KR20130131421A - Uniaxial eccentric screw pump - Google Patents

Abstract

An object of the present invention is to provide a uniaxial eccentric screw pump which can easily distinguish a stator into an outer cylinder and a lining member and whose fastening value can be easily adjusted.
The stator 20 has a cylindrical liner portion 22 and an outer cylinder portion 24 which are integrally formed such that the inner circumferential surface thereof is female. On both ends of the liner portion 22, flange portions 26, 26 protruding toward the radially outer side are provided, and an outer cylinder mounting portion 28 is provided therebetween. The outer cylinder portion 24 is attached to the outer cylinder mounting portion 28 in a non-adhesive state, and both ends thereof contact the flange portions 26 and 26. The fastening value can be adjusted by inserting or removing the shim 25 between the liner portion 22 and the outer cylinder portion 24.

Description

Single Axis Eccentric Screw Pumps {UNIAXIAL ECCENTRIC SCREW PUMP}

The present invention relates to a uniaxial eccentric screw pump having a stator that can be divided into an outer cylinder portion and a lining portion.

Conventionally, as disclosed in Patent Document 1, a pump called a uniaxial eccentric screw pump having a structure in which a rotor formed in a male screw shape is inserted into a stator in which an inner circumferential surface is formed in a female screw shape is provided. Most of the stators employed in this pump have a structure in which a lining member formed of rubber, resin, or the like is inserted into a metal outer cylinder. In the stator employed in the prior art, by fixing the outer cylinder and the lining member by adhesion or the like, the positional shift between the two and the lining member are prevented.

Japanese Patent Laid-Open No. 2005-344587

In the uniaxial eccentric screw pump of the prior art, the contact pressure and tightening value (overlapping between the outer surface of the rotor and the inner surface of the stator) between the outer surface of the rotor and the inner surface of the stator are accompanied by deterioration with the passage of time of the stator. When it falls and it cannot exhibit sufficient performance, the countermeasure by replacing a stator or the rotor by replacing a rotor with a large diameter is taken. In the case of adopting a method of replacing the rotor with a large diameter for adjustment of the tightening value or the like, there is a problem that the disassembly work of the uniaxial eccentric screw pump is required, and the work efficiency is reduced by that.

In addition, since the stator of the prior art has a structure in which the outer cylinder and the lining member are integrated by adhesion, it is necessary to replace not only the worn lining member but also the outer cylinder when the stator is replaced. Therefore, from the viewpoint of consideration for environmental problems, running cost, etc., the contact pressure between the rotor and the stator can be easily recovered by exchanging the outer cylinder and the lining member constituting the stator, replacing the worn lining member, and the like. It is preferable that it is a structure which can recover a fastening value.

In the case of correspondence by replacing the lining member or the like, it is necessary to disassemble and assemble the uniaxial eccentric screw pump. In addition, in the uniaxial eccentric screw pump of the prior art, the work which exactly matches the center axis of a lining member and a stator at the time of an assembling work is also required. Therefore, in order to further suppress the running frequency associated with the replacement of the lining member and the replacement of the lining member, the fastening can be performed easily and with high accuracy without replacing the lining member except when the lining member is extremely worn. It is preferable that it is a structure which can recover a value etc. and does not need to match the center axis of a lining member and a stator, when performing the operation | work which recovers a fastening value.

In addition, in the uniaxial eccentric screw pump, it is desired to be able to adjust the tightening value appropriately according to the temperature change, the use, etc. of the conveyed fluid. Specifically, in a uniaxial eccentric screw pump, there is a desire to clean members such as a rotor and a stator by transferring hot water or the like after transferring a fluid such as food. However, in the prior art, since the tightening value cannot be adjusted unless the rotor or stator is replaced, the outer diameter of the rotor and the inner diameter of the stator are set so that the tightening value does not become excessive when transferring hot water or the like. Therefore, in the uniaxial eccentric screw pump of the prior art, it was very difficult to set the fastening value etc. at the time of conveying a low temperature fluid to an appropriate state.

Accordingly, the present invention is to provide a uniaxial eccentric screw pump that can easily distinguish the stator into the outer cylinder and the lining member, and can easily and accurately adjust the contact pressure and the fastening value between the outer surface of the rotor and the inner surface of the stator. It was.

The uniaxial eccentric screw pump of the present invention, which is provided to solve the above-mentioned problems, has a male-type rotor, a stator into which the rotor can be inserted, and the stator has a cylindrical liner portion having a female-threaded inner circumferential surface; And an outer cylinder portion disposed so as to surround an outer circumference of the liner portion, the outer cylinder portion being mounted in a non-adhesive state with respect to the liner portion, and the outer cylinder portion being able to offset the radial direction of the liner portion in an area corresponding to at least a portion of the circumferential direction. It is characterized by having the means.

In such a configuration, the contact pressure and the tightening value between the outer surface of the rotor and the inner surface of the stator can be adjusted by offsetting a region corresponding to at least a portion of the outer cylinder portion in the radial direction in the radial direction. Thereby, the fastening value can be appropriately adjusted according to the wear of the lining member, the temperature change of the fluid to be conveyed, the use, and the like, without the replacement of the stator or the rotor. In addition, it is possible to further suppress the replacement frequency and the running cost of the lining member.

Furthermore, as a result of earnestly examining by the present inventors, even when only the area | region corresponding to a part of the circumferential direction of the outer cylinder part was offset as mentioned above, the contact pressure and fastening value of the outer surface of a rotor and the inner surface of a liner part are substantially uniform irrespective of a site | part. It has been found that the lining member wears substantially uniformly without being worn out. Therefore, in the uniaxial eccentric screw pump of this invention, the replacement frequency and running cost of a liner part can be suppressed to the minimum. In addition, in the uniaxial eccentric screw pump of the present invention, when the contact pressure and the tightening value are adjusted by using the adjusting member, it is not necessary to perform the work of matching the center axis of the lining member and the rotor, and the tightening value. The adjustment of the back can be performed easily and with high accuracy.

In the uniaxial eccentric screw pump of the present invention, by adjusting the fastening value or the like using an adjusting means, it is possible to make the operation state suitable for the temperature, use, etc. of the fluid to be conveyed. Accordingly, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent the stator from being damaged due to an excessive tightening value and a decrease in the conveying performance of the fluid due to the excessively fastening value.

The uniaxial eccentric screw pump of the present invention provided on the basis of the same knowledge includes a tubular liner portion having a male-threaded rotor, a stator through which the rotor can be inserted, and the stator having a female-threaded inner circumferential surface; An outer cylinder portion forming a liner portion mounting region in which the liner portion is received in a non-adhesive state, and adjusting means capable of expanding and / or reducing the liner portion mounting region in a radial direction of the liner portion in at least a part of the circumferential direction of the liner portion; It is characterized by having.

In the uniaxial eccentric screw pump of the present invention, the outer surface of the rotor and the stator are enlarged and / or reduced in the radial direction in a part of the circumferential direction of the liner portion by the adjusting means. The contact pressure and tightening value with the inner surface can be adjusted. As a result, the tightening value can be appropriately adjusted without performing replacement of the stator or rotor.

In addition, in the uniaxial eccentric screw pump of the present invention, the lining member does not need to be replaced except when the lining member is excessively worn, and the lining member and There is no need to change the rotor. Thereby, the replacement frequency of a lining member can be suppressed to the minimum, and the labor, running cost, etc. which are required for maintenance can be suppressed to the minimum.

Moreover, as a result of earnestly examining by the present inventors, even when only the area | region corresponding to one part of a circumferential direction is expanded and reduced in the inner peripheral surface of an outer cylinder part, the contact pressure and fastening value of the outer surface of a rotor and the inner surface of a liner part are substantially irrespective of a site | part. It was found to be uniform. For this reason, in the uniaxial eccentric screw pump of this invention, even if it operates in the state which expanded and contracted the liner part mounting area by the adjustment means, the abrasion of lining member does not generate | occur | produce. Therefore, according to this invention, the exchange frequency and running cost of a liner part can be suppressed to the minimum.

