JPH1130196A - Pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve wear resistance by communicating a first area of a sliding face of a sliding bearing for supporting a shaft body rotatably, with a high pressure part where pressure becomes high in fluid passage constitution, while communicating a second area with a low pressure part, and feeding liquid to the sliding face of the sliding bearing by differential pressure. SOLUTION: Driving force is transmitted to a shaft body 6 through a belt and a pulley 14 and an impeller 8 in a pumping chamber 7 is rotated. Then liquid is sucked into the pumping chamber 7 from a first passage of a mating member 20 and discharged to a second passage through a spiral passage 103. At this time, pressure becomes high at a minimum width part 103a of the spiral passage 103 communicated with an inlet hole 12 provided at a housing 2, and pressure becomes low in a wide part 102 from an outlet of the spiral passage 103 communicated with an outlet hole 13. The liquid flowing into an outer peripheral fit-in part of a sliding bearing 4 from the inlet hole 12 due to this differential pressure is fed to the sliding faces of a resin liner part 42 and the shaft body 6 from a peripheral recessed part 46 of a metal ring 41 of the sliding bearing 4 through an end face part 45 of the metal ring 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump used for, for example, a water pump used for cooling an automobile engine.

[0002]

2. Description of the Related Art As a conventional pump of this type, for example, a pump as shown in FIG. 13 is known. That is,
A shaft 103 is rotatably supported on the inner periphery of a shaft hole 101 of a housing 100 via a bearing 102, and an impeller 105 inserted into a pump chamber 104 is connected to one end of the shaft 103. A rolling bearing was used as the bearing 102.

[0003]

However, in recent years, there has been a demand for lighter and smaller pumps, and other components such as the housing 100 have been made lighter with resin or the like. However, since there are rolling bearings, There was a limit to weight reduction.

[0004] Therefore, in order to further reduce the weight, the use of a sliding bearing instead of a rolling bearing has been studied. However, in the case of a plain bearing, there is a problem that durability is poor because the sliding surface is worn.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems of the prior art. It is an object of the present invention to use a sliding bearing for a pump and supply the liquid in the pump chamber to the sliding surface. To provide a pump that can improve wear resistance.

[0006]

In order to achieve the above object, according to the present invention, a shaft is rotatably supported on the inner periphery of a shaft hole of a housing via a bearing, and a pump is provided at one end of the shaft. In a pump, which is inserted into a chamber and connected to a transport member that transports a liquid by applying mechanical energy to the liquid, the bearing is a slide bearing, and a first region of a sliding surface of the slide bearing is formed on a liquid flow path configuration. The second region communicates with a high-pressure portion that becomes high in pressure, and the second region communicates with a low-pressure portion that becomes lower in pressure than the high-pressure portion in the flow path configuration. The liquid is supplied to the surface to enable lubrication.

In the present invention, the driving force is transmitted to the shaft body, and the transport member such as the impeller in the pump chamber rotates to flow the liquid through the flow path. The liquid is supplied to the sliding surface of the sliding bearing by the pressure difference between the high-pressure part and the low-pressure part in the flow path, and the sliding surface is lubricated. As described above, the sliding surface of the sliding bearing is lubricated by the liquid, so that the sliding surface can be prevented from being worn, the durability can be improved, and the frictional heat generated on the sliding surface due to the liquid can be cooled. .

In addition, an inlet hole and an outlet hole are provided in the housing for connecting the slide bearing outer peripheral fitting portion and the pump chamber, and the inlet hole is in a high pressure portion of the pump chamber flow passage and the outlet hole is in a low pressure portion of the pump chamber flow passage. The sliding surface of the sliding bearing communicates with one end of the sliding surface in the axial direction as the first region and the inlet hole, and the other end of the sliding surface of the sliding bearing in the second region as the second region. And the outlet hole, and the liquid is supplied to the sliding surface of the slide bearing by a pressure difference between the inlet hole and the outlet hole.

According to this structure, the liquid flows into the sliding bearing outer peripheral fitting portion from the inlet hole provided in the housing communicating with the high pressure portion side in the pump chamber. The inflowing liquid is supplied to the sliding surface between the slide bearing and the shaft body from one end in the axial direction, flows out from the other end side, lubricates the sliding surface between the slide bearing and the shaft body, and flows out of the liquid. Flows out from the outlet hole provided in the housing to the low pressure side in the pump chamber. Since the inlet hole and the outlet hole are provided in the housing itself, no special piping is required, and the size of the pump can be reduced.

[0010] Further, a liquid suction port or a discharge port is provided on the side opposite to the pump chamber with a slide bearing of the housing therebetween, and a communication hole for communicating the suction port or the discharge port with the pump chamber is provided in the slide bearing. With a configuration that transports the liquid through the communication hole by rotation of the indoor transport member,
It is also preferable that liquid is supplied to the sliding surface of the slide bearing by a differential pressure generated on both sides of the communication hole.

According to this configuration, when the suction port is provided on the side opposite to the pump chamber with the sliding bearing of the housing interposed therebetween,
Liquid is sucked into the pump chamber through the communication hole. In this case, the high pressure section is located on the side opposite to the pump chamber and the low pressure section is located on the pump chamber side of the communication hole, and the liquid is supplied to the sliding surface of the slide bearing by the differential pressure.

On the other hand, when there is a discharge port on the side opposite to the pump chamber, the liquid is transported from the pump chamber into the housing through the communication hole and discharged from the discharge port. In this case, the pump chamber side of the communication hole serves as a high-pressure section, and the counter-chamber side serves as a low-pressure section. The liquid is supplied to the sliding surface of the slide bearing by the differential pressure.

As described above, the flow conveyed by the pump passes through the communication hole of the sliding bearing, and the liquid is supplied to the sliding surface of the sliding bearing by the differential pressure before and after the passage, so that the lubricating effect is high.

[0014] It is also preferable that the shaft has a communication hole communicating from an end on the pump chamber inner side to one axial end of a sliding surface of the slide bearing.

