JPH11153095A - Liner ring and pump having this liner ring - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce leakage of fluid to a low pressure part from a high pressure part, and to self-correct core dislocation of a rotary body and a liner ring by arranging a machining object layer having high machinability on an inner peripheral side slidingly movable surface of the liner ring in a pump liner ring to generate peripheral directional sliding motion in a liner ring part. SOLUTION: An almost cylindrical liner ring 3 is arranged in an orifice part S where a fixed side casing 1 and a rotary body 2 are opposed to each other, and a machining object layer 4 having high machinability is arranged on an inner peripheral surface of the liner ring 3. The liner ring 3 is made of metal such as bronze and stainless steel, and is fixed to the casing 1. While, the machining object layer 4 is made of plastic, and a clearance 5 between the machining object layer 4 and the rotary body 2 is set small. When the rotary body 2 eccentrically contacts with the machining object layer 4, since a contact part of the machining object layer 4 with the rotary body 2 is shaven off by the rotary body 2, leakage of liquid to a low pressure part L from a high pressure part H is reduced by securing a necessary minimum quantity of clearance 5 formed of a slidingly movable surface of the machining object layer 4 and the rotary body 2.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liner ring provided in a throttle section between a high pressure section and a low pressure section of a centrifugal pump, and a pump provided with the liner ring.

[0002]

2. Description of the Related Art Conventionally, a liner ring used for a centrifugal pump has a substantially cylindrical shape and is generally made of metal, plastic, or the like, so that the rotating body does not come into direct contact with the liner ring even if the main shaft is bent. In addition, the gap between the liner ring and the rotating body is set to be larger than the minimum required. Further, the liner ring is directly and rigidly attached to a fixed side of the pump casing or the like via a pin or the like.

[0003]

However, in the above conventional example, since the gap between the liner ring and the rotating body is larger than the required minimum amount, the fluid leaking from the high-pressure section to the low-pressure section through this gap is reduced. The volume increases, leading to a decrease in pump efficiency. In addition, since the relationship between the liner ring and the pump casing is rigid, high precision is required for the centering work between the rotating body and the liner ring, which is not only troublesome but also stabilizes the rotor dynamics. There is a problem that the damping force to be converted is determined only by the shape of the liner ring.

In view of the above, the present invention has been made in view of the above, and has been made to reduce the leakage of fluid from a high-pressure portion to a low-pressure portion, thereby enabling self-correction (self-alignment) of the misalignment between the rotating body and the liner ring, and the liner ring. It is an object of the present invention to provide a pump provided with:

[0005]

According to a first aspect of the present invention, there is provided a liner ring for a pump in which a liner ring slides in a circumferential direction. It is characterized in that a work layer having high machinability is provided.

According to the present invention, by providing the work layer on the inner peripheral surface of the liner ring, even if the rotating body comes into contact with the work layer during the rotation of the rotary body, the work layer can be removed. The contact portion of the layer is scraped off by the rotating body, and the gap between the sliding surface of the workpiece layer and the rotating body becomes a necessary minimum amount, so that the amount of fluid leaking from the high pressure section to the low pressure section can be reduced.

A second aspect of the liner ring according to the present invention is a liner ring for a pump in which a liner ring slides in a circumferential direction. In a liner ring, an outer surface of the liner ring has a higher damping than a material of the liner ring. A damping member having a capability is provided.

According to the present invention, the liner ring can be provided with a structural damping property and a movable property by the damping member, so that the self-aligning property of the liner ring can be given by the damping force to the rotating body and the fluid force. .

A third aspect of the liner ring according to the present invention is a liner ring for a pump in which a liner ring slides in a circumferential direction. A cutting layer is provided, and a damping member having a higher damping capacity than a material of the liner ring is provided on a mounting surface on an outer peripheral side of the liner ring.

According to the present invention, the liner ring is provided with structural damping and movability by the damping member, thereby providing the liner ring with the damping force to the rotating body and the fluid force, and the liner ring is self-aligning. By providing the work layer on the inner peripheral surface of the liner ring, even if the rotating body comes into contact with the work layer during rotation of the rotary body, the contact portion of the work layer is scraped off by the rotary body. In addition, the gap between the sliding surface of the work layer and the rotating body is a necessary minimum amount, and the amount of fluid leaking from the high pressure portion to the low pressure portion can be reduced.

A pump according to the present invention is characterized in that the liner ring according to any one of claims 1 to 3 is provided on a sliding portion between a pump casing and an impeller. Thereby, the leakage of the fluid from the high-pressure section to the low-pressure section can be reduced, the pump efficiency can be increased, and the assembling work can be simplified.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are views showing a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view, and FIG. 2 is a sectional view taken along line II-II of FIG. In the first embodiment, a throttle section S between a high pressure section H and a low pressure section L of the pump has the following configuration.