In addition, since uneven wear of the lining member does not occur, it is not necessary to perform the operation of matching the central axes of the lining member and the rotor when the operation of adjusting the contact pressure and the fastening value using the adjustment member. Therefore, the uniaxial eccentric screw pump of this invention can implement adjustment work, such as a fastening value, very easily.

In the uniaxial eccentric screw pump of the present invention, by adjusting the fastening value or the like using an adjusting means, it is possible to make the operation state suitable for the temperature, use, etc. of the fluid to be conveyed. Accordingly, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent the stator from being damaged due to an excessive tightening value and a decrease in the conveying performance of the fluid due to the excessively fastening value.

The uniaxial eccentric screw pump of the present invention provided on the basis of the same knowledge includes a tubular liner portion having a male-threaded rotor, a stator through which the rotor can be inserted, and the stator having a female-threaded inner circumferential surface; The liner portion mounting region is adjusted by adjusting an outer cylinder portion forming a liner portion mounting region in which the liner portion is received in a non-adhesive state, and a pressing force acting in a radial direction from the outer cylinder portion side with respect to at least a portion of the circumferential direction of the liner portion. And an adjusting means capable of expanding and / or contracting in the radial direction of the liner portion in at least a portion of the liner portion in the circumferential direction.

In the uniaxial eccentric screw pump of the present invention, by adjusting the pressing force acting on at least a part of the circumferential direction portion of the liner portion from the outer cylinder portion by using an adjusting means, the liner portion mounting region is enlarged and / or reduced in the radial direction. The contact pressure and tightening value between the outer surface of the rotor and the inner surface of the stator can be adjusted. As a result, the tightening value can be appropriately adjusted without performing replacement of the stator or rotor.

In the uniaxial eccentric screw pump of the present invention, except that the lining member is excessively worn, when the tightening value is lowered due to the wear of the lining member, when the temperature of the conveyed fluid is changed, or when the application is changed. For example, the tightening value can be appropriately adjusted only by using the adjusting means. Therefore, according to the uniaxial eccentric screw pump of this invention, the frequency of replacement of a lining member can be suppressed to the minimum, and labor, running cost, etc. which are required for maintenance can be suppressed to the minimum.

Moreover, as a result of earnestly examining by the present inventors, even when the pressing force acting in the radial direction from the outer cylinder part side with respect to a part of the circumferential direction part of a liner part is used, the contact pressure of the outer surface of a rotor and the inner surface of a liner part is adjusted. And it was found that the tightening value became substantially uniform regardless of the site. For this reason, in the uniaxial eccentric screw pump of this invention, even if fastening value etc. are adjusted using an adjustment means, uneven wear of a lining member does not generate | occur | produce. Therefore, according to this invention, the exchange frequency and running cost of a liner part can be suppressed to the minimum.

In addition, since uneven wear of the lining member does not occur, it is not necessary to perform the operation of matching the central axes of the lining member and the rotor when the operation of adjusting the contact pressure and the fastening value using the adjustment member. Therefore, the uniaxial eccentric screw pump of this invention can implement adjustment work, such as a fastening value, very easily.

In the uniaxial eccentric screw pump of the present invention, by adjusting the pressing force acting on at least a part of the circumferential direction of the liner part by using an adjusting means, the fastening value and the like can be easily adjusted to an appropriate value according to the temperature, use, and the like of the conveyed fluid. It becomes possible. Accordingly, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent the stator from being damaged due to an excessive tightening value and a decrease in the conveying performance of the fluid due to the excessively fastening value.

In the uniaxial eccentric screw pump of this invention, it is preferable that the said adjustment means is comprised by the shim which can be interposed and / or detached between the said liner part and the said outer cylinder part.

According to such a configuration, the contact pressure and the tightening value between the outer surface of the rotor and the inner surface of the stator can be adjusted to the optimum state by inserting and extracting the seam, adjusting the seam thickness, and adjusting the number of seams.

In the uniaxial eccentric screw pump of the present invention, the outer cylinder portion can be divided into a plurality of outer cylinder components in the circumferential direction, and the outer cylinder component member has flange portions extending in the axial direction at both ends in the circumferential direction, and the adjustment means described above. It is preferable that it is comprised by the connecting body which connects the flange parts of the said outer cylinder structural member adjacent to this circumferential direction, and it is preferable that the space | interval of the said flange parts can be adjusted.

According to such a structure, by adjusting the space | interval of flange parts by an adjustment means, the contact pressure and fastening value between the outer surface of a rotor and the inner surface of a stator can be adjusted to an optimal state.

Moreover, in the uniaxial eccentric screw pump of this invention, the said connection body may be comprised by the clamping member which clamps the said flange part.

According to such a structure, by adjusting the clamping force which acts on a flange part by a clamping member, the space | interval of flange parts can be adjusted easily and fastening value etc. can be adjusted with high precision.

The uniaxial eccentric screw pump of the present invention provided on the basis of the same knowledge includes a tubular liner portion having a male-threaded rotor, a stator through which the rotor can be inserted, and the stator having a female-threaded inner circumferential surface; A liner portion disposed so as to surround an outer circumference of the liner portion, the outer cylinder portion mounted in a non-adhesive state with respect to the liner portion, at least a portion of the liner portion in a circumferential direction, and extending in the axial direction of the liner portion, It is characterized in that the shim can be interposed and / or detached between the outer cylinder.

In such a configuration, by interposing and / or detaching the shim between the liner portion and the outer cylinder portion, a region corresponding to at least a part of the peripheral direction of the inner circumferential surface of the outer cylinder portion can be offset in the radial direction of the liner portion. In other words, the area (liner part attachment area) for mounting the liner part formed inside the outer cylinder part can be enlarged and / or reduced in the radial direction of the liner part in a part of the circumferential direction of the liner part. Therefore, in the uniaxial eccentric screw pump of the present invention, the contact pressure and the tightening value between the outer surface of the rotor and the inner surface of the stator can be adjusted by interposing and / or detaching the shim between the liner portion and the outer cylinder portion. Therefore, the uniaxial eccentric screw pump of the present invention can appropriately adjust the tightening value according to the wear of the lining member, the temperature change of the conveyed fluid, the use, and the like without performing the replacement of the stator or the rotor. In addition, it is possible to further suppress the replacement frequency and the running cost of the lining member.

Moreover, as mentioned above, when the inventors earnestly examined, when only the area | region corresponding to a part of circumferential direction was offset in the inner peripheral surface of an outer cylinder part, or a liner part mounting area is a part of the circumferential direction of a liner part, a liner part Even when enlarged and / or reduced in the radial direction, it was found that the contact pressure and the fastening value between the outer surface of the rotor and the inner surface of the liner portion became substantially uniform regardless of the site. Therefore, even if the uniaxial eccentric screw pump of the present invention transfers the fluid in the state where the shim is inserted and / or detached between the outer cylinder and the lining member, the lining member is not uniformly worn and wears substantially uniformly. Therefore, in the uniaxial eccentric screw pump of the present invention, it is possible to minimize the replacement frequency and running cost of the liner portion due to uneven wear. In addition, since uneven wear of the liner portion does not occur, it is not necessary to perform the operation of matching the center axis of the lining member and the rotor when the shim is interposed between the liner portion and the outer cylinder portion. Therefore, the uniaxial eccentric screw pump of this invention can perform adjustment work, such as a fastening value, very simply.

In the uniaxial eccentric screw pump of the present invention, by adjusting the tightening value or the like using a shim, an appropriate operating state can be achieved according to the temperature, the use, and the like of the fluid to be conveyed. Accordingly, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent the stator from being damaged due to an excessive tightening value and a decrease in the conveying performance of the fluid due to the excessively fastening value.