According to this, the communication hole formed in the shaft body can supply the liquid from the pump chamber to the sliding surface of the slide bearing and discharge the liquid from the sliding surface of the slide bearing to the pump chamber. In addition, the centrifugal force generated by the rotation of the shaft can be used as a liquid transporting action.

An inlet hole and an outlet hole are provided in the housing for connecting the outer periphery fitting portion of the slide bearing and the pump chamber, and the inlet hole is opened to a high pressure portion of the flow passage in the pump chamber and the outlet hole is opened to a low pressure portion of the flow passage in the pump chamber. A first communication hole communicating with the slide bearing a first region of the slide surface of the slide bearing and the inlet hole; and a circumferentially separated from the first region of the slide surface of the slide bearing. It is also preferable to provide a second communication hole communicating the second region with the outlet hole.

According to this, the sliding area of the sliding bearing can be lubricated by passing the first area and the second area, which are circumferentially separated from each other in the circumferential direction, by the pressure difference of the supplied liquid. And

Further, by providing a groove for drawing the liquid into the sliding surface on the sliding surface of the sliding bearing, the lubricating effect can be enhanced.

Two bearings are provided apart from each other in the axial direction, the bearing on the pump chamber side is a sliding bearing, the bearing on the opposite side of the pump chamber is a rolling bearing, and a shaft hole of the housing is provided between the sliding bearing and the rolling bearing. It is also preferable to provide a sealing member for sealing between the shaft member and the shaft member.

In this case, the liquid supplied from the pump chamber through the inlet hole lubricates the sliding surface between the slide bearing and the shaft, and is discharged from the outlet hole of the housing to the low pressure side of the pump chamber. The liquid that has flowed out of the sliding surface of the slide bearing toward the pump chamber side is sealed by the seal member and does not reach the rolling bearing portion.

Also, two slide bearings are provided in the axial direction so as to be spaced apart from each other. One end of the slide surface of one slide bearing in the axial direction communicates with the inlet hole, and the other slide bearing has a slide surface. It is also preferable that the other end in the axial direction communicates with the outlet hole.

In this case, since the liquid flows in the space between the two slide bearings on the inner circumference of the housing, the housing can be cooled.

Further, the inner peripheral portion of the shaft hole of the housing and the outer cylindrical portion of the slide bearing held by the inner peripheral portion of the housing have a spherical shape. It is also preferable to hold it swingably.

According to this, the entire sliding bearing can be inclined in the axial direction with respect to the inclination of the shaft body, and the axial direction can be made the same, so that the surface pressure of the sliding surface of the sliding bearing can be made uniform and the sliding surface can be made uniform. Wear is reduced.

Further, the sliding surface of the slide bearing includes a contact sliding portion that comes into contact with the surface of the shaft and a non-contact sliding portion that is separated from the surface of the shaft. Are also suitable.

Thus, the amount of liquid supplied to the sliding surface of the plain bearing can be increased, and the cooling effect and the lubrication effect can be improved.

[0027]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below based on the illustrated embodiment.

[Embodiment 1] FIGS. 1 and 2 illustrate a case where a pump according to Embodiment 1 of the present invention is applied to a water pump for cooling an engine.

In the water pump 1, a shaft body 6 is rotatably supported on the inner periphery of a shaft hole 3 of a housing 2 via a sliding bearing 4 and a rolling bearing 5 provided apart from each other in the axial direction. An impeller 8 as a transport member such as an impeller inserted into the pump chamber 7 is connected to one end of the shaft 6. The rotation of the impeller 8 imparts mechanical rotational energy to the liquid to transport the liquid.

The housing 2 is an integrally molded product of resin, and comprises a cylindrical portion 9 through which the shaft hole 3 is formed, and a flange-like lid portion 10 extending from a middle portion of the cylindrical portion 9. ing. The cylindrical portion 9 has a stepped shape including a large-diameter cylindrical portion 91 inserted into the pump chamber 7 and a small-diameter cylindrical portion 92 extending toward the opposite side of the pump chamber. The small-diameter cylindrical portion 92 is integrally provided at the boundary. The outer diameter of the small-diameter cylindrical portion 92 is tapered so that the diameter gradually decreases from the pump chamber 6 side to the opposite pump chamber side.

The lid 10 has a circular portion 101 and a wide portion 102.
The shaft hole 3 of the cylindrical portion 9 is slightly eccentric with the center of the circular portion 101, and one end in the radial direction has a minimum width between the outer diameter end of the impeller 8 and the inner circumference of the circular portion 101. A spiral flow path 10 whose width gradually widens so that the end has the maximum width.
3 are formed.

The lid 10 is fixed to a mating member 20 such as an engine block by a fixing tool such as a bolt. A concave portion 21 for the pump chamber is formed in the counterpart member 20, the concave portion 21 is closed by the lid portion 10, and the pump chamber 7 sealed by the concave portion 21 and the lid portion 10 is formed. The gasket 22 seals between the joining surfaces of the lid 10 and the mating member.

The sliding bearing 4 and the rolling bearing 5 are separated from each other in the axial direction. The sliding bearing 4 is provided on the pump chamber 7 side, and the rolling bearing 5 is provided on the opposite side of the pump chamber.
The housing 2 is disposed between the sliding bearing 4 and the rolling bearing 5.
A seal member 11 for sealing between the shaft hole 3 and the shaft body 6 is provided.

The sliding bearing 4 is fitted and fixed to the inner periphery of the large-diameter cylindrical portion 91 of the housing 2 provided in the pump chamber 7. An inlet hole 12 and an outlet hole 13 communicating with the inside of the chamber 7 are provided. The inlet hole 12 is open on the high pressure side where the pressure is high in the flow path configuration in the pump chamber 7, and the outlet hole 13 is open on the low pressure side where the pressure is low in the flow path configuration.

In the case of the pump using the impeller 8 as in the present embodiment, the flow velocity is high near the minimum width portion 103a of the spiral flow path 103 of the pump chamber 7, and the pressure is the highest.
The inlet hole 12 is opened in the minimum width portion 103 a of the spiral flow path 103, and the outlet hole 13 is opened in the wide portion 102.

