WO2012090968A1

WO2012090968A1 - Uniaxial eccentric screw pump

Info

Publication number: WO2012090968A1
Application number: PCT/JP2011/080135
Authority: WO
Inventors: 隆橋間; 雅樹小川
Original assignee: 兵神装備株式会社
Priority date: 2010-12-27
Filing date: 2011-12-26
Publication date: 2012-07-05
Also published as: KR20130131421A; CN103282664B; JP2012137038A; CN103282664A; JP5821058B2; EP2660471A4; EP2660471A1; KR101890001B1

Abstract

[Problem] The purpose is to provide a uniaxial eccentric screw pump allowing for easy separation of a stator into an outer tube and a lining member, and for easy adjustment of the tightening margin. [Solution] The stator (20) has an outer tube (24) and a tubular liner (22) integrally formed so that the inner circumferential surface thereof has an internal thread. Flanges (26, 26) extending diametrically outward are provided at both ends of the liner (22), and an outer-tube mounting unit (28) is provided between the flanges. The outer tube (24) is mounted in a non-bonded state in the outer-tube mounting unit (28), and both ends thereof abut against the flanges (26, 26). The tightening tolerance can be adjusted by inserting or removing a shim (25) between the liner (22) and the outer tube (24).

Description

Uniaxial eccentric screw pump

This invention relates to the uniaxial eccentric screw pump provided with the stator which can be divided | segmented into an outer cylinder part and a lining part.

Conventionally, as disclosed in the following Patent Document 1, there is provided 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 having an inner peripheral surface formed in a female screw shape. Has been. Most of the stators employed in this pump have a structure in which a lining member made of rubber or resin is inserted into a metal outer cylinder. In the stator employed in the prior art, the outer cylinder and the lining member are fixed by bonding or the like, thereby preventing the positional deviation between the two and the lining member.

JP-A-2005-344587

In a conventional single-shaft eccentric screw pump, the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance (overlap between the outer surface of the rotor and the inner surface of the stator) are reduced as the stator deteriorates over time. When performance cannot be exhibited, countermeasures are taken by exchanging the stator or by exchanging the rotor with a larger diameter. In the case of adopting a method of replacing the rotor with a larger diameter for adjustment of the tightening allowance or the like, there is a problem that the work of disassembling the single-shaft eccentric screw pump is required, and the work efficiency is reduced accordingly.

In addition, since the stator of the prior art has a structure in which the outer cylinder and the lining member are integrated by bonding, when replacing the stator, it is necessary to replace not only the worn lining member but also the outer cylinder. is there. Therefore, from the viewpoint of environmental issues, running costs, etc., the outer cylinder and the lining member constituting the stator can be easily separated and collected, and contact between the rotor and the stator can be achieved by replacing the worn lining member. It is desirable for the structure to be able to restore pressure and tightening allowance.

場合 When responding by replacing the lining members, etc., disassembly and assembly of the single-shaft eccentric screw pump must be performed. Further, in the conventional single-shaft eccentric screw pump, it is necessary to accurately match the lining member and the central axis of the stator during assembly work. Therefore, in order to further suppress the replacement frequency of the lining member and the running cost associated with the replacement of the lining member, etc., it is easy and accurate even if the lining member is not replaced unless the lining member is extremely worn. It is desirable that the tightening allowance can be recovered well and that the lining member and the center axis of the stator do not need to coincide when performing the operation of recovering the tightening allowance.

Furthermore, in a single-shaft eccentric screw pump, it is desired that the tightening allowance can be appropriately adjusted according to the temperature change of the fluid to be transferred, the application, and the like. Specifically, in a single-shaft eccentric screw pump, there is a demand for cleaning members such as a rotor and a stator by transferring hot water after transferring a fluid such as food. However, in the prior art, the outer diameter of the rotor and the inner diameter of the stator are set so that the tightening allowance is not excessive when transferring hot water or the like because the tightening allowance cannot be adjusted unless the rotor or stator is replaced. Has been. Therefore, in the conventional single-shaft eccentric screw pump, it is very difficult to set the tightening allowance when transferring a low-temperature fluid to an appropriate state.

Therefore, according to the present invention, the stator can be easily separated into the outer cylinder and the lining member, and the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance can be adjusted easily and accurately. The purpose was to provide a simple uniaxial eccentric screw pump.

The uniaxial eccentric screw pump of the present invention provided to solve the above-described problem has a male screw type rotor and a stator through which the rotor can be inserted, and the stator has a female screw type inner peripheral surface. A cylindrical liner part, an outer cylinder part which is arranged so as to surround the outer periphery of the liner part, and is attached in an unbonded state to the liner part, and the outer cylinder part corresponds to at least a part in the circumferential direction And adjusting means that can be offset in the radial direction of the liner portion in the region to be used.

In such a configuration, the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance can be adjusted by offsetting the region corresponding to at least a part of the outer cylinder portion in the radial direction by the adjusting means. Is possible. Accordingly, it is possible to appropriately adjust the tightening allowance according to the wear of the lining member, the temperature change of the fluid to be transferred, the use, and the like without replacing the stator or the rotor. Moreover, it is possible to further suppress the replacement frequency and running cost of the lining member.

Further, as a result of intensive studies by the present inventors, contact between the outer surface of the rotor and the inner surface of the liner portion is possible even when only the region corresponding to a part in the circumferential direction of the outer cylinder portion is offset as described above. It has been found that the pressure and the tightening allowance are substantially uniform regardless of the portion, and the lining member is worn substantially uniformly without uneven wear. 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. Further, in the uniaxial eccentric screw pump of the present invention, when the operation for adjusting the contact pressure and the tightening allowance is performed by using the adjustment member, it is not necessary to perform the operation of matching the lining member and the central axis of the