That is, a substantially cylindrical liner ring 3 is provided at the throttle portion S where the stationary casing 1 and the rotating body 2 face each other, and the inner peripheral surface (sliding surface) of the liner ring 3 has machinability. A high work layer 4 is provided. The liner ring 3 is made of a metal such as bronze or stainless steel, and is fixed to the casing 1. The work layer 4 is made of a soft plastic. The gap 5 between the workpiece layer 4 and the rotating body 2 is set small.

In this embodiment, even if the rotating body 2 is eccentric and comes into contact with the workpiece layer 4, the contact portion of the workpiece layer 4 with high machinability with the rotating body 2 is rotated. As a result, the gap 5 between the sliding surface of the workpiece layer 4 and the rotating body 2 is minimized. Thereby, leakage of the liquid from the high-pressure section H to the low-pressure section L can be reduced.

FIGS. 3 and 4 are views showing a second embodiment of the present invention. FIG. 3 is a longitudinal sectional view, and FIG.
FIG. 4 is a sectional view taken along line IV. In the present embodiment, a substantially cylindrical liner ring 3 is provided in a narrowed portion S where the stationary casing 1 and the rotating body 2 face each other, and the liner ring 3 is attached to the mounting surface of the liner ring 3 on the casing 1. A thin ring-shaped damping member 6 having a higher damping performance than the material or having a higher elastic-plastic deformability than the material of the liner ring is provided. The damping member 6 is made of a high damping member such as α-gel. If the handling liquid is hot, use Teflon, silicon,
Kalrez or the like is used as the damping member.

In this embodiment, the damping member 6 provides damping capacity and movability between the casing 1 and the liner ring 3 so that the fluid existing in the gap 5 between the rotating body 2 and the liner ring 3 is removed. At the same time, the rotating body 2 is damped through the rotating body 2, and at the same time, the center of the casing 1 and the liner ring 3 is displaced by the fluid force (force for returning the eccentricity) caused by the misalignment of the rotating body 2 and the liner ring 3. Body 2 and liner ring 3
Can be self-aligned.

In the embodiment shown in FIGS. 3 and 4, the damping member is constituted by a thin ring-shaped member. As shown in FIGS. 5 and 6, the damping member is constituted by an O-ring 7 having a circular cross section. The O-ring 7 may be interposed between the casing 1 and the liner ring 3.

FIGS. 7 and 8 show a third embodiment of the present invention. FIG. 7 is a longitudinal sectional view, and FIG.
FIG. 8 is a sectional view taken along line VIII. In the present embodiment, the throttle portion S where the fixed casing 1 and the rotating body 2 face each other includes:
A thin-walled ring having a substantially cylindrical liner ring 3 and having a higher damping performance than the material of the liner ring or a higher elastic-plastic deformability than the material of the liner ring is provided on the surface of the liner ring 3 attached to the casing 1. A damping member 6 having a shape of a circle is provided. The work layer 4 having high machinability is provided on the inner peripheral surface of the liner ring 3. Workpiece layer 4 and rotating body 2
Is set small.

In this embodiment, since the offset between the rotating body 2 and the liner ring 3 is corrected by the damping member 6, the work layer 4 is rotated more than in the embodiment shown in FIGS. The amount removed by the body 2 is reduced, and the gap 5 between the rotating body 2 and the work layer 4 is reduced. As a result, the leakage amount of the fluid leaking from the high-pressure portion H to the low-pressure portion L through the gap 5 is reduced. Less.

Next, an example in which the liner ring of the present invention is applied to a double suction centrifugal pump will be described with reference to FIGS. FIG. 9 is a sectional view showing an example of a pump to which the liner ring of the present invention is applied. A main shaft 11 that is rotationally driven by a motor (not shown) inside a pump casing 10.
Is rotatably supported by a pair of bearings 12 and is inserted therethrough. An impeller 13 serving as a rotating body located inside the spiral chamber 10a of the pump casing 10 is mounted on the main shaft 11 with the main shaft 11. It is mounted so as to rotate together. Thereby, the spiral chamber 10a side of the pump casing 10 becomes the high pressure part H, and the suction chambers 10b, 10b side become the low pressure part L.

The pump casing 10 and the impeller 1
3, a substantially cylindrical liner ring 3 is provided via a pin 14 at a position where the pump casing 10 and the suction portion of the impeller 13 face a narrowed portion S between the high-pressure portion H and the low-pressure portion L. Installed. The suction portion of the impeller 13 is made of a metal such as bronze or stainless steel.

FIGS. 10 to 12 are diagrams showing details of the portion A in FIG. FIG. 10 shows the first embodiment of the present invention shown in FIGS.
13 shows an example in which the liner according to the embodiment is applied. As shown in FIG. 10, a work layer 4 having high machinability is attached to the inner peripheral surface of the liner ring 3. Thus, even if the impeller 13 is eccentric and comes into contact with the work layer 4, the contact portion of the work layer 4 having high machinability with the impeller 13 is scraped off by the impeller 13, and the work layer The gap 5 between the sliding surface 4 and the impeller 13 is the minimum required. Therefore, leakage of the liquid from the high-pressure section H to the low-pressure section L can be reduced.