A first end of the sliding surface of the sliding bearing 4 in the axial direction communicates with the inlet hole 12 and an axial direction of the sliding surface of the sliding bearing 4 as the second region The other end and the outlet hole 13 communicate with each other, and a liquid is supplied to the sliding surface of the slide bearing 4 by a pressure difference between the inlet hole 12 and the outlet hole 13.

As shown in FIG. 1 (c), the sliding bearing 4 has a metal ring 41 having a substantially U-shaped cross section which opens to the side opposite to the pump chamber.
And a resin liner portion 4 joined to the inner periphery of the metal ring 41.
And 2. The metal ring 41 has a U-shaped cross section opened to the side opposite to the pump chamber, and includes an outer cylindrical portion 43 and an inner cylindrical portion 44.
And an end surface portion 45 connecting the outer cylinder portion 43 and an end of the inner cylinder portion 44 on the pump chamber 7 side. The resin liner portion 42 is joined to the inner periphery of the inner cylinder portion 44. I have.

The material of the resin liner portion 42 is P
Various materials such as EEK, PPS, PSF, PEI, and phenol resin can be used. Among them, a phenol resin is preferable in consideration of wear resistance.

The outer cylindrical portion 43 of the metal ring 41 of the sliding bearing 4 is fitted to the inner periphery of the large-diameter cylindrical portion 91 of the housing 2 in a liquid-tight manner. Is provided with a concave portion 46. The recess 46 is formed in the outer cylinder 4
3 is open at the end on the pump chamber 6 side, and is closed at the end on the side opposite to the pump chamber. A notch 47 is provided in a portion corresponding to the outlet hole 13 of the outer cylindrical portion 43.
The communication between the side opposite to the pump chamber and the outlet hole 13 is communicated through 7.

Instead of the notch 47, a recess similar to the inlet hole 12 may be provided. However, it is necessary to open the recess on the side opposite to the pump chamber and close the pump chamber 7 side.
The size of the concave portion 46 is set from the minimum flow rate required for cooling and lubrication.

On the other hand, the 41 end surface portion 45 of the metal ring is substantially flush with the end surface of the large diameter cylindrical portion 91 on the pump chamber 7 side. The outer diameter of the impeller 8 is substantially equal to the outer diameter of the large-diameter cylindrical portion 91, and the impeller 8, the end faces of the large-diameter cylindrical portion 91 and the metal ring 4.
The first end surfaces 45 face each other with a predetermined gap g therebetween.

In this embodiment, the sliding bearing 4 is constituted by two members of the metal ring 41 and the resin liner portion 42. However, the sliding bearing 4 may be constituted by only one member of resin. As in the present embodiment, if the liquid ring is constituted by the two members of the metal ring 41 and the resin liner portion 42 and the concave portion 46 and the cutout portion 47 are provided in the metal ring 41 to form a flow path for the lubricating liquid, Can be easily formed when the metal ring 41 is press-formed.

In this embodiment, after the metal ring 41 is press-formed in a form having the concave portion 46 and the notch portion 47, the resin liner portion 42 is insert-molded by insert molding.

The material of the sliding bearing 4 is not limited to resin, but may be metal, ceramic, or the like.

On the other hand, the rolling bearing 5 is interposed between the opening end of the small-diameter cylindrical portion 91 of the cylindrical portion 9 on the side opposite to the pump chamber and the middle of the shaft 6. A pulley 14 constituting a winding drive mechanism is fixed to an end of the small-diameter cylindrical portion 91 that protrudes further from the pump chamber side to the pump chamber side, and a belt (not shown) is fixed to the pulley 14. Power is transmitted by being wound around.

The radial load acting on the shaft 6 via the belt is mainly supported by the rolling bearing 5, and no excessive radial load due to the belt tension acts on the sliding bearing 4. In particular, in the illustrated example, the rolling bearing 5 is located immediately below the pulling position of the pulley 14 around the belt. By doing so, the radial load acting on the slide bearing 4 becomes about the weight of the shaft body 5 and almost no radial load acts.

As the winding drive mechanism, not only the pulley 14 and the belt, but also a combination of a sprocket and a chain may be used, and another power transmission mechanism may be used.

In this embodiment, the driving force is transmitted to the shaft body 6 via the belt and the pulley 14, and the shaft body 6 rotates.
The impeller 8 in the pump chamber 7 rotates with the rotation of the shaft body 6, and the liquid flows from the first flow path 23 of the mating member 20 to the pump chamber 6.
The vortex is drawn through the spiral flow path 103 and is discharged to the second flow path 24.

The minimum width portion 103a of the spiral flow passage 103 provided in the housing 2 and communicating with the inlet hole 12 has a high pressure, and has a low pressure in the wide portion 102 from the outlet of the spiral flow passage 103 communicating with the outlet hole 13. .

Due to the pressure difference, the liquid flows from the inlet hole 12 into the outer peripheral fitting portion of the sliding bearing 4, and the inflowing liquid flows from the concave portion 46 on the outer periphery of the metal ring 41 of the sliding bearing 4 through the end surface portion 45 of the metal ring 4. It is supplied to the sliding surface between the resin liner portion 42 and the shaft body 6.

A part of the supplied liquid moves to the low-pressure wide part 102 side through the gap g between the end face part 45 and the impeller 8, and a part of the liquid flows out to the axially opposite pump chamber side while lubricating the sliding surface. Then, the outflowing liquid flows out of the outlet hole 13 to the low-pressure side in the pump chamber 7 through the cutout portion 47 provided in the outer cylindrical portion 43 of the metal ring 4.

As described above, the sliding surface of the sliding bearing 4 is lubricated by the liquid, so that the abrasion of the sliding surface is prevented, and the durability can be improved.

Further, the frictional heat generated on the sliding surface between the resin liner portion 42 and the shaft 7 by the liquid can be cooled.

Further, since the housing 2 itself is provided with the inlet hole 12 and the outlet hole 13, no special piping is required.
The size of the pump can be reduced.

