JP2008038770A - Pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pump device, stably, highly accurately and continuously operable over a long period, by incorporating a bearing cage superior in lubricating performance for excellently continuously maintaining a lubricating state of a bearing, into rolling bearings for supporting an impeller shaft. <P>SOLUTION: The pump device has: the impeller shaft S extending in the predetermined direction; a plurality of rolling bearings 2, 4 and 6 rotatably supporting the impeller shaft; and an oil bath 54 storing lubricating oil 52 for lubricating the rolling bearings. In at least one rolling bearing, the cage 26 rotatably incorporated between bearing rings 20 and 22, is formed by using a porous sintered material as its material, and has a predetermined pore on its surface and the inside, and is positioned so that its part can always contact with the lubricating oil. The lubricating oil is made to flow in the pore from the oil bath in response to rotation, and circulates by being made to flow out to the oil bath from the pore, and cools the bearing by promoting heat exchange between the inside of the pore and the lubricating oil in the oil bath. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a pump device, and more particularly to a pump device in which an impeller shaft is supported by a rolling bearing in which a bearing cage having excellent lubrication performance is incorporated.

  Conventionally, as pump devices for sucking, discharging and circulating liquids and gases, there are various types such as submersible pumps, turbine pumps, vacuum pumps, high pressure pumps and process pumps according to their applications, functions and structures. Are known. Among these, the process pump is used as a pump device for sending essential oil or the like in an oil refinery plant, for example.

  Such a process pump includes, for example, a main shaft (impeller shaft) with an impeller (impeller) that sucks and sends out essential oil or the like attached to the tip, and the main shaft is rotatably supported by a rolling bearing. Has been. In this case, the process pump needs to continue to rotate the impeller shaft with high accuracy over a long period of time so that essential oil and the like can be delivered stably and continuously. For this reason, the rolling bearing is lubricated for the purpose of reducing wear caused by friction between the inner surface, for example, the raceway surface of the bearing ring and the rolling surface of the rolling element, and preventing seizure. ing.

Here, there are mainly two types of bearing lubrication methods: grease lubrication using various greases as a lubricant and oil lubrication using various lubricants as a lubricant. It is possible to suppress the leakage of the bearing and to simplify the bearing and its peripheral structure. In contrast, oil lubrication, for example, has a feature that the fluidity of the lubricant and the cooling effect on the apparatus are high, and the lubrication performance is superior to grease lubrication.
Generally, in the process pump as described above, oil lubrication, which is superior in lubrication performance to grease lubrication, is often employed as a bearing lubrication method. Furthermore, in such oil lubrication, various measures are conventionally known in order to further improve the lubrication performance and lubrication efficiency.

For example, Patent Document 1 discloses a configuration of a bearing cage for improving the lubrication performance of a bearing during oil lubrication as an example. A porous polyamide molded body is applied to the cage as a material thereof, and the polyamide molded body is heated and formed into a cylindrical shape, and is cut and processed. In this case, the polyamide molded body, that is, the cage is set so that the porosity thereof is a predetermined value within a range of 10 to 50%.
According to the cage having such a configuration, the impregnation property of the lubricant (for example, lubricating oil) is enhanced, and a large amount of lubricating oil can be retained in the pores. For this reason, it becomes possible to improve the lubrication performance of the rolling bearing by incorporating the cage into the rolling bearing.
JP 2000-110838 A

  By the way, since the lubricating oil as a lubricant changes in performance and deteriorates as the temperature rises, it is necessary to consider the temperature range assumed at the time of use when the lubricating oil is used. For this reason, for example, the temperature range in which various types of lubricating oil can be used properly is defined by the standards of the American Petroleum Institute (API), and the lubricating oil is used within the specified temperature range. It becomes important.

  However, in the case of the polyimide cage disclosed in Patent Document 1 described above, the lubricating oil once impregnated in the pores of the cage continues to remain in the pores for a long time. In this case, the lubricating oil remaining in the pores of the cage is not likely to come into contact with the outside of the pores (for example, exposed to the internal air of the process pump), and heat is not sufficiently released, so that the temperature rises. Resulting in. In particular, polyimide has the property that heat tends to be trapped in the pores, and therefore, when lubricating oil whose temperature has risen remains in the pores, it causes a disadvantage that it does not easily decrease while the temperature of the cage rises. .