FIG. 11 shows an example in which the second embodiment of the present invention shown in FIGS. 3 and 4 is applied. FIG.
As shown in FIG. 3, a substantially cylindrical liner ring 3 is provided at a position where the pump housing 10 and the suction portion of the impeller 13 face each other.
Are attached while interposing a thin ring-shaped damping member 6 having a higher damping performance or a higher elastic-plastic deformability than the material of the liner ring.

As a result, the damping member 6 provides damping capacity and movability between the pump casing 10 and the liner ring 3, and through the fluid existing in the gap 5 between the suction portion of the impeller 13 and the liner ring 3. At the same time that the impeller 13 is damped, the pump casing 10 and the core of the liner ring 3 are displaced by the fluid force (force for returning the eccentricity) caused by the misalignment between the impeller 13 and the liner ring 3. 13 and the core of the liner ring 3 can be self-aligned.

FIG. 12 shows an example in which the third embodiment of the present invention shown in FIGS. 7 and 8 is applied. FIG.
As shown in FIG. 3, a substantially cylindrical liner ring 3 is provided at a position where the pump casing 10 and the suction portion of the impeller 13 face each other.
Is attached with a damping member 6 having a higher damping performance or a higher elastic-plastic deformability than the material of the liner ring, and a workable material layer 4 having high machinability is provided on the inner peripheral surface of the liner ring 3. Is provided.

As a result, the impeller 13 is
And the liner ring 3 is misaligned, the amount by which the work layer 4 is scraped off by the impeller 13 is reduced, and the gap 5 between the impeller 13 and the liner ring 3 is reduced. The amount of fluid leaking from the high-pressure section H to the low-pressure section L is reduced. Note that the liner ring of the present invention is not limited to a double-suction volute pump, but can be applied to various pumps.

[0027]

As described above, according to the present invention,
By providing the work layer on the inner peripheral surface of the liner ring, the gap between the rotating body and the work layer can be minimized, and the amount of fluid flowing out from this gap is minimized, and the pump leaks. Loss can be reduced and pump efficiency can be increased.

Also, by attaching the liner ring to the fixed side with an intervening damping member, damping is given to the rotating body to enhance the stability of the rotor dynamics, and self-correction of misalignment between the rotating body and the liner ring is achieved. By doing so, the centering operation can be simplified.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a sectional view showing a second embodiment of the present invention.

FIG. 4 is a sectional view taken along line IV-IV in FIG. 3;

FIG. 5 is a cross-sectional view showing a modification of the second embodiment of the present invention.

6 is a sectional view taken along line VI-VI of FIG.

FIG. 7 is a sectional view showing a third embodiment of the present invention.

8 is a sectional view taken along line VIII-VIII in FIG.

FIG. 9 is a sectional view showing an example of a pump to which the liner ring of the present invention is applied.

FIG. 10 is an enlarged view of a portion A in FIG. 9, and is an enlarged sectional view of a main part of a pump to which the first embodiment of the present invention shown in FIGS. 1 and 2 is applied.

FIG. 11 is an enlarged view of a part A in FIG. 9, and is an enlarged sectional view of a main part of a pump to which the second embodiment of the present invention shown in FIGS. 3 and 4 is applied;

12 is an enlarged view of a part A in FIG. 9, and is an enlarged sectional view of a main part of a pump to which the third embodiment of the present invention shown in FIGS. 7 and 8 is applied.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing (fixed side) 2 Rotating body 3 Liner ring 4 Workpiece layer 5 Gap 6 Damping member 7 O-ring (damping member) 10 Pump casing 13 Impeller (rotating body) H High pressure part L Low pressure part S Throttle part

Claims (4)

[Claims] 1. A liner for a pump in which a liner ring slides in a circumferential direction, wherein a work layer having high machinability is provided on a sliding surface on an inner peripheral side of the liner ring. Liner to do. 2. A liner for a pump in which a liner ring slides in a circumferential direction, wherein a damping member having a higher damping capacity than a material of the liner ring is provided on a mounting surface on an outer peripheral side of the liner ring. Characteristic liner ring. 3. A liner for a pump in which a liner ring slides in a circumferential direction, wherein a work layer having high machinability is provided on a sliding surface on an inner peripheral side of the liner ring, and the liner ring is provided. A damping member having a higher damping ability than a material of the liner ring is provided on a mounting surface on an outer peripheral side of the liner ring. 4. A pump, wherein the liner ring according to claim 1 is provided on a sliding portion between a pump casing and an impeller.