It is preferable that a groove is provided in the sliding surface of the sliding bearing 4 so that a liquid is drawn into the sliding surface between the sliding bearing 4 and the shaft 6 by the rotation of the shaft 7. By doing so, the lubrication effect can be enhanced.

The liquid flowing out of the sliding surface of the sliding bearing 4 toward the pump chamber is sealed by the seal member 11 and does not reach the rolling bearing 5. The groove may be a groove extending linearly in the axial direction, or a spiral groove having a screw pump function may be provided.

As described above, since the liquid reaches the seal member 11 via the slide bearing 4, the pressure is reduced by the slide bearing 4, and the seal member 4 is not limited to a high-pressure seal, but a lip-type seal is used. Can be
Liquid leakage can be completely sealed. Conversely, the sliding bearing 4 can reduce the pressure to a pressure that can be sealed by the lip seal.

However, the seal member 11 is not limited to a lip-type seal, and a mechanical seal may be used, and other various seal members may be applied.

In the present embodiment, the liquid is caused to flow from the pump chamber side to the non-pump chamber side on the sliding surface of the slide bearing 4 with the shaft 6, but the impeller 8 and the spiral flow The fluid may flow from the pump chamber side to the pump chamber side according to the shape and characteristics of the passage 103. In this case, since there is no depressurizing effect of the seal member, it is effective to use a pressure-resistant seal as the seal member.

[Second Embodiment] FIG. 2 shows a pump according to a second embodiment of the present invention.

Although the second embodiment also uses two bearings, unlike the first embodiment, both the bearings on the pump chamber side and the opposite side of the pump chamber are sliding bearings.

That is, one end of the sliding surface of one first sliding bearing 104 in the axial direction communicates with the inlet hole 12, and the other end of the sliding surface of the second sliding bearing 105 communicates with the other end of the sliding surface in the axial direction. The holes 13 communicate with each other.

As a result, the liquid is supplied from the inlet hole 12 of the housing 2 through the sliding surface of the first sliding bearing 104 on the pump chamber 7 side to the sliding surface of the second sliding bearing 105 on the opposite side of the pump chamber, and The liquid lubricated on the sliding surface of the second sliding bearing 105 on the chamber side is discharged to the low pressure side of the pump chamber 7 through the outlet hole 13 of the housing 2.

Then, the second sliding bearing 1 on the side opposite to the pump chamber side
Further, a seal member 11 that seals between the small-diameter cylindrical portion 92 of the housing 3 and the shaft body 6 is provided on the opposite side of the pump chamber 05 from the pump chamber side.

The structure of the first and second sliding bearings 104 and 105 is basically the same as that of the first embodiment shown in FIG. Ring 41
And a resin liner portion 42 integrally joined to the inner periphery of the metal ring 41. The outer cylindrical portion 43 of the metal ring 41 of the first plain bearing 104 corresponds to the inlet hole 12. Only a concave portion 46 is provided, and a cutout portion corresponding to the outlet hole 13 is not provided.

The outer periphery of the outer cylindrical portion 43 of the metal ring 41 of the second plain bearing 105 does not require any concave portion or notch.

The small-diameter cylindrical portion 92 of the housing 2 is provided with a second outlet hole 16 that opens between the second plain bearing 105 and the seal member 11. A circulation path 17 communicating between the second outlet hole 16 and the outlet hole 13 provided in the large-diameter cylindrical portion 91 on the pump chamber 7 side.
Is provided.

In the case of the second embodiment, since the liquid flows through the space between the two sliding bearings 104 and 204 on the inner periphery of the housing 2, the housing 2 is cooled by the liquid introduced from the pump chamber 7. Can be.

The first and second sliding bearings 104, 10
5 is positioned so as to abut against both side steps of the large diameter portion 61 provided in the middle of the shaft body 6, and is partially so that the sliding surface is opened at the step of the large diameter portion 61. Are provided with a plurality of notched grooves 62.

By separating the inlet hole 12 and the outlet hole 13 and communicating the outlet hole 13 with the high-pressure side and the inlet hole 12 with the low-pressure side, one of the sliding bearings is moved from the second sliding bearing 105 to the other sliding bearing. First sliding bearing 10 as bearing
It may be configured to flow to the four sides.

Since other structures and operations are completely the same as those of the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.

[Third Embodiment] FIG. 3 shows a pump according to a third embodiment of the present invention.

This pump 301 is also a water pump for cooling the engine similarly to the first embodiment, and
A shaft body 306 is rotatably supported on the inner periphery of the second shaft hole 303 via a slide bearing 304 and a rolling bearing 305 provided apart from each other in the axial direction. And an impeller 308 as a transport member such as an impeller to be inserted into the vehicle. The other end of the shaft body 306 has a pulley 3 as in the example of FIG.
14 is fixed.

The housing 302 is a resin integrally molded product.
A cylindrical portion 309 having a shaft hole 303 formed therethrough, and a flange-like lid portion 310 protruding from one end of the cylindrical portion 309.
And is composed of The outer peripheral shape of the cylindrical portion 309 is
It has a tapered shape such that the diameter gradually decreases from the pump chamber 306 side toward the non-pump chamber side.

The lid portion 310 has a circular portion 3101 and a wide portion 3
And the shaft hole 303 of the cylindrical portion 309 is circular portion 3
The center of the impeller 308 is slightly eccentric, and the width between the outer diameter end of the impeller 308 and the inner circumference of the circular portion 3101 gradually increases so that one end in the radial direction has a minimum width and the other end has a maximum width. A spiral flow path 3103 is formed.

The sliding bearing 304 and the rolling bearing 305 are separated from each other in the axial direction. The sliding bearing 304 is provided on the pump chamber 307 side, and the rolling bearing 30 is provided on the opposite side of the pump chamber.
5 are provided. A seal member 311 for sealing between the shaft hole 303 of the housing 302 and the shaft body 306 is provided between the slide bearing 304 and the rolling bearing 305.