The uniaxial eccentric screw pump of the present invention provided on the basis of the same knowledge has a tubular liner portion having a male-threaded rotor, a stator through which the rotor can be inserted, and the stator having a female-threaded inner circumferential surface; And an outer cylinder portion disposed so as to surround the outer circumference of the liner portion, the outer cylinder portion being mounted in a non-adhesive state with respect to the liner portion, wherein the outer cylinder portion can be divided into a plurality of outer cylinder component members in the circumferential direction, and the outer cylinder component member is in the axial direction. The said outer cylinder part can be formed by connecting the flange parts of the said outer cylinder constitution member adjacent to the circumferential direction with a connecting body by having the extended flange part in the circumferential direction both ends, and the said connecting body can adjust the space | interval of the said flange parts. It is characterized by.

In such a configuration, by adjusting the spacing between the flange portions of the outer cylinder constituting members constituting the outer cylinder portion using a connecting body, an area corresponding to at least a part of the peripheral direction of the inner circumferential surface of the outer cylinder portion can be offset in the radial direction of the liner portion. do. In other words, the area (liner part attachment area) for mounting the liner part formed inside the outer cylinder part can be enlarged and / or reduced in the radial direction of the liner part in a part of the circumferential direction of the liner part. Moreover, the pressing force which acts on a liner part can be changed in the area | region of at least one part in the circumferential direction of a liner part. Therefore, in the uniaxial eccentric screw pump of this invention, by adjusting the space | interval of the flange parts of an outer cylinder structural member using a connecting body, the contact pressure and fastening value of the outer surface of a rotor and the inner surface of a stator can be adjusted, There is no need to replace the stator or rotor. In addition, it is possible to further suppress the replacement frequency and the running cost of the lining member.

As described above, according to the results of the present inventors' diligent study, when only an area corresponding to a part of the circumferential direction is offset on the inner circumferential surface of the outer cylinder part, the liner part mounting area is moved in the radial direction of the liner part in a part of the circumferential direction of the liner part. In case of enlargement and / or reduction, the contact pressure between the outer surface of the rotor and the inner surface of the liner portion and the tightening value in any of the cases where the pressing force acting on the liner portion is changed in at least part of the peripheral direction of the liner portion. It becomes roughly uniform regardless of this area. Therefore, even if the uniaxial eccentric screw pump of the present invention transfers the fluid in a state in which the flanges of the outer cylinder constituent members are adjusted by using a connecting body, the lining member is not uniformly worn and wears substantially uniformly. . Therefore, in the uniaxial eccentric screw pump of the present invention, it is possible to minimize the replacement frequency and running cost of the liner portion due to uneven wear. In addition, since uneven wear of the liner portion does not occur, it is not necessary to perform the operation of matching the central axis of the lining member and the rotor when the shim is interposed between the liner portion and the outer cylinder portion. Therefore, the uniaxial eccentric screw pump of this invention can implement adjustment work, such as a fastening value, very easily.

In the uniaxial eccentric screw pump of this invention, it is preferable that a coupling body is comprised by the clamping member which clamps a flange part.

According to this structure, the connecting force acting on a flange part by the holding member can be adjusted easily. Thereby, the fastening value and the like can be adjusted with high accuracy.

In the uniaxial eccentric screw pump of this invention, the flange part which protrudes toward the radial direction outer side is provided in the both ends of the said liner part, The said outer cylinder part is arrange | positioned between the said flange shape parts, The said It is preferable that the edge part of an outer cylinder part contacts.

In the uniaxial eccentric screw pump of this invention, the outer cylinder part is arrange | positioned between the flange-shaped parts provided in the both ends of a liner part, and it is set as the structure which made the edge part of the outer cylinder part contact with the flange-shaped part. Therefore, the outer cylinder portion serves as a support for preventing shrinkage in the axial direction of the liner portion, and the inner diameter of the liner portion can be kept substantially uniform. As a result, uneven wear of the liner portion can be avoided and the discharge amount can be stabilized.

In the uniaxial eccentric screw pump of the present invention, it has an end stud to which one end side of the stator is connected, a pump casing to which the other end side of the stator is connected, and a stay bolt connecting the end stud and the pump casing. It is preferable that the end stud and / or the pump casing are provided with a nut part screwable to the stay bolt, and the gap between the end stud and the pump casing can be changed by relatively rotating the stay bolt and the nut part. Do.

In the uniaxial eccentric screw pump of the present invention, the distance between the end stud and the pump casing can be changed by relatively rotating the stay bolt and the nut portion, so that the tightening value adjustment by the above-described adjustment means can be easily performed.

The uniaxial eccentric screw pump of this invention may be a polygonal shape of the external shape of the said liner part.

By setting it as such a structure, the position shift to the circumferential direction of a liner part can be prevented, and the movable state of a uniaxial eccentric screw pump can be stabilized further.

Moreover, in the uniaxial eccentric screw pump of this invention, it is preferable that the said outer cylinder part is bent in the shape which follows the outer shape of the said liner part.

By setting it as such a structure, position shift to the circumferential direction of a liner part can be prevented more reliably, and the operation state of a uniaxial eccentric screw pump can be further stabilized.

According to the present invention, it is possible to provide a uniaxial eccentric screw pump which can easily distinguish a stator into an outer cylinder and a lining member, and can easily and accurately adjust the contact pressure and the fastening value between the outer surface of the rotor and the inner surface of the stator. .

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the uniaxial eccentric screw pump which concerns on one Embodiment of this invention.
FIG. 2A is an enlarged view of α part of FIG. 1 and (b) is an enlarged view of β part of FIG. 1.
3 is an exploded perspective view of the stator.
Fig. 4 is a diagram showing a stator employed in the uniaxial eccentric screw pump of Fig. 1, (a) is a front view, (b) is a side view, (c) is a BB cross-sectional view of (d), (d Is AA sectional drawing of (a).
FIG. 5 is a view showing a liner portion employed in the stator of FIG. 3, (a) is a front view, (b) is a side view, (c) is a DD cross-sectional view of (b), and (d) is (a) CC cross section.
It is explanatory drawing explaining the attachment method of the clamping piece to the holding part at the time of clamping an outer cylinder structure.
(A) is sectional drawing of the stator in the state which attached a shim, (b) is sectional drawing of the stator in the state which detached a shim.
(A), (b) is a side view of a clamping piece, (c) is sectional drawing of the stator in the state which attached the clamping piece shown to (a).

Then, the uniaxial eccentric screw pump 10 which concerns on one Embodiment of this invention is demonstrated in detail, referring drawings. The uniaxial eccentric screw pump 10 is a so-called rotary displacement pump, and as shown in FIG. 1, the stator 20, the rotor 50, the power transmission mechanism 70, and the like are provided. have. In addition, the uniaxial eccentric screw pump 10 has a cylindrical pump casing 12 and an end stud 13 made of metal, and has a structure in which both of them are integrated. Specifically, in the uniaxial eccentric screw pump 10, swivel nuts 12x and 13x are provided in each of the pump casing 12 and the end stud 13. The pump casing 12 and the end stud 13 are connected via the stay bolt 18 connected with respect to the swivel nut 12x, 13x, and are integrated. Therefore, the uniaxial eccentric screw pump 10 can enlarge and reduce the space | interval of the pump casing 12 and the end stud 13 by rotating the swivel nut 12x, 13x.

The uniaxial eccentric screw pump 10 has the 1st opening 14a in the end stud 13, and has the 2nd opening 14b in the outer peripheral part of the pump casing 12. As shown in FIG. The first opening 14a is a through hole penetrating in the axial direction of the uniaxial eccentric screw pump 10. The second opening 14b communicates with the internal space of the pump casing 12 at the intermediate portion 12a located in the longitudinal middle portion of the pump casing 12.

