuration will be described.
In the same manner as in the assembling procedure 4, the bearing member 11 is rotated in the circumferential direction B of the rotary shaft 5 so that the positions of the oil supply groove 23 and the oil draining groove 24 are optimized. Then, the other housing part 12a is joined to one housing part 12b, and the bearing housing 12 is assembled. As a result, the bearing member 11 is fitted into the fitting hole 14 of the bearing housing 12 by an interference fit, so that the bearing member 11 can be arbitrarily set without using a special member such as the pin 32 in the first embodiment. Can be positioned. Accordingly, the positions of the oil supply groove 23 and the oil discharge groove 24 can be determined more finely than when the pin 32 is used, and the engagement hole 34 and the engagement recess 35 are not required, so that the configuration of the bearing device 7 is simple. Become cheaper.

  In each of the above embodiments, as shown in FIG. 2, the rotary shaft 5 has the shaft body 5a and the sleeve 5b, but may be the rotary shaft 5 that does not include the sleeve 5b. In this case, an oil film is formed between the inner peripheral surface of the bearing member 11 and the outer peripheral surface of the shaft body 5a.

  In each of the above embodiments, as shown in FIG. 1, the bearing device 7 is provided in the horizontal-axis multistage pump 1, but may be provided in other types of pumps other than the horizontal-axis multistage pump. Moreover, you may provide in apparatuses provided with the rotating shaft 5 other than the pump 1. FIG.

DESCRIPTION OF SYMBOLS 1 Pump 5 Rotating shaft 7 Bearing apparatus 8 Rotating body 10 Shaft hole 11 Bearing member 11a, 11b Bearing piece 12 Bearing housing 12a, 12b Housing part 14 Fitting hole (fitting part)
18 Lubricating oil 19a, 19b Oil supply hole 20 Oil discharge hole 23 Oil supply groove 24 Oil discharge groove 32 Pin (positioning means)
34 Engagement hole (first engagement part)
35 Engaging recess (second engaging part)
B Circumferential direction C Rotational direction D Straight line F Operating load T Oil film thickness α1, α2 Operating load angle β1, β2 Minimum oil film angle γ1, β2 Discharge reaction force fluctuation angle

Claims (8)

A bearing member having a shaft hole is provided in the bearing housing;
A bearing device in which a rotating shaft is inserted into and supported by a shaft hole of a bearing member,
The bearing member is provided with an oil supply hole for supplying lubricating oil between the rotating shaft and the bearing member, and an oil draining hole for discharging the lubricating oil from between the rotating shaft and the bearing member,
An oil supply groove communicating with the oil supply hole and an oil discharge groove communicating with the oil discharge hole are formed on the inner peripheral surface of the bearing member.
The bearing member is rotatable in the circumferential direction of the rotation shaft with respect to the bearing housing,
A bearing device comprising positioning means for positioning the bearing member in the circumferential direction on the bearing housing. The positioning means is a pin,
The bearing device according to claim 1, wherein the pin is engaged with the bearing member and the bearing housing in a circumferential direction of the rotating shaft. The first engaging portion that can engage with one end of the pin is provided at a plurality of locations in the circumferential direction of the bearing member,
The bearing device according to claim 2, wherein a second engagement portion that can engage with the other end portion of the pin is provided in the bearing housing. 2. The bearing device according to claim 1, wherein the positioning means is an interference fit by a bearing housing of the bearing member. The bearing member is divided into two bearing pieces, one and the other, by a cut surface that vertically cuts the rotating shaft,
The bearing device according to any one of claims 1 to 4, wherein the bearing housing is divided into one and the other housing part by a cut surface that vertically cuts the rotating shaft. A rotary shaft is supported by the bearing device according to any one of claims 1 to 5. A separable bearing member having a shaft hole is provided at a fitting portion in the separable bearing housing,
The rotating shaft is inserted and supported in the shaft hole of the bearing member,
The bearing member is provided with an oil supply hole for supplying lubricating oil between the rotating shaft and the bearing member, and an oil draining hole for discharging the lubricating oil from between the rotating shaft and the bearing member,
An assembly method of a bearing device in which an oil supply groove communicating with an oil supply hole and an oil discharge groove communicating with an oil discharge hole are formed on an inner peripheral surface of the bearing member,
Dividing the bearing housing into one and the other housing part,
Dividing the bearing member into one and the other bearing piece;
One bearing piece is rotated in the circumferential direction of the rotation shaft, and is fitted between the rotation shaft and the fitting portion in one housing portion,
By assembling the bearing member by joining the other bearing piece to the one bearing piece, the bearing member is externally fitted to the rotating shaft,
The bearing member is rotated in the circumferential direction of the rotating shaft and positioned by positioning means,
A method for assembling a bearing device, comprising assembling a bearing housing by joining the other housing part to one housing part. An oil drain groove position adjusting method for a bearing device in a pump according to claim 6,
By combining the vertical load obtained from the weight of the rotating body having the rotating shaft and the discharge reaction force obtained from the planned operating point of the pump, the direction of the operating load acting on the rotating body during operation is obtained,
Operating load angle from the vertical straight line passing through the axis of the rotating shaft to the operating load direction, and the position of the minimum oil film thickness at which the oil film thickness between the rotating shaft and the bearing member is minimum from the operating load direction Find the minimum oil film angle and discharge reaction force fluctuation angle until
The bearing member is rotated in the circumferential direction of the rotating shaft, and the angle from the vertical straight line to the oil drain groove in the rotating direction of the rotating shaft is the sum of the operating load angle, the minimum oil film angle, and the discharge reaction force fluctuation angle. Position the oil drain groove at an angle,
An oil drain groove position adjusting method for a bearing device, wherein the bearing member is fixed by positioning means at this position.

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