In the case of this embodiment, the housing 3
A liquid suction port 323 is provided on the side opposite to the pump chamber, that is, between the sliding bearing 304 and the seal member 311 with the sliding bearing 304 of No. 02 therebetween. The sliding bearing 304 is provided with a communication hole 312 for communicating the suction port 323 and the pump chamber 307. The rotation of the impeller 308 in the pump chamber 307 causes the pump chamber 307 to enter the pump chamber 307 in the axial direction through the suction port 323 and the communication hole 312. It is configured to suck liquid. Therefore, the sliding bearing 30
The high-pressure portion H is on the side of the suction surface 323 on the sliding surface of No. 4 and the low-pressure portion L is on the side of the axial pump chamber 307.

The sucked liquid is transported by the rotation of the impeller 308 to the wide part 3102 while being pressed against the flow path wall of the spiral flow path 3103 by centrifugal force.
It flows out to the flow path 324 in the partner member 320 communicating with 102.

FIG. 4 shows an example of a piping system of a cooling system such as an engine to which the pump is applied.

In the present embodiment, the heat of the mating member 20 such as the engine block is absorbed through the cooling passage in the engine or the like, is transported to the radiator 203 through the return passage 201, and the radiator 203 cools the liquid. The liquid is supplied to the suction port 3 of the pump through the supply channel 204.
23. Therefore, the sliding surface of the slide bearing 304 is provided in the main flow path of the liquid.

In this regard, in the first and second embodiments, FIG.
As shown in (b), the present embodiment differs in that a supply passage 204 from a radiator 203 is connected to a counterpart member 20 such as an engine, and the counterpart member 20 is provided with a supply passage 204 communicating with the pump chamber 7. It is different from the form.

The inclination of the blades of the impeller 308 is opposite to that of the first and second embodiments. The counterpart member 20 has no suction port, and is provided with a discharge port 324 communicating with the wide portion.

The sliding bearing 304 faces the pump chamber 307 and is fitted and fixed to the inner periphery of the housing 302. The metal ring 341 has a substantially U-shaped cross section and opens to the side opposite to the pump chamber. Resin liner 342 joined to the circumference
And is composed of The metal ring 341 has a U-shaped cross section open to the pump chamber side, and has an outer cylindrical portion 343 and an inner cylindrical portion 34.
4 and an end face portion 345 connecting the outer cylinder portion 343 and the end of the inner cylinder portion 344 on the pump chamber 307 side, and a resin liner portion 342 is joined to the inner periphery of the inner cylinder portion 344. ing. In this embodiment, the end face 3
A plurality of communication holes 312 are provided in 45 in the circumferential direction.

The sliding bearing 304 may be made of only one resin, but the metal ring 341 and the resin liner 3
When the metal ring 341 is formed by two members, the structure of the flow path can be easily formed at the time of press forming the metal ring 341. In this embodiment, after the metal ring 341 is press-formed in a form having the communication hole 312, the resin liner portion 342 is insert-molded by insert molding.

In the case of this embodiment, the pump 301
Hole 3 of the sliding bearing 305
12 and the sliding bearing 30
The liquid is supplied to the sliding surface of No. 5 and the lubrication effect is high.

The direction of transport of the liquid is, for example,
By rotating 08 in reverse, liquid can be transported from the pump chamber side of the sliding bearing 305 to the pump chamber 307 side. In that case, the suction port 323 becomes a discharge port, and the discharge port 324 becomes a suction port.

In each of the above embodiments, the case where the present invention is applied to a water pump for circulating cooling water has been described. However, the transporting liquid is not limited to cooling water, and pumps for transporting various liquids such as various chemicals and oils are provided. Can be applied to Also, the case where an impeller is used as a transport member has been described as an example, but a type having a vane may be used. In short, the present invention can be applied to a pump that transports a fluid by rotation.

Embodiment 4 FIGS. 5A, 5B, and 5
(C) is a figure explaining a 4th embodiment. In this figure, the same components as those of the first embodiment shown in FIG. 1 are denoted by the same reference numerals. A characteristic configuration of this embodiment is that the outer cylindrical portion 43a of the metal ring 41a of the sliding bearing 4a and the inner peripheral surface of the large-diameter cylindrical portion 91 of the housing 2 are spherical. Part 9
It is configured to be able to swing by the spherical inner peripheral surface.

The swing in this case refers to a resin liner when the shaft 6 is tilted by a small angle α from the shaft of the housing 2 in relation to the rolling bearing 5 as shown in FIG. It is intended to equalize the bearing surface pressure on the part, and is fixed in a predetermined posture when supporting the rotating shaft body 6.

Therefore, it is not impossible for the sliding bearing 4 a to always hold the shaft 6 while vibrating in accordance with the eccentricity of the shaft 6, but it is rather impossible to maintain the coaxiality of the rolling bearing 5 and the sliding bearing 4. This is a configuration that can eliminate the deviation.

FIG. 5C is a partially sectional perspective view of the sliding bearing 4a. In the sliding bearing 4a, the configuration of the resin liner portion 42, the inner cylindrical portion 44, the end surface portion 45, and the concave portion 46
It is the same as the sliding bearing 4 of FIG. 1 and exhibits the same operation and effect.

[Embodiment 5] FIGS. 6 (a), 6 (b),
(C) is a figure explaining a 5th embodiment. In this figure, the same components as those of the first embodiment shown in FIG. 1 are denoted by the same reference numerals. A characteristic configuration of this embodiment is that the resin liner portion 42b joined to the inner cylinder portion 44 of the slide bearing 4b is not cylindrical,
It is an arc shape divided into approximately half, and the mounting direction with respect to the slide bearing 4b is set to the side capable of supporting the shaft body 6 (the lower side of the inner cylindrical portion 44 in the upright state of the device).

Accordingly, the inner peripheral surface of the resin liner portion 42b serves as a contact sliding portion 42c for supporting the shaft 6, and the region on the inner peripheral side of the inner cylinder portion 44 where the resin liner portion 42b does not exist is a non-contact sliding portion. 42d.

With this configuration, the liquid supplied from the inlet hole 12 is supplied to the contact sliding portion 4 of the resin liner portion 42b.
2c can be supplied in large quantities, cooling effect,
Improve the lubrication effect. Further, the arc-shaped resin liner portion 42b uses less material than the cylindrical one, and can contribute to cost reduction.