The 1st, 2nd opening 14a, 14b is a part which functions as the suction port and the discharge port of the uniaxial eccentric screw pump 10, respectively. More specifically, the uniaxial eccentric screw pump 10 of the present embodiment rotates the rotor 50 in the positive direction so that the first opening 14a functions as a discharge port, and the second opening 14b is The fluid can be pressurized to function as an inlet. Also on the contrary, the uniaxial eccentric screw pump 10 rotates the rotor 50 in the opposite direction so that the first opening 14a functions as the inlet port and the second opening 14b functions as the outlet port. Can be pumped.

As shown in FIG. 1 and FIG. 2, the pump casing 12 has a cross-sectional shape at a portion (end portion 12b) facing the end stud 13 side in the assembled state of the uniaxial eccentric screw pump 10. It has the fitting part 12c formed so that it may become step shape. Moreover, also about the end stud 13, the fitting formed in the part (end part 13a) which faces the pump casing 12 side in the assembled state of the uniaxial eccentric screw pump 10 so that a cross-sectional shape may become a step shape is provided. It has a portion 13b. The fitting portions 12c and 13b are portions provided for fitting the flange portion 26 of the stator 20 which will be described later in detail. The width h1 (length in the axial direction) of the fitting portions 12c and 13b is approximately equal to the thickness (length in the axial direction) of the flange portion 26, and is provided at a portion where the fitting portions 12c and 13b are provided. The opening diameter h2 in the inside is substantially the same as the outer diameter of the flange portion 26.

The uniaxial eccentric screw pump 10 has a stator attachment portion 15 for attaching the stator 20 between the pump casing 12 and the end stud 13. The uniaxial eccentric screw pump 10 mounts the stator bolt 18 in a state in which the stator 20 is disposed on the stator attachment portion 15, whereby the pump casing 12 and the end stud 13 are stator 20. A series of flow paths connected between the first and second openings 14a and 14b are formed.

The stator 20 is the most characteristic part of the uniaxial eccentric screw pump 10, and as shown in FIGS. 1, 3, and 4, the liner portion 22, the outer cylinder portion 24, and the shim 25 are provided. Are largely distinguished. The liner portion 22 is formed integrally with an elastic body, resin, or the like represented by rubber. Although the material of the liner part 22 can be suitably selected suitably according to the kind, property, etc. of the fluid to be conveyed using the uniaxial eccentric screw pump 10, fluorine rubber, a flor silicone rubber, or a silicone rubber is appropriate. Can be used. Moreover, as a characteristic of the liner part 22, the small test piece was compressed under the conditions which made the compression ratio 25% using the measuring method described in JISK6262, and it exposed over 72 hours in 100 degreeC temperature atmosphere. It is preferable that the compressive permanent strain at the time is formed of a rubber material having 20% or less. Moreover, it is preferable that the hardness of the liner part 22 exists in the range of 60-80 by the measurement in the temperature atmosphere of 23 +/- 1 degreeC by the type A durometer described in JISK6253.

The liner portion 22 has flange portions 26 and 26 (flange-shaped portions) projecting outward in the radial direction at both ends in the axial direction, and for mounting the outer cylinder portion 24 between the flange portions 26 and 26. It is a cylinder provided with the outer cylinder mounting part 28. The liner portion 22 is formed by integrally forming the flange portions 26 and 26 and the outer cylinder mounting portion 28, and has a step 30 at the boundary portion between the flange portions 26 and 26 and the outer cylinder mounting portion 28. . As for the flange parts 26 and 26, an external shape (cross-sectional shape) is substantially circular, and the external cylinder mounting part 28 has an external shape (cross-sectional shape) in a polygonal shape (in this embodiment, about a dozen square shape). As described above, the thicknesses of the flange portions 26 and 26 are the widths of the fitting portions 12c and 13b provided at the end portions 12b and 13a of the pump casing 12 and the end stud 13. It is equal to h1) or more than the width h1. It is preferable that the thickness of the flange parts 26 and 26 is 5 to 15% thick with respect to the width h1. Thereby, the flange parts 26 and 26 are firmly crimped | bonded and fixed between the pump casing 12 and the end stud 13, and it will be in the sealed state. The outer diameters of the flange portions 26, 26 are the opening diameters h2 of the fitting portions 12c, 13b provided at the ends 12b, 13a of the pump casing 12 and the end studs 13, respectively. It is about the same.

The inner circumferential surface 32 of the liner portion 22 has a n-stage single-threaded or multi-stage female screw shape. In the present embodiment, the inner circumferential surface 32 of the liner portion 22 has a multistage female screw shape. More specifically, the inside of the liner portion 22 is provided with a female threaded through hole 34 extending along the longitudinal direction of the liner portion 22 and twisted at a predetermined pitch. The through-hole 34 is formed so that the cross-sectional shape (opening shape) may become substantially elliptical, even if it sees in a cross section at any position of the liner part 22 in the longitudinal direction.

As shown in FIG.3 and FIG.4, the outer cylinder part 24 covers the outer periphery of the liner part 22 in the outer cylinder mounting part 28 of the liner part 22 mentioned above, and is mounted in a non-adhesive state. Specifically, the outer cylinder portion 24 is mounted on the outer circumference of the liner portion 22 in a pressurized state, and is integrated with the liner portion 22 without using an adhesive, so that the state positioned in both the circumferential direction and the axial direction is do.

As shown in FIG. 3, the outer cylinder part 24 is comprised by the outer cylinder structure 36, 36 and the clamps 38 and 38 in plurality (two in this embodiment), and a liner part mounting area inside. (27) can be formed. The outer cylinder members 36 and 36 are each made of a metal member which covers approximately half of the region in the outer cylinder mounting portion 28 of the liner portion 22 in the circumferential direction, so as to have a shape along the outer cylinder mounting portion 28. It is curved. Therefore, by attaching the outer cylinder member 36 with respect to the liner part 22 so that the outer cylinder mounting part 28 is accommodated in the liner part mounting area 27, the outer cylinder member 36 will be prevented from rotating in the circumferential direction. . In addition, as shown in FIG. 4C, the thickness of the outer cylinder member 36 is larger than the step 30 formed between the flange portion 26 and the outer cylinder mounting portion 28 in the liner portion 22. Therefore, when the outer cylinder member 36 is attached to the outer cylinder mounting portion 28, as shown in FIGS. 1 and 4, the outer cylinder member 36 is radially outer side of the liner portion 22 than the flange portion 26. The state protrudes toward.

In addition, the length of the outer cylinder member 36 is substantially the same as the length of the outer cylinder mounting portion 28. Therefore, when the outer cylinder body 36 is attached to the outer cylinder mounting part 28, the outer cylinder body 36 is formed in the part in which the step | step 30 of the liner part 22 was formed as shown to FIG. 1, FIG. 2, and FIG. Both ends of the c) are in contact with the flange portions 26 and 26. Therefore, when the compressive stress acts toward the axial direction (length direction) in the state which attached the outer cylinder structure 36 with respect to the liner part 22, the outer cylinder part 24 has the said stress in the outer cylinder structure 36. By this, the compressive deformation of the liner portion 22 and the deformation of the through hole 34 formed in the liner portion 22 can be prevented.

At both ends of the outer cylinder mounting portion 28 in the circumferential direction, the gripping portions 40 and 40 (flange portions) are formed so as to extend in the longitudinal direction. Pin insertion through holes 42 and 42 are provided on one end side of the grip portions 40 and 40, and coupling grooves 44 and 44 are formed on the other end side. The pin insertion through holes 42 and 42 and the engaging grooves 44 and 44 are used to mount the clamps 38 and 38 which will be described later in detail. The engaging groove 44 is formed to extend from the edge of the grip portion 40 toward the inclined rear side (the other end side).