  As in the process pump described above, for example, in the case of a pump device that inhales and sends out essential oil or the like, it is necessary to avoid an excessive temperature rise in order to ensure safety, which is disclosed in Patent Document 1. In addition, the lubrication method using the cage cannot provide sufficient lubrication performance in terms of the cooling effect on the apparatus.

  The present invention has been made in order to solve such a problem, and the object thereof is excellent in lubrication performance capable of continuously maintaining the lubrication state of the bearing with respect to the rolling bearing supporting the impeller shaft. Another object of the present invention is to provide a pump device that can be stably operated with high accuracy over a long period of time by incorporating a bearing retainer.

  In order to achieve such an object, a pump device according to the present invention includes an impeller shaft extending in a predetermined direction and having an impeller attached to an extending end portion thereof, and a plurality of rotatably supporting the impeller shaft. A rolling bearing and an oil bath for storing lubricating oil for lubricating the rolling bearing. In this case, in at least one rolling bearing, the rolling element is rotatably held, and the cage that is rotatably incorporated between the races is formed using a porous sintered material as its material, and its surface In addition, predetermined pores are provided inside, and a part thereof is always positioned so as to be in contact with the lubricating oil. With such a configuration, as the retainer rotates, the lubricating oil flows into the pores from the oil bath, flows out from the pores to the oil bath, circulates, and the lubricating oil in the pores and the oil bath The rolling bearing is cooled by promoting heat exchange with the lubricating oil.

  According to the present invention, a roller bearing that supports an impeller shaft is incorporated with a bearing retainer that has excellent lubrication performance and can maintain its lubrication state well, so that the pump device can be used for a long time. You can continue to drive stably and with high accuracy.

  Hereinafter, a pump device according to an embodiment of the present invention will be described with reference to the accompanying drawings. In addition, as a pump apparatus which concerns on this invention, although various types, such as a submersible pump, a turbine pump, a vacuum pump, a high pressure pump, and a process pump, are applicable, for example, the process pump was applied here. Assuming the case, the configuration will be described below.

  FIG. 1 shows a process pump according to the present embodiment. As an example, the process pump includes a base end (same as the extension direction of the impeller shaft S (the left-right direction in FIG. 1)). An oil chamber L, a motor part M, and a pump part P are arranged in this order from the right end in the figure to the extending end (left end in the figure). That is, in this case, the process pump is provided with an oil chamber L on the base end side (right end side in the figure) of the impeller shaft S, and a pump portion on the extension end side (left end side in the figure) of the impeller shaft S. P is provided, and a motor part M is provided between the oil chamber L and the pump part P.

  The impeller shaft S has a predetermined length penetrating from the oil chamber L through the motor part M to the pump part P, and extends from the base end (right end in the figure) to the extended end (left end in the figure). An impeller 50 having a plurality of blades 56 for sucking, discharging, and circulating the liquid, gas, etc. in the pump part P is extended to the extended end (the left end in the figure). It is attached.

In the configuration shown in FIG. 1, the oil chamber L accommodates a plurality (three) of rolling bearings 2, 4, 6 that rotatably support the impeller shaft S, and these bearings 2, 4, 6 An oil bath 54 for storing a lubricating oil 52 for lubricating the oil is provided. In this case, a total of three angular ball bearings 2 and 4 and one deep groove ball bearing 6 are accommodated in the oil chamber L, and the two angular ball bearings 2 and 4 are on the base end side of the impeller shaft S. (A right side in the figure) and an axial load is applied by the angular ball bearings 2 and 4. Note that the two angular ball bearings 2 and 4 are configured as rear combination type (DB type) bearings in which the back surfaces thereof are brought into contact with each other.
On the other hand, the deep groove ball bearing 6 is fitted on the extended end side (left side in the figure) of the impeller shaft S, and a radial load is applied by the deep groove ball bearing 6.

  A predetermined amount of lubricating oil 54 is sealed in the oil chamber L and stored in the oil bath 54. In this case, the lubricating oil 54 reaches the position where the angular ball bearings 2 and 4 and the deep groove ball bearing 6 are disposed, and the liquid level 52s stored in the oil bath 54 is a constituent member of the bearings 2, 4 and 6. The oil chamber L is enclosed in a predetermined amount that is a height that can always contact a part of the inner and outer rings, rolling elements (balls, and cage) described later. Thereby, the angular ball bearings 2, 4 and the deep groove ball bearing 6 can be always lubricated.

  In this process pump, the motor part M contains an electric motor (for example, a motor (not shown)) for rotating the impeller shaft S, and the pump part P contains an impeller 50. Yes.