Although the opening angle of the arc-shaped resin liner portion 42b with respect to the cylindrical shape is approximately 180 degrees in this embodiment, it is 180 degrees or more (for example, 270 degrees) in order to restrict the movement of the shaft body 6. Alternatively, it is also possible to provide a pair of 90-degree ones up and down and make the left and right gaps non-contact sliding parts. In addition, although the resin liner portion itself has a cylindrical shape, it is also possible to use a resin liner having a configuration in which a groove serving as a non-contact sliding portion is formed in a part of the inner peripheral surface.

[Embodiment 6] FIGS. 7A, 7B and 7
(C) is a figure explaining a 6th embodiment. In this figure, the same components as those of the first embodiment shown in FIG. 1 are denoted by the same reference numerals. A characteristic configuration of this embodiment is that a resin liner portion 4 of a sliding bearing 4c is provided.
2e is formed so as to cover the inner cylindrical portion 44c of the metal ring 41c.

The resin liner portion 42e is integrated with the metal ring 41c by inserting the metal ring 41c formed by press working or the like when forming the resin.

The end surface 45c of the metal ring 41c is not flush with the end surface of the resin liner portion 42e on the pump chamber 7 side, and is located at a position moved toward the opposite pump chamber 7 side. And a gap larger than the gap g.
Then, the liquid from the inlet hole 12 is introduced into the space between the rear surface of the impeller 8 and the end surface 45c from between the outer cylindrical portion 43c and the sliding surface of the slide bearing 4c. Therefore, the metal ring 4
It is not necessary to provide the outer cylindrical portion 43c with a concave portion 46 (see FIG. 1) for guiding the liquid from the inlet hole 12 to the inside of the outer cylindrical portion 43c (although there is no problem even if the concave portion 46 is provided). Manufacturability during insert molding can be improved.

[Seventh Embodiment] FIG. 8 is a diagram for explaining a seventh embodiment. In this figure, the same components as those of the first embodiment shown in FIG. 1 are denoted by the same reference numerals. A characteristic configuration of this embodiment is that the shaft body 6a and the impeller 8a are integrally molded with a resin material.

The end of the shaft body 6a on the side opposite to the pump chamber 7 is a mounting portion 6b of the rolling bearing 5 having a small diameter for fixing the rolling bearing 5, and the mounting portion 6b is provided with the rolling bearing 5 and the sleeve. The shaft 6a is fixed by inserting the 6c and tightening a bolt 6f via a washer 6e to a stud 6d fitted into the shaft 6a.

In this embodiment, the sliding bearing 4 has a sliding surface formed of a resin liner. However, since the shaft body 6a is made of a resin material, the sliding bearing 4 is not provided with a resin liner and is made of metal. It is also possible to make the inner cylinder part of the ring directly contact and slide with the shaft body 6a.

With such a configuration, the number of parts can be reduced, and the assemblability can be improved. Also, the fixing method of the shaft body 6a is not press-fitting,
Since the bolts are fastened, if the shaft body 6a and the impeller 8a become defective or worn out due to long-term use, the bolts 6f can be easily replaced by loosening the bolts 6f, thereby improving the maintainability.

[Eighth Embodiment] FIGS. 9A and 9B show
It is a figure explaining an 8th embodiment. In this figure, the same components as those of the sixth embodiment shown in FIG. 7 are denoted by the same reference numerals. A characteristic configuration of this embodiment is that a deep hole 6h extends from an end of the shaft body 6g on the pump chamber 7 side to the opposite side of the pump chamber 7, and the sliding bearing 4c and the seal member 11 of the deep hole 6h are formed. A radial hole 6i that opens outward in the radial direction is provided at a position facing the gap G1 therebetween. In addition, the inlet hole 12 of the large-diameter cylindrical portion 91 and the cutout portion 47 of the outer cylindrical portion 43c of the metal ring 41 are not formed.

According to this configuration, the deep hole 6h and the radial hole 6
By i, the gap G1 between the pump chamber 7 side and the slide bearing 4c on the side opposite to the pump chamber 7 communicates. And the shaft 6
When g rotates, the fluid is conveyed to the gap G1 by the centrifugal force generated in the radial hole 6i, and the sliding surface of the slide bearing 4c is directed from the side opposite to the pump chamber 7 toward the pump chamber 7 (leftward in the figure). The liquid is supplied and discharged from the gap g to the low pressure side of the pump chamber 7 through the outlet hole 13.

Although not shown in the drawing, the position of the radial hole 6i is set to a position facing the gap g, and the liquid is supplied from the pump chamber 7 side to the anti-pump chamber 7 side (rightward in the figure). Notch portion 47 (not shown) provided in cylindrical portion 43c
May be configured to be discharged through the outlet hole 13.

FIG. 10 shows a structure in which the water pump 1 according to the second embodiment shown in FIG.
k and a radial hole 6l. However, the second outlet hole 16 and the outlet hole 13 provided in the small-diameter cylindrical portion 92 of the housing 2 shown in FIG. 2 become unnecessary and are not provided.

As the shaft 6j rotates, the second sliding bearing 1
Liquid is supplied to a gap G2 between the first sliding bearing 105 and the sealing member 11, and the liquid flows from the sliding surface of the second sliding bearing 105 toward the sliding surface of the first sliding bearing 104, and the outlet hole 12a (see FIG. 2). Is returned from the inlet hole 12) to the pump chamber 7 side.

The liquid is supplied from the first sliding bearing 104 to the second sliding bearing 10 by setting the pressure on the outlet hole 12a side to the high pressure side.
5, and the high-pressure side and the low-pressure side may be set so as to be configured so as to be discharged to the radial direction hole 61 and the deep hole 6k.

FIG. 11 shows a shaft 6a in the configuration of the seventh embodiment shown in FIG. 8, which is provided with a deep hole 6m and a radial hole 6n. However, the exit hole 13 shown in FIG. 8 becomes unnecessary and is not provided.