The clamp 38 is provided with the clamping piece 46 and the pin 48 of substantially "inverse c" shape in cross section. When the clamping piece 46 is attached to the outer cylinder mounting part 28, the clamping piece 46 is attached so that the holding | gripping part 40 and 40 which are in the superimposed state can be pinched | interposed. The clamping piece 46 has a length substantially the same as the holding part 40, the pin insertion through-hole 46a is provided in the longitudinal direction one end side, and the projection 46b is provided in the other end side. The clamping piece 46 slides the projection 46b along the engagement groove 44 formed so that it may extend in the diagonal direction in the holding part 40, as shown by the arrow X in FIG. In the state hit by the end of the engaging groove 44, as shown by the arrow Y, by rotating around the projection 46b, the pin insertion through-hole 46a is inserted into the pins on the grip portions 40, 40 side. It can be set in the state which communicated with the through-holes 42 and 42. FIG. In this state, the pins 48 are inserted through the pin insertion through holes 46a, 42, and 42, so that the grip portions 40, 40 are clamped by the clamps 38, and the fixed state (clamp-coupled State).

As shown in FIG. 3, the shim 25 (adjustment means, pressing force adjusting means) is made of a thin plate made of metal or resin, and is interposed between the liner portion 22 and the outer cylinder portion 24 described above. It is absent. The thickness of the shim 25 is preferably about 1/30 to 1/100 of the diameter of the rotor 50. In this embodiment, the thickness of the shim 25 is about 0.1 mm to 0.4 mm. In addition, the horizontal width of the shim 25 corresponds to the length in the axial direction of the outer cylinder mounting portion 28 in the liner portion 22 described above, that is, the length of the liner portion mounting region 27 of the outer cylinder portion 24. It is a length to say. In addition, the vertical width of the shim 25 is a length corresponding to a part of the outer circumferential length of the outer cylinder mounting portion 28 in the liner portion 22. Specifically, the vertical width of the shim 25 is about 1/12 to about 1/8 the length of the outer circumference of the outer cylinder mounting portion 28. In other words, the longitudinal width of the shim 25 is a length corresponding to a length of 45 degrees from a length of 30 degrees in the circumferential direction of the outer cylinder mounting portion 28.

As shown in FIG. 3, the shim 25 is mounted over approximately the entire width of the outer cylinder mounting portion 28 in the liner portion 22. 3, 4, and 7 (a), the seam 25 is a part of the region in the circumferential direction of the outer cylinder mounting portion 28 (in this embodiment, 1/12 to 1 on the outer circumference). / 8 region). In addition, the shim 25 may be mounted in only one sheet, and may be mounted in a folded state in plurality. Furthermore, in the case where the shim 25 is already mounted in a stacked state, some of them can be detached as necessary. Although the shim 25 can be arrange | positioned as it is on the outer cylinder mounting part 28, the position by preventing from falling off from the outer cylinder mounting part 28, and the influence by vibration, etc. accompanying the operation of the uniaxial eccentric screw pump 10, and the like. In consideration of preventing misalignment and the like, it is also possible to mount the outer cylinder mounting portion 28 using an adhesive or the like.

The stator 20 inserts or detaches the shim 25 between the liner portion 22 and the outer cylinder portion 24, thereby forming a portion corresponding to a portion of the outer cylinder portion 24 in the circumferential direction, that is, the outer cylinder member 36. 22) in the radial direction.

Specifically, in a situation where the shim 25 is not interposed, as shown in FIG. 7B, the entire inner circumferential surface of the outer cylinder portion 24 is relative to the outer cylinder mounting portion 28 of the liner portion 22. It is in a close state. In this situation, when the shim 25 is inserted between the liner portion 22 and the outer cylinder portion 24, the outer cylinder member 36 on the side where the shim 25 is inserted is inserted as shown in FIG. 7. It will be in the state offset to the radial direction outer side of the part 22. As shown in FIG. When the shim 25 is detached from between the liner portion 22 and the outer cylinder portion 24, the entire inner circumferential surface of the outer cylinder portion 24 is brought into close contact with the outer cylinder mounting portion 28 of the liner portion 22. As a result, the outer cylinder member 36 is in a state of being offset toward the radially inner side of the liner portion 22 by the thickness of the detached shim 25. In this manner, by inserting or detaching the shim 25 between the liner portion 22 and the outer cylinder portion 24, a part of the outer cylinder portion 24 can be offset toward the radial direction of the liner portion 22.

In addition, the stator 20 inserts or detaches the shim 25 between the liner portion 22 and the outer cylinder portion 24, thereby moving the liner portion mounting area 27 in at least part of the circumferential direction of the liner portion 22. It can enlarge and / or reduce in the radial direction of the part 22. Further, by inserting or detaching the shim 25, the pressing force acting in the radial direction from the outer cylinder portion 24 side with respect to a portion of the liner portion 22 in the circumferential direction can be adjusted. Specifically, when the shim 25 is inserted and detached between the liner portion 22 and the outer cylinder portion 24, the liner portion mounting region is as much as the thickness of the shim 25 in the region where the shim 25 is inserted and detached. 27 is enlarged or reduced in the radial direction. Moreover, since the outer cylinder part 24 is mounted so that it may be pressurized with respect to the liner part 22, when the shim 25 is inserted between the liner part 22 and the outer cylinder part 24, it will be in the area | region where the shim 25 was inserted. In this way, the pressing force acting on the liner portion 22 locally rises. On the contrary, when the shim 25 is detached, the pressing force acting on the liner portion by that extent decreases locally.

In addition, the number of the shims 25 interposed between the liner portion 22 and the outer cylinder portion 24 need not necessarily be single, and may be inserted in a plurality of interposed states. In the case where the plurality of shims 25 are interposed, the number of offsets of the overlapping shims 25 is adjusted so that the offset amount of the outer cylinder member 36, the degree of expansion and contraction of the liner portion mounting area 27, and the liner are adjusted. The balance of the pressing force acting on the part 22 can be adjusted more precisely.

The stator 20 covers the outer cylinder members 36 and 36 with respect to the liner portion 22, and is used in a state in which the grip portions 40 and 40 are coupled by the clamps 38 and 38. The stator 20 is embedded in the stator attachment portion 12b at a position adjacent to the first opening 14a in the pump casing 12. Specifically, the stator 20 inserts flange portions 26 and 26 provided at both ends of the liner portion 22 into the fitting portions 12c and 13b provided at the pump casing 12 and the end studs 13. While sandwiching between the end stud 13 and the intermediate part 12a (stator attachment part 12b), the stay bolt 18 is attached over the main stud part of the end stud 13 and the pump casing 12, It is fixed by fastening.

When the stator 20 is attached as described above, as shown in Fig. 2A, one flange portion 26 is formed at one end side of the liner portion 22 so that the end stud 13 and the outer cylinder portion ( 24) It is in the state sandwiched between them. As shown in FIG. 2B, on the other end side, the other flange portion 26 is sandwiched between the intermediate portion 12a and the outer cylinder portion 24. Moreover, about the outer cylinder part 24, it contacts the edge part of the flange part 26 and the end stud 13 by the one end side, and contacts the edge part of the flange part 26 and the pump casing 12 on the other end side. It is in a state. Therefore, the stator 20 does not cause position shift etc. in both the liner part 22 and the outer cylinder part 24 in the stator attachment part 12b of the pump casing 12.

As shown in FIG. 1, the rotor 50 is a shaft made of metal, and has n-1 pairs of single-stage or multistage female threads. In the present embodiment, the rotor 50 has a multistage eccentric male screw shape in one pair. The rotor 50 is formed so that the cross-sectional shape may become substantially circular even if it sees from a cross section at any position of a longitudinal direction. The rotor 50 is inserted into the through hole 34 formed in the stator 20 described above, and is freely eccentrically rotatable inside the through hole 34.