  FIGS. 2 (a) and 2 (b) show angular ball bearings 2 and 4 that rotatably support the impeller shaft S. The two angular ball bearings 2 and 4 can rotate relative to each other. And a plurality of rolling elements (balls) incorporated in a freely rotatable manner between a pair of race rings (inner ring 20 and outer ring 22) arranged opposite to each other and raceway surfaces 20r, 22r formed on the inner and outer rings 20, 22. ) 24 and a cage 26 that rotatably holds the rolling elements (balls) 24 one by one. In this case, the inner ring 20 is configured as a rotating wheel that rotates together with the impeller shaft S, and the outer ring 22 is configured as a stationary wheel that is always maintained in a non-rotating state.

  In the configuration shown in FIG. 2A, as an example, the inner ring 20 has a groove shoulder (track) so that one side (right side in the figure) of the outer peripheral surface is thinner than the other side (left side in the figure). It has the shape of a so-called one-sided counterbore with the shoulder of the surface 20r dropped. In this case, the counter bore 20c of the inner ring 20 is formed in a flat surface that is constant without changing the distance from the inner peripheral surface of the outer ring 22 to a predetermined distance.

  On the other hand, as an example, the outer ring 22 has one side of the inner peripheral surface (the side opposite to the counter bore 20c of the inner ring 20 (the left side in FIG. 2A)) on the other side (the right side in the figure). The groove shoulder (shoulder portion of the raceway surface 22r) is dropped so as to be thinner than that of a so-called one-side counter bore. In this case, the counter bore 22c of the outer ring 22 is formed in a flat surface that is constant without changing the distance from the outer peripheral surface of the inner ring 20 to a predetermined distance.

Note that the shapes and sizes of the counter bores 20c, 22c of the inner ring 20 and the outer ring 22 are arbitrarily set according to, for example, the sizes of the inner and outer rings 20, 22, and are not particularly limited here. For example, in addition to the configuration shown in FIG. 2A described above, the counter bore 20c of the inner ring 20 is formed in an inclined surface shape in which the distance from the inner peripheral surface of the outer ring 22 gradually increases toward the outside of the bearing. Similarly, the counter bore 22c of the outer ring 22 may be formed in an inclined surface shape in which the distance from the inner peripheral surface of the inner ring 20 gradually increases toward the outside of the bearing.
Further, in the configuration shown in FIG. 2 (a), both the inner ring 2 and the outer ring 4 are configured to have the shape of a single-side counterbore, but only one of the inner ring 2 or the outer ring 4 is configured as a single-side counterbore. You may comprise so that a shape may be comprised.

  In these angular ball bearings 2 and 4, a plurality of rolling elements (balls) 24 are rotatably held one by one at predetermined intervals and held by a cage 26, and the raceway surfaces of the inner and outer rings 20 and 22. Built between 20r and 22r. Thereby, each rolling element (ball) 24 can roll between the raceway surfaces 20r and 22r, without the rolling surfaces contacting each other. As a result, it is possible to prevent an increase in rotational resistance or seizure due to the rolling elements (balls) 24 coming into contact with each other to generate friction.

  In this case, each rolling element (ball) 24 has a contact angle set to a predetermined size (for example, about 15 ° to 40 °) and is incorporated between the raceway surfaces 20r and 22r. Here, the contact angle is a line of action (not shown) connecting two points where the rolling elements (balls) 24 are in contact with the inner and outer rings 20 and 22 (the raceway surfaces 20r and 22r), respectively. A predetermined angle formed between a plane (radial plane) perpendicular to an axis (not shown).

  Here, in the angular ball bearings 2 and 4, the number of rolling elements (balls) 24 incorporated between the raceway surfaces 20 r and 22 r of the inner and outer rings 20 and 22 depends on, for example, the size of the bearings 2 and 4. Since it is arbitrarily set, there is no particular limitation here. As an example, in the configuration shown in FIG. 2B, eleven rolling elements (balls) 24 are incorporated between the raceway surfaces 20r and 22r of the inner and outer rings 20 and 22.

  Further, the angular ball bearings 2 and 4 have a main body portion 26m in which either one side (the right side in FIG. 2A) forms a tapered cylindrical shape having a smaller diameter than the other side (the left side in the figure). A retainer 26 that rotatably holds rolling elements (balls) 24 one by one is provided in a plurality of pockets 26p formed at predetermined intervals along the tapered circumferential surface of the main body portion 26m. The vessel 26 is incorporated in the inner and outer rings 2 and 4 with each rolling element (ball) 24 held in the pocket 26p one by one.