Then, similarly to FIG. 9 and FIG.
When a rotates, the fluid is conveyed to the gap G3 by the centrifugal force generated in the radial hole 6n, and the sliding surface of the slide bearing 4 is directed from the side opposite to the pump chamber 7 toward the pump chamber 7 (leftward in the figure). The liquid is supplied, and the outlet hole 12b (see FIG.
Is discharged into the pump chamber 7 through the inlet hole 12).

As described above, it becomes possible to connect the sliding surface of the slide bearing to the high pressure side or the low pressure side of the pump flow path by using the deep hole and the radial hole formed in the shaft as communication holes. Since it can be supplied to the sliding surface and can replace the flow path formed in the housing, the processing can be simplified. In addition, the liquid discharged from the radial hole can increase the amount of liquid supplied to the sliding surface of the slide bearing due to the centrifugal force caused by the rotation of the shaft.

In particular, when the impeller and the shaft shown in FIG. 11 are integrally formed, deep holes and radial holes can be formed by molding at the time of resin molding, which contributes to improvement in productivity and cost reduction. Is big.

[Embodiment 9] FIGS. 12 (a), (b),
(C) is a diagram for explaining a ninth embodiment, FIG.
2 (a) is a cross-sectional configuration diagram of the water pump 1, and FIG.
2 (b) is a view of the water pump 1 viewed from the impeller 8 side in the axial direction, and FIG. 12 (C) is a view of S1 in FIG. 12 (b).
It is a partial cross-sectional perspective view of the sliding bearing 4d cut along the -S1 cross section. In this figure, the same components as those of the first embodiment shown in FIG. 1 are denoted by the same reference numerals.

Slide bearing 4d in this embodiment
Are provided with notches 4d1 and 4d2 which are V-shaped when viewed from the axial direction on the outer peripheral surface corresponding to the entrance hole 12 and the exit hole 13. Further, first and second communication holes 4d4 and 4d5 are provided to communicate from the slopes of the notches 4d1 and 4d2 to the sliding surface 4d3 of the slide bearing 4d. The area of the sliding surface 4d3 where the communication holes 4d4 and 4d5 are opened is:
In this embodiment, it is provided at a position approximately 180 degrees (angle) apart in the circumferential direction.

According to this configuration, when the impeller 8 rotates, the inlet hole 12 becomes the high pressure side due to the flow path structure, and the outlet hole 1
3 is on the relatively low pressure side. Then, the liquid is supplied from the inlet hole 12 to the sliding surface 4d3 of the slide bearing 4d through the communication hole 4d4, passes through the gap between the sliding surface 4d3 and the shaft 6, and passes through the opposite communication hole 4d4. It flows from the outlet hole 13 to the pump chamber 7 side.

Therefore, the sliding surface 4d3 of the sliding bearing 4d is lubricated, and the flow of the liquid traveling in the circumferential direction on the sliding surface 4d3 is generated due to the pressure difference between the inlet hole 12 and the outlet hole 13.
Effective cooling can be performed.

[0117]

As described above, according to the present invention, the liquid is supplied to the sliding surface of the sliding bearing by the pressure difference between the high pressure portion and the low pressure portion in the flow path, and the sliding surface is lubricated. You.

As described above, the sliding surface of the sliding bearing is lubricated by the liquid, so that the abrasion of the sliding surface is prevented, and the durability can be improved.

Further, the frictional heat generated on the sliding surface by the liquid can be cooled.

Further, if an inlet hole and an outlet hole are provided in the housing itself, no special piping is required and the size of the pump can be reduced.

If a groove for drawing liquid into the sliding surface is provided on the sliding surface of the sliding bearing, the lubricating effect can be enhanced.

The bearings are spaced apart from each other in the axial direction.
If the bearing on the pump chamber side is a sliding bearing, the bearing on the opposite pump chamber side is a rolling bearing, and a seal member is provided between the sliding bearing and the rolling bearing to seal between the shaft hole of the housing and the shaft body. The radial load acting on the shaft body is mainly supported by the rolling bearing, and no excessive radial load acts on the sliding bearing, so that the durability can be further improved due to the lubrication structure of the sliding bearing.

If two slide bearings are provided axially separated from each other, the liquid flows in the space between the two slide bearings on the inner periphery of the housing, and the housing can be cooled.

Furthermore, if a liquid suction port is provided on the side opposite to the pump chamber with the sliding bearing of the housing interposed therebetween, and the liquid is sucked into the pump chamber through a communication hole provided in the sliding bearing, the liquid transported by the pump can be removed. The liquid passes through the communication hole of the sliding bearing, and the liquid is supplied to the sliding surface of the sliding bearing by the pressure difference between before and after the passage, so that the lubrication effect is high.

With the sliding bearing held swingably,
The surface pressure of the sliding surface of the sliding bearing can be made uniform, and wear of the sliding surface is reduced.

By providing the sliding surface of the sliding bearing with a contact sliding portion and a non-contact sliding portion, the amount of liquid supplied to the sliding surface can be increased, and the cooling effect and the lubricating effect can be improved. .

The communication hole provided in the shaft body can be used as a flow path for supplying a liquid to the sliding surface of the slide bearing. At this time, the supply of liquid can be assisted by the centrifugal force applied to the communication hole of the rotating shaft, and the amount of liquid supplied to the sliding surface of the slide bearing can be increased.

Since the slide bearing is provided with a communication hole connected to a region of the slide surface circumferentially separated from the slide bearing in the circumferential direction, a flow of liquid traveling in the circumferential direction on the slide surface is generated, and effective lubrication is achieved. And cooling can be performed.

[Brief description of the drawings]

FIG. 1A is a sectional view showing a pump according to Embodiment 1 of the present invention, FIG. 1B is a plan view of the impeller side of FIG. 1A, and FIG. It is a partial section perspective view of a bearing.

FIG. 2 is a sectional view showing a pump according to a second embodiment of the present invention.

FIGS. 3A and 3B show a pump according to a third embodiment of the present invention. FIG. 3A is a cross-sectional view, and FIG. 3B is a plan view on an impeller side.