When the rotor 50 is inserted into the through hole 34 formed in the liner portion 22 of the stator 20, the outer circumferential surface 52 of the rotor 50 and the inner circumferential surface 32 of the stator 20 are tangential to both. It is in a contact state over. In this state, the fluid transfer path 60 is formed between the inner circumferential surface 32 of the stator 20 and the outer circumferential surface of the rotor 50.

The fluid conveyance path 60 extends in a spiral shape toward the longitudinal direction of the stator 20 and the rotor 50. Moreover, when the rotor 50 rotates in the through-hole 34 of the stator 20, the fluid conveyance path 60 advances in the longitudinal direction of the stator 20, rotating the inside of the stator 20. As shown in FIG. Therefore, when the rotor 50 is rotated, the fluid is sucked into the fluid conveyance path 60 from one end side of the stator 20, and the fluid is trapped in the fluid conveyance path 60. It can be conveyed toward the other end side and discharged on the other end side of the stator 20. That is, when the rotor 50 is rotated in the positive direction, the fluid sucked from the second opening 14b can be fed and discharged from the first opening 14a. Moreover, when the rotor 50 is rotated in the opposite direction, the fluid sucked from the first opening 14a can be discharged from the second opening 14b.

The power transmission mechanism 70 is provided for transmitting power to the above-described rotor 50 from a power source (not shown) such as a motor provided outside the pump casing 12. The power transmission mechanism 70 has a power connection portion 72 and an eccentric rotation portion 74. The power connection portion 72 is one end side in the longitudinal direction of the pump casing 12, and more specifically, the side opposite to the end stud 13 and the stator attachment portion 12b described above (hereinafter also referred to simply as the "base end side"). Is installed in the shaft housing portion 12c. In addition, the eccentric rotation part 74 is provided in the intermediate part 12a formed between the shaft accommodating part 12c and the stator attachment part 12b.

The power connecting portion 72 has a drive shaft 76, which is supported to be freely rotatable by two bearings 78a and 78b. The drive shaft 76 is taken out from the closed part of the base end side of the pump casing 12, and is connected to the power source. Therefore, the drive shaft 76 can be rotated by operating a power source. Between the shaft accommodating part 12c in which the power connection part 72 was installed, and the intermediate part 12a, the shaft stick apparatus 80 which consists of mechanical seals, grand packing, etc. is provided, for example, As a result, the fluid to be conveyed is not leaked from the intermediate portion 12a side to the shaft receiving portion 12c side.

The eccentric rotation part 74 is a part which connects the drive shaft 76 mentioned above and the rotor 50 so that a power transmission is possible. The eccentric rotation part 74 has a connecting shaft 82 and two connecting bodies 84 and 86. The connecting shaft 82 is made of a conventionally known coupling rod, screw rod, or the like. The connecting body 84 connects the connecting shaft 82 and the rotor 50, and the connecting body 86 connects the connecting shaft 82 and the drive shaft 76. The connecting bodies 84 and 86 are all constituted by a conventionally known universal joint or the like, and transmit the rotational power transmitted via the drive shaft 76 to the rotor 50 so as to eccentrically rotate the rotor 50. Can be.

The uniaxial eccentric screw pump 10 interposes or detaches the shim 25 between the liner portion 22 and the outer cylinder portion 24 in the stator 20, and offsets the outer cylinder portion 24 (the outer cylinder member 36). Amount of the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 by adjusting the amount, the expansion / reduction of the liner portion mounting region 27 and the balance of the pressing force acting on the liner portion 22. Contact pressure and tightening value can be adjusted.

Specifically, when it is necessary to improve the contact pressure and the fastening value between the outer circumferential surface 52 of the rotor 50 and the inner circumferential surface 32 of the liner portion 22 with the wear of the liner portion 22, etc., A part or all of the outer cylinder member 36 constituting the outer cylinder portion 24 is removed from the liner portion 22, and the shim 25 is disposed on the outer circumferential surface of the liner portion 22. When the shim 25 is arrange | positioned previously, the shim 25 is piled up further and arrange | positioned. The shim 25 is in a state where a portion of the outer cylinder mounting portion 28 of the liner portion 22 is attached over the entire width (the entire axial direction). By attaching the outer cylinder member 36 removed in this state, the outer cylinder member 36 is in a state where the outer cylinder member 36 is offset toward the radially outer side in the region where the shim 25 is mounted. In addition, in the region where the shim 25 is mounted, the liner portion mounting region 27 is reduced in the radial direction, and the pressing force acting on the liner portion 22 is locally increased. Thereby, the contact pressure and fastening value with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner part 22 become high.

On the other hand, when it is necessary to reduce the contact pressure and the fastening value between the outer circumferential surface 52 of the rotor 50 and the inner circumferential surface 32 of the liner portion 22 due to the high temperature of the fluid, etc., the outer cylinder portion Part or all of the outer cylinder member 36 constituting (24) is removed from the liner portion 22, and the shim 25 disposed on the outer circumferential surface of the liner portion 22 is removed. When the shim 25 is arrange | positioned in the state piled up multiplely, in addition to removing all the shims 25, some shims 25 can be removed. After removing the shim 25 in this manner, the outer cylinder body 36 is attached, so that the outer cylinder body 36 is offset toward the radially inner side by the amount of the core 25 removed. Moreover, in the area | region from which the shim 25 was removed, the liner part mounting area | region 27 expands in the radial direction, and the pressing force acting on the liner part 22 becomes low. Thereby, the contact pressure and fastening value with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner part 22 become low.

As described above, in the uniaxial eccentric screw pump 10 of the present embodiment, the outer circumferential surface 52 of the rotor 50 and the inner circumferential surface 32 of the liner portion 22 are removed by removing the shim 25. The contact pressure and tightening value can be adjusted. In addition, by detaching part or all of the outer cylinder member 36 constituting the outer cylinder portion 24, the shim 25 can be detached, and it is not necessary to detach and disassemble both the stator 20 and the rotor 50. In addition, in the uniaxial eccentric screw pump 10, the space between the pump casing 12 and the end stud 13, i.e., the stator attachment portion 15, can be expanded and reduced by rotating the swivel nuts 12x and 13x. It does not require labor for the desorption operation of the outer cylinder structure 36. Therefore, the uniaxial eccentric screw pump 10 can easily adjust the fastening value etc. by the shim 25, and is excellent in maintainability.

In the uniaxial eccentric screw pump 10, even if it operates in the state which attached and detached the shim 25 as mentioned above, the contact pressure of the rotor 50 and the liner part 22, The tightening value becomes approximately uniform regardless of the site. Therefore, in the uniaxial eccentric screw pump 10, the liner portion 22 is not uniformly worn and wears substantially uniformly. Moreover, even if the shim 25 is interposed between the liner part 22 and the outer cylinder part, it is not necessary to perform the operation which matches the central axis of the liner part 22 and the rotor 50. Accordingly, the uniaxial eccentric screw pump 10 can minimize the work required for the replacement frequency and maintenance of the liner portion 22 to a minimum.

The uniaxial eccentric screw pump 10 can be operated by setting the fastening value or the like appropriate to the operating conditions by attaching or detaching the shim 25 in accordance with the operating conditions such as the temperature of the fluid to be conveyed and the use. Therefore, according to the uniaxial eccentric screw pump 10, the fall of the stator 20 by the excessive tightening value, and the fall of the conveyance performance of the fluid due to the shortening of the fastening value can be prevented.

The thickness, the vertical width, and the horizontal width of the shim 25 described above are not all limited to those described above, and can be adjusted as appropriate. In addition, when making the width | variety of the shim 25 shorter than the length of the axial direction of the outer cylinder mounting part 28, by implementing measures, such as arrange | positioning the some shim 25 side by side in the axial direction of the outer cylinder mounting part 28, etc. The effect similar to the case where the shim 25 of this embodiment mentioned above is used is obtained by making it the state which the shim 25 was attached over substantially the whole axial direction of the outer cylinder mounting part 28.

In the present embodiment, the shim 25 is interposed between the liner portion 22 and the outer cylinder portion 24, or detached from the outer cylinder portion 24 (the outer cylinder member 36) so as to be interleaved or detached from the liner portion 22 and the outer cylinder portion 24. Although the example used as the adjustment member for adjusting the expansion / reduction of 27) and the balance of the pressing force acting on the liner part 22 was shown, this invention is not limited to this. Specifically, it is good also as a structure which can use the clamp 38 provided in order to hold the holding parts 40 and 40 provided in the circumferential direction both ends of the outer cylinder structure 36 as the above-mentioned adjustment member. Specifically, as shown in FIG. 8, the holding pieces 46x and 46y having different spacings of the opposing surface 46p and 46q on two surfaces are prepared, and the holding pieces 46x and 46y are made in accordance with the fastening value or the like. You may use separately.

Specifically, when the outer cylinder members 36 and 36 are connected by using the gripping piece 46x having a distance d1 shown in Fig. 8A, the liner portion is mounted as shown in Fig. 8C. The area 27 is enlarged so that the pressing force acting on the liner portion 22 is relaxed. Moreover, a part of the outer cylinder part 24 which surrounds the liner part 22, ie, the outer cylinder structure 36, will be in the state offset toward the radially outer side of the liner part 22. As shown in FIG. Thereby, the contact pressure and fastening value with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner part 22 become low.

On the contrary, when the outer cylinder mounting part 28 is connected using the holding piece 46y which is d2 smaller than d1, the space | interval shown in FIG. 8B is outer cylinder part 24, as shown to FIG. The entire inner circumferential surface of the s) is in a state of being in close contact with the outer cylinder mounting portion 28 of the liner portion 22. In this state, the liner part attaching area 27 is reduced compared with the case where the holding piece 46x is used, and the pressing force acting on the liner part 22 becomes high. In addition, a part of the outer cylinder portion 24 surrounding the liner portion 22, that is, the outer cylinder member 36 is in a state of being offset toward the radially inner side of the liner portion 22 than when the gripping piece 46x is used. . Thereby, the contact pressure and fastening value with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner part 22 become high.

As described above, the shim 25 can also be used in the case where the holding pieces 46x and 46y having different intervals are used according to the fastening value or the like. By using the holding pieces 46x, 46y and the shim 25 together, the offset amount of the outer cylinder member 36, which is part of the outer cylinder portion 24, the enlargement and reduction of the liner portion mounting region 27, and acting on the liner portion 22 The balance of the pressing force can be adjusted more precisely.

In addition, the uniaxial eccentric screw pump 10 uses the clamping part 40 of the outer cylinder structure 36 instead of using the clamp 38 with the space | interval of the narrow surface 46p, 46q as shown in FIG. It is good also as a structure which fixes using the fastener 47 which can adjust the clamping force comprised by the bolt etc. in the longitudinal direction of several site | part. In such a configuration, by adjusting the clamping force acting on the gripping portion 40 by the fastener 47, the offset amount of the outer cylinder member 36, the enlargement and reduction of the liner portion mounting area 27, and the liner portion 22 The pressing force acting on) can be adjusted, and the tightening value and the like can be optimized. In addition, also when using the fastener 47, by using together the shim 25 mentioned above, it becomes possible to adjust fastening value etc. more finely.

As described above, in the stator 20 of the uniaxial eccentric screw pump 10 of the present embodiment, the outer cylinder portion 24 is attached to the liner portion 22 formed integrally in a non-adhesive state. Specifically, the radial direction of the liner portion 22 with respect to the outer cylinder portion 24 is influenced by the clamping force generated by attaching the clamp 38 to the gripping portions 40, 40 of the outer cylinder members 36, 26. The pressing force in the inward direction acts. The outer cylinder part 24 is attached to the outer periphery of the liner part 22 by this pressing force, and is in the state positioned in the axial direction and the circumferential direction of the liner part 22. Accordingly, the uniaxial eccentric screw pump 10 can be easily separated and recovered into the liner portion 22 and the outer cylinder portion 24 by removing the outer cylinder members 36 and 36 and the clamps 38 and 38, thereby causing environmental problems. Enough consideration for

In addition, in the uniaxial eccentric screw pump 10, the outer cylinder mounting portion 28 existing between the flange portions 26 provided at both ends of the liner portion 22 is covered by the outer cylinder portion 24, and the end portion of the outer cylinder portion 24 is closed. The structure in contact with the flange portion 26 can prevent the liner portion 22 from contracting in the axial direction. That is, the outer cylinder part 24 plays a supporting role for preventing the shrinkage of the liner part 22 in the axial direction. Thereby, even if the compressive force in the axial direction acts on the stator 20 due to the influence of the discharge pressure, the inner diameter of the liner portion 22 can be maintained substantially uniform regardless of the portion, Uneven wear can be avoided and stabilization of the discharge amount can be attained. In addition, in this embodiment, although the flange part 26 was provided in the both ends of the liner part 22 from the viewpoint of preventing shrinkage of the liner part 22 in the axial direction, etc., this invention is limited to this. It is good also as a structure which does not provide either or both of the flange parts 26.

Since the uniaxial eccentric screw pump 10 can divide | segment the outer cylinder part 24 into the some outer cylinder structure 36 in the circumferential direction, the detachable operation | work of the outer cylinder part 24 with respect to the liner part 22 can be performed easily. In addition, the outer cylinder part 24 mentioned above is integrated by combining (clamping) the outer cylinder members 36 with the clamp 38, and the clamping piece 46 and the pin (with respect to the holding parts 40 and 40). The outer cylinder part 24 can be attached or detached only by attaching and detaching 48).

In addition, although the example which comprised the outer cylinder part 24 by the two outer cylinder members 36 was illustrated in this embodiment, this invention is not limited to this, Furthermore, even if it is comprised by many outer cylinder members 36, do. In addition, although the example which combined the outer cylinder members 36 and 36 by the clamp 38 in two circumferential directions was illustrated in this embodiment, this invention is not limited to this, For example, the outer cylinder members 36, It is also possible to have a structure in which one end side of the circumferential direction of 36 is connected by a hinge or the like and the other end side is connected by a clamp 38 or another method. Furthermore, although the example which used the clamp 38 comprised by the clamping piece 46 and the pin 48 to couple the outer cylinder members 36 and 36 was illustrated in this embodiment, this invention is not limited to this, As long as it can fix the outer cylinder members 36 and 36 so that a position may not shift, the outer cylinder members 36 and 36 may be joined by some other method.

In the uniaxial eccentric screw pump 10 of this embodiment, the end stud 13 is arrange | positioned at the one end side of the stator 20, and the stator 20 ends using the clamping force which the stator bolt 18 produces | generates. It is integrally connected to the pump casing 12 with the stud 13. Moreover, the stator 20 is in the state which the outer cylinder part 24 contacted the end stud 13 and the edge part 12b, 13a of the pump casing 12. As shown in FIG. Therefore, in the state in which the stator 20 is assembled, the clamping force by the stay bolt 18 acts preferentially on the outer cylinder portion 24 rather than the liner portion 22, and is larger in the axial direction with respect to the liner portion 22. The compression force acts or the liner portion 22 can be prevented from compressive deformation. In this way, uneven wear of the liner portion 22 can be prevented and the discharge amount can be stabilized.

In the uniaxial eccentric screw pump 10 of the present embodiment, the fitting portion 12c into which the flange portion 26 can be inserted into the end portion 12b of the pump casing 12 and the end portion 13a of the end stud 13. , 13b) are provided, and the flange portion 26 of the liner portion 22 sandwiched therebetween is sandwiched between the outer cylinder portion 24, the end stud 13, and the pump casing 12. Thereby, position shift of the liner part 22 to the axial direction can be prevented reliably, and the movable state of the uniaxial eccentric screw pump 10 can be stabilized further.