  2 (a) and 3 (a) to (c), for example, the cage 26 has an axial width (a distance in the left-right direction in FIG. 4 (inner and outer rings 20, 22) is set to a predetermined dimension smaller than the axial width (distance in the same direction in the figure), and the same number of rolling elements (balls) 24 (same as the same) on the taper circumferential surface. In the configuration shown in the figure, 11 pockets 26p are formed at equal intervals. In this case, the cage 26 is configured as a machined type cage in which the pocket 26p is formed by cutting a tapered circumferential surface.

Further, in the configuration shown in FIG. 2 (a), as an example, the retainer 26 has a rolling element (ball) in which the inner peripheral surface 26a and the outer peripheral surface 26b of the main body portion 26m do not contact the inner and outer rings 20, 22. It is configured as a rolling element guide type that is rotationally guided only by 24. However, the guide method of the cage 26 is not limited to this, and for example, an inner ring guide type in which the inner peripheral surface 26a of the main body portion 26m is in contact with the groove shoulder of the inner ring 20 (shoulder portion of the raceway surface 20r) to guide rotation. Alternatively, an outer ring guide type in which the outer peripheral surface 26b of the main body portion 26m is brought into contact with the groove shoulder of the outer ring 22 (shoulder portion of the raceway surface 22r) for rotation guidance may be used.
In any case, the cage 26 can rotate between the inner and outer rings 20 and 22 together with the rolling elements (balls) 24 with each rolling element (ball) 24 held in the pocket 24p one by one. it can.

  In the present embodiment, the cage 26 is formed using a porous sintered material as its material, and has predetermined (many) pores on the surface and inside thereof. In this case, the specific material used for manufacturing the cage 26 is not particularly limited. For example, the strength and heat resistance of the cage 26 set by the usage form of the bearings 2 and 4 and the manufacturing conditions are set. Any material may be applied according to requirements such as corrosion resistance. For example, as the material of the cage 26, various synthetic resins, ceramics, metals, and the like that can form predetermined (many) pores on and inside the produced cage 26 are appropriately selected and applied. Can do.

  Then, these materials (porous materials) are molded by, for example, heating and pressing, and the molded body subjected to heat sintering is processed into a predetermined shape, thereby forming a cage (porous cage) 26. can do. In the configuration shown in FIGS. 2A and 3A to 3C, a so-called machined type is used as the retainer 26 as an example. For example, various types such as a punching die, a crown shape, a wave shape, and a mating die can be applied depending on the type of rolling element.

  Further, as shown in FIG. 1, the retainer 26 is positioned so that a part of the retainer 26 (portion located on the oil bath 54 side with respect to the impeller shaft S in the figure) can always come into contact with the lubricating oil 52. It has been. In other words, the angular ball bearings 2 and 4 in which the cage 26 is incorporated between the inner and outer rings 20 and 22 are lubricated so that a part (same as above) of the cage 26 is always stored in the oil bath 54. The oil 52 is externally fitted to the impeller shaft S so as to be located below the liquid level 52s of the oil 52, that is, to be in a state of being submerged in the lubricating oil 52.

  As a result, the cage 26 rotates together with the inner rings 20 of the angular ball bearings 2 and 4, and at the time of rotation, a part of the cage 26 always sinks into the lubricating oil 52 stored in the oil bath 54. Contact with. In the present embodiment, since the retainer 26 has predetermined (many) pores on the surface and inside thereof, the retainer 26 sinks into the lubricating oil 52 and contacts the lubricating oil 52 when the lubricating oil 52 is in contact therewith. Flows into the pores from the oil bath 54 and flows out from the pores to the oil bath 54. Then, in accordance with the rotation of the cage 26, such inflow and outflow of the lubricating oil 52 into and out of the pores are repeated. Therefore, the lubricating oil 52 stored in the oil bath 54 can always be circulated during the rotation of the cage 26, that is, during the rotation of the angular ball bearings 2, 4 (inner ring 20).

  As a result, the lubricating oil 52 that has flowed into the pores does not remain for a long period of time, and heat exchange between the lubricating oil 52 in the pores and the lubricating oil 52 in the oil bath 54 can be promoted. The temperature rise of 52 can be effectively suppressed. As a result, the angular ball bearings 2 and 4 can be effectively cooled, the angular ball bearings 2 and 4 can be rotated with high accuracy over a long period of time, and the process pump can be stably maintained over a long period of time. Can continue driving.

  In addition, how many pores are provided in the cage 26, that is, how much the porosity (porosity content) is set depends on, for example, the amount and type of lubricating oil, lubrication requirements, and the like. Therefore, there is no particular limitation here. For example, FIGS. 3A to 3C show three cages (a punched-type porous cage) 26 according to the present embodiment, respectively. In FIG. 3 (a), the porosity (α) is set to a predetermined value larger than 50% (α> 50%), and in FIG. 3 (b), the porosity (α) is set to 50%. (C = 50%), the porosity (α) is set to a predetermined value larger than 0% and smaller than 50% (0% <α <50%). Each configuration is shown as an example.

  Here, in the cage 26, the amount of the lubricating oil 52 that flows into and out of the pores varies with the set porosity (α), and if the porosity (α) is set large, it flows into and out of the pores. The amount of lubricating oil 52 to be discharged also increases. In addition, when the lubricating oil 52 flows out from the pores of the cage 26, the lubricating oil 52 is subjected to a centrifugal force generated with the rotation of the cage 26, and the lubricating oil 52 is caused to contact the angular ball bearing 2. , 4 are scattered in the outward direction (upward and downward directions in FIG. 1A).

  In this case, the scattering amount increases as the porosity (α) of the cage 26 increases, and the flow amount of the lubricating oil 52 in the oil chamber L increases. That is, the fluidity of the lubricating oil 52 in the oil chamber L can be activated and promoted. As a result, the lubricating oil 52 is positively brought into contact with the inside air 58 and the inner surface 60 of the oil chamber L, whereby heat exchange between them can be promoted, and the temperature rise of the lubricating oil 52 is effectively suppressed. be able to.

  In the configuration shown in FIGS. 1 (a) and 2 (a), the angular ball bearings 2, 4 include sealing members (contact type seals, non-contact type seals, shields, etc.) for sealing the inside of the bearings. ) Is not provided. For this reason, the lubricating oil 52 can be easily flowed into and out of the pores of the cage 26 and the lubricating oil 52 can be easily scattered into the oil chamber L. As a result, the amount of the lubricating oil 52 in contact with the inside air 58 and the inner surface 60 of the oil chamber L can be increased, and heat exchange between the lubricating oil 52 and the inside air 58 and the inner surface 60 of the oil chamber L can be further promoted. Can do.

  In this way, by adjusting the porosity (α) of the cage 26, the flow rate of the lubricating oil 52 per rotation speed of the cage 26 can be optimally maintained with the effect of suppressing the temperature rise due to heat exchange. The predetermined amount can be adjusted. That is, by adjusting the porosity (α) of the cage 26, the cooling amount of the lubricating oil 52 per unit time can be easily adjusted. In another way, the difference between the temperature of the lubricating oil 52 stored in the oil bath 54 and the temperature of the angular ball bearings 2 and 4 is adjusted by adjusting the porosity (α) of the cage 26. Can be small.

As a result, deterioration of the lubricating performance of the lubricating oil 52 can be effectively prevented, and the angular ball bearings 2 and 4 do not become poorly lubricated or insufficiently lubricated, and the lubricating state can be maintained well. .
The temperature of the oil bath 54 itself may be adjusted by applying a conventional method (for example, air cooling or water cooling). In this case, since the temperature rise of the angular ball bearings 2 and 4 is suppressed and the heat generation thereof is also suppressed, the temperature of the oil bath 54 itself can be easily adjusted.

  In the present embodiment described above, the cage (porous retainer) 26 is incorporated in both of the two angular ball bearings 2 and 4, but either one of the bearings (the angular ball bearing on the right side in FIG. 1). The cage (porous cage) 26 may be incorporated only in the 2 or left angular ball bearing 4).

For example, such a cage (porous retainer) 26 is incorporated only in the left angular ball bearing 4 in FIG. 1, and the right angular ball bearing 2 in FIG. 1 is not made of a porous sintered material. A cage that is formed using (for example, bearing steel) and does not have predetermined pores on the surface and inside thereof may be incorporated. In this case, the cage incorporated in the angular ball bearing 2 (right bearing in FIG. 1) is more than the cage (porous retainer) 26 incorporated in the angular ball bearing 4 (left bearing in FIG. 1). The strength can be easily increased, and as a result, the strength of the bearings 2 and 4 itself can be increased as compared with the case where the cage (porous cage) 26 is incorporated in both the bearings 2 and 4. Can do.
Thereby, even when an axial load is applied to the two angular ball bearings 2 and 4 by the impeller 50 attached to the impeller shaft S, the axial load can be more reliably applied.