FIG. 4 (a) is a diagram showing an example of piping of the pump of FIG. 3,
FIG. 2B is a diagram showing an example of the piping in FIGS. 1 and 2.

5 (a) is a sectional view showing a pump according to Embodiment 4 of the present invention, FIG. 5 (b) is an enlarged view of the slide bearing of FIG. 5 (a), and FIG. 5 (c) is a slide It is a partial section perspective view of a bearing.

6A is a sectional view showing a pump according to Embodiment 5 of the present invention, FIG. 6B is a plan view of the impeller side of FIG. 6A, and FIG. It is a partial section perspective view of a bearing.

7A is a sectional view showing a pump according to Embodiment 6 of the present invention, FIG. 7B is a plan view of the impeller side of FIG. 7A, and FIG. It is a partial section perspective view of a bearing.

FIG. 8 is a sectional view showing a pump according to a seventh embodiment of the present invention.

FIG. 9A is a sectional view showing a pump according to an eighth embodiment of the present invention, and FIG. 9B is a plan view of the impeller side of FIG. 9A.

FIG. 10 is a sectional view showing a pump according to an eighth embodiment of the present invention.

FIG. 11 is a sectional view showing a pump according to an eighth embodiment of the present invention.

FIG. 12 is a sectional view showing a pump according to a ninth embodiment of the present invention.

FIG. 13 is a sectional view of a conventional pump.

[Explanation of symbols]

 1,301 Water pump 2,302 Housing 3,303 Shaft hole 4,304 Sliding bearing 104 First sliding bearing 204 Second sliding bearing 41,341 Metal ring 42,342 Resin liner 43,343 Outer cylinder 44,344 Cylindrical part 45, 345 End face part 46 Depression 47 Notch 5, 305 Rolling bearing 6, 306 Shaft 61 Large diameter part 62 Notch groove 7, 307 Pump chamber 8, 308 Impeller 9, 309 Cylindrical part 91 Large diameter cylindrical part 92 Small-diameter cylindrical part 10,310 Lid part 101,3101 Circular part 102,3102 Wide part 103,3103 Spiral flow path 103a Minimum width part 11,311 Seal member 12 Inlet hole 13 Exit hole 14 Pulley 16 Second exit hole 17 Circulation Path 20 Mating member 21 Depression 22 Gasket 23 First flow path 24 Second flow path 324 Flow path 01 return flow path 203 radiator 204 supply passage

Claims (10)

[Claims] 1. A transport member which rotatably supports a shaft through a bearing on an inner periphery of a shaft hole of a housing and which is inserted into a pump chamber at one end of the shaft and gives mechanical energy to the liquid to transport the liquid. In the coupled pump, the bearing is a sliding bearing, and a first region of a sliding surface of the sliding bearing communicates with a high-pressure portion that is high in liquid flow path configuration, and a second region is in a flow path configuration. A pump which communicates with a low-pressure portion having a pressure lower than that of the high-pressure portion and supplies lubrication to a sliding surface of a slide bearing by a differential pressure between the high-pressure portion and the low-pressure portion of the flow path, thereby enabling lubrication. An inlet hole and an outlet hole are provided in the housing for connecting the slide bearing outer peripheral fitting portion and the pump chamber. The inlet hole is in a high pressure portion of the pump chamber flow passage, and the outlet hole is in a low pressure portion of the pump chamber flow passage. The sliding end of the sliding bearing communicates with one end of the sliding surface in the axial direction as the first region and the inlet hole, and the other end of the sliding surface of the sliding bearing as the second region in the axial direction. The pump according to claim 1, wherein the pump and the outlet hole communicate with each other, and a liquid is supplied to a sliding surface of the slide bearing by a differential pressure between the inlet hole and the outlet hole. 3. A liquid suction port or a discharge port is provided on a side opposite to the pump chamber with a sliding bearing of the housing therebetween.
The slide bearing is provided with a communication hole that communicates the suction port or the discharge port with the pump chamber, and the liquid is transported through the communication hole by rotation of a transport member in the pump chamber. The slide is caused by a differential pressure generated on both sides of the communication hole. 2. The pump according to claim 1, wherein a liquid is supplied to a sliding surface of the bearing. 4. The pump according to claim 1, wherein the shaft body has a communication hole communicating from an end on the pump chamber inner side to one axial end of a sliding surface of the slide bearing. 5. A housing having an inlet hole and an outlet hole communicating the slide bearing outer peripheral fitting portion and the pump chamber, wherein the inlet hole is at a high pressure portion of the pump chamber flow passage and the outlet hole is at a low pressure portion of the pump chamber flow passage. A first communication hole communicating the first area of the sliding surface of the sliding bearing and the inlet hole with the sliding bearing; and a circumferential direction extending from the first area of the sliding surface of the sliding bearing. 2. The pump according to claim 1, further comprising a second communication hole that communicates the second region separated from the outlet hole with the second region. 3. 6. The pump according to claim 1, wherein the sliding surface of the slide bearing is provided with a groove for drawing liquid into the sliding surface. 7. Two bearings are provided apart from each other in the axial direction, the bearing on the pump chamber side is a sliding bearing, the bearing on the opposite side of the pump chamber is a rolling bearing, and the housing is located between the sliding bearing and the rolling bearing. The pump according to any one of claims 1 to 6, further comprising a seal member for sealing between the shaft hole and the shaft body. 8. The sliding bearings are spaced apart from each other in the axial direction.
And one end of the sliding surface of one of the sliding bearings communicates with one end of the sliding surface in the axial direction and the inlet hole, and the other end of the sliding surface of the other sliding bearing communicates with the other end of the sliding surface and the outlet hole. The pump according to any one of claims 1 to 6, wherein 9. An inner peripheral portion of the shaft hole of the housing and an outer cylindrical portion of the slide bearing held by the inner peripheral portion of the housing are formed in a spherical shape. The pump according to any one of claims 1 to 8, wherein the pump is swingably held. 10. The sliding surface of the slide bearing includes a contact sliding portion that contacts the surface of the shaft, and a non-contact sliding portion that is separated from the surface of the shaft. Item 1
A pump according to any one of claims 1 to 9.