As described above, the outer cylinder mounting portion 28 of the liner portion 22 has a polygonal shape (approximately decagonal in this embodiment). In addition, all the outer cylinder members 36 and 36 are bent in the shape along the outer cylinder mounting part 28, and hold | grip and hold | grip and hold | grip and hold | grip and hold | grip and hold | grip and hold | grip and hold | grip the holding | gripping part 40 with the clamp 38, and are shape substantially the same as the outer cylinder mounting part 28. (In this embodiment, a substantially pentagonal shape), the cylindrical outer cylinder part 24 is formed. Thereby, even if the load in the circumferential direction acts on the liner part 22, the liner part 22 is prevented from causing position shift in the circumferential direction, and stabilization of the movable state of the uniaxial eccentric screw pump 10 is achieved. You can do it.

Moreover, since the liner part 22 is formed in polygonal shape, it is easy to arrange the shim 25 in a desired position and area | region. Moreover, since the outer cylinder structure 36 is formed in the shape which follows the outline of the liner part 22, also when the shim 25 is arrange | positioned over the some surface beyond the angle formed in the outer periphery of the liner part 22, The seam 25 can be reliably bent into a shape along the surface of the liner portion 22 and can be fitted so as not to be misaligned.

In addition, in this embodiment, in order to prevent the misalignment of the liner part 22 with respect to the outer cylinder part 24, and to make arrangement | positioning of the shim 25 easy, etc., the outer cylinder mounting part 28 and the outer cylinder part 24 are each angled. Although the example formed in the shape was illustrated, the case where employ | adopted the other structure which can prevent the position shift etc. to a circumferential direction, the case where it is not necessary to consider even the position shift to the circumferential direction etc. is set as a structure different from the above-mentioned. do. Specifically, the outer cylinder mounting portion 28 and the outer cylinder portion 24 each had substantially the same cross-sectional shape, but, for example, the outer cylinder mounting portion 28 was approximately regular pentagon and the outer cylinder portion 24 was approximately regular hexagon. The cross-sectional shape of both may differ in the range which functions as prevention of rotation of the liner part 22, etc.

Moreover, the structure which provided the processus | protrusion in the inner peripheral side of the outer cylinder part 24, and is equipped with the outer cylinder part 24 in the outer cylinder mounting part 28, The structure which the above-mentioned protrusion contacts with the outer peripheral surface of the liner part 22 in the state pressed. You may make it. According to such a structure, a protrusion is caught by the outer peripheral surface and the shim 25 of the liner part 22, and the position shift in the circumferential direction and the axial direction of the liner part 22, the fall of the shim 25, etc. can be prevented. have. Thus, the structure which forms a processus | protrusion is not only the case where the outer cylinder mounting part 28 and the outer cylinder part 24 are polygonal shapes like this embodiment, but also the liner part like the case where the external shape of the liner part 22 is cylindrical shape. It is also effective when the positional shift of (22), the fall of the shim 25, etc. are concerned.

10: axial eccentric screw pump
12: pump casing
12b: end
12c: Insertion part
13: end stud
13b: Insertion part
15: Stator attachment part
20: Stator
22: liner
24: outer tube
25 seam (adjustment means)
26: flange portion (flange shape portion)
27: liner part mounting area
28: outer cylinder mounting portion
36: outer cylinder structure
46: narrowing edition
50: Rotor

Claims (13)

With a male rotor,
Has a stator through which the rotor can be inserted,
The stator is
A cylindrical liner having a female threaded inner circumferential surface,
An outer cylinder portion disposed to surround an outer circumference of the liner portion, and mounted in a non-adhesive state with respect to the liner portion;
A uniaxial eccentric screw pump, comprising: an adjusting means capable of offsetting the outer cylinder portion in a radial direction of at least a portion of the peripheral direction in a radial direction. With a male rotor,
Has a stator through which the rotor can be inserted,
The stator is
A cylindrical liner having a female threaded inner circumferential surface,
An outer cylinder portion forming a liner portion mounting region in which the liner portion is received in a non-adhesive state;
And an adjusting means capable of enlarging and / or reducing the liner portion mounting region in a radial direction of the liner portion in at least a portion of the liner portion at least in a circumferential direction. With a male rotor,
Has a stator through which the rotor can be inserted,
The stator is
A cylindrical liner having a female threaded inner circumferential surface,
An outer cylinder portion forming a liner portion mounting region in which the liner portion is received in a non-adhesive state;
By adjusting the pressing force acting in the radial direction from the outer cylinder portion side to at least a portion of the liner portion in the circumferential direction, the liner portion mounting region is enlarged and / or radially in the liner portion in at least a circumferential direction portion of the liner portion. A uniaxial eccentric screw pump having an adjusting means that can be reduced. The uniaxial eccentric screw pump according to any one of claims 1 to 3, wherein the adjusting means is constituted by a shim that can interpose and / or detach between the liner portion and the outer cylinder portion. The said outer cylinder part is dividable by the some outer cylinder structural member in a circumferential direction, The said outer cylinder part is any one of Claims 1-4,
The outer cylinder member has a flange portion extending in the axial direction at both ends in the circumferential direction,
The said axial means is comprised by the coupling body which connects the flange parts of the said outer cylinder component member adjacent to a circumferential direction, and the space | interval of the said flange parts is adjustable, The uniaxial eccentric screw pump characterized by the above-mentioned. The uniaxial eccentric screw pump according to claim 5, wherein the connecting member is constituted by a sandwiching member that sandwiches the flange portion. With a male rotor,
Has a stator through which the rotor can be inserted,
The stator is
A cylindrical liner having a female threaded inner circumferential surface,
It is disposed so as to surround the outer periphery of the liner portion, and has an outer cylinder portion mounted in a non-adhesive state with respect to the liner portion,
A portion of at least a circumferential direction of the liner portion, wherein in the region extending in the axial direction of the liner portion, a uniaxial eccentric screw pump, wherein a shim can be interposed and / or detached between the liner portion and the outer cylinder portion. With a male rotor,
Has a stator through which the rotor can be inserted,
The stator is
A cylindrical liner having a female threaded inner circumferential surface,
It is disposed so as to surround the outer periphery of the liner portion, and has an outer cylinder portion mounted in a non-adhesive state with respect to the liner portion,
The outer cylinder portion can be divided into a plurality of outer cylinder structural members in the circumferential direction,
The outer cylinder member
Has a flange portion extending in the axial direction at both ends in the circumferential direction,
The said outer cylinder part can be formed by connecting the flange parts of the said outer cylinder structural member adjacent to a circumferential direction by a coupling body,
The axial eccentric screw pump, wherein the connecting body is capable of adjusting the distance between the flange portions. The uniaxial eccentric screw pump according to claim 8, wherein the connecting member is constituted by a sandwiching member that sandwiches the flange portion. The flange-shaped part which protrudes in the radial direction outer side is provided in the both ends of the said liner part,
The said outer cylinder part is arrange | positioned between the said flange-shaped parts, The edge part of the said outer cylinder part is contacted with the said flange-shaped part, The uniaxial eccentric screw pump characterized by the above-mentioned. The end stud according to any one of claims 1 to 10, wherein one end of the stator is connected;
A pump casing to which the other end side of the stator is connected;
Having a stay bolt connecting the end stud and the pump casing,
The end stud and / or the pump casing are provided with a nut portion screwable to the stay bolt,
The rotation of said stay bolt and said nut part can change the spacing of an end stud and a pump casing, The uniaxial eccentric screw pump characterized by the above-mentioned. The uniaxial eccentric screw pump according to any one of claims 1 to 11, wherein an outer shape of the liner portion is polygonal. The uniaxial eccentric screw pump according to claim 12, wherein the outer cylinder portion is bent in a shape along the outer shape of the liner portion.

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