  Further, in the present embodiment described above, the cage (porous retainer) 26 set to the same porosity is incorporated for both of the two angular ball bearings 2 and 4, but different porosity is set. A cage 26 may be incorporated for each of the bearings 2 and 4. In this case, the retainer 26 sets the porosity to a predetermined value so as to have a predetermined strength required at that time according to the magnitude of the axial load applied to the bearings 2 and 4, for example. What is necessary is just to set and form.

  In addition, in the two angular ball bearings 2 and 4, as described above, when a cage having a different configuration is incorporated (when a cage made of a different material or a cage having a different porosity) is incorporated, an oil bath It is preferable to incorporate a retainer (porous retainer) 26 or a retainer 26 having a higher porosity with respect to the bearing located on the side 52 (in FIG. 1, the angular ball bearing 4 located on the left side). . As a result, the axial load acting on the two angular ball bearings 2 and 4 can be more reliably applied, and the heat exchange promoting effect of the lubricating oil 52 included in the cage (porous cage) 26, and Accordingly, the effect of suppressing the temperature rise of the lubricating oil 52 (the cooling effect of the lubricating oil 52) can be reliably and effectively exhibited.

  In the above-described embodiment, the cage (porous cage) 26 is incorporated into the two angular ball bearings 2 and 4, but in addition to or instead of this, the deep groove ball bearing 6 On the other hand, a similar cage (porous cage) 26 may be incorporated. In the above-described embodiment, the bearing configuration of the deep groove ball bearing 6 is not particularly mentioned. However, the deep groove ball bearing 6 has a pair of bearing rings (an inner ring and an outer ring) arranged so as to be relatively rotatable. And a plurality of rolling elements (balls) that are rotatably incorporated between the races, and a cage that rotatably holds the rolling elements (balls) one by one.

  Furthermore, in the above-described embodiment, the impeller shaft S is rotatably supported by the two angular ball bearings 2 and 4 and the one deep groove ball bearing 6, but the rolling bearing that rotatably supports the impeller shaft S is: It is not limited to these bearings and combinations. For example, all of the rolling bearings that rotatably support the impeller shaft S may be angular ball bearings, or all may be deep groove ball bearings. Further, as rolling bearings that rotatably support the impeller shaft S, for example, double row angular ball bearings, double row deep groove ball bearings, and various rollers as rolling elements (cylindrical rollers, tapered rollers, spherical rollers, etc.) Single-row and double-row roller bearings in which are used may be applied.

Sectional drawing which shows the structural example of the pump apparatus which concerns on one Embodiment of this invention. It is a figure which shows the structural example of the rolling bearing for supporting the impeller shaft of the pump apparatus which concerns on one Embodiment of this invention rotatably, Comprising: (a) is sectional drawing, (b) is the figure (a) The top view seen from the arrow A direction of). FIG. 2 is a diagram showing an example of the overall configuration of a rolling bearing cage formed using a porous sintered material according to an embodiment of the present invention and having a predetermined porosity (α), where (a) A perspective view showing a cage set to> 50%, (b) is a perspective view showing a cage set to α = 50%, and (c) is a hold set to 0 <α <50%. The perspective view which shows a container.

Explanation of symbols

2,4 Rolling bearing (angular ball bearing)
6 Rolling bearings (deep groove ball bearings)
20, 22 raceway ring 24 rolling element (ball)
26 Cage 50 Impeller 52 Lubricating Oil 54 Oil Bath S Impeller Shaft

Claims (1)

An impeller shaft that extends in a predetermined direction and has an impeller attached to the extending end thereof, a plurality of rolling bearings that rotatably support the impeller shaft, and an oil that stores lubricating oil for lubricating the rolling bearing A pump device comprising a bath,
In at least one rolling bearing, a cage that rotatably holds a rolling element and that is rotatably incorporated between races is formed by using a porous sintered material as a material, and has a surface and an inside thereof. While having predetermined pores, a part thereof is always positioned so as to be able to come into contact with the lubricating oil, and as the retainer rotates, the lubricating oil flows into the pores from the oil bath, and the pores The pump device is characterized in that the rolling bearing is cooled by flowing out from the oil bath into the oil bath and circulating, thereby promoting heat exchange between the lubricating oil in the pores and the lubricating oil in the oil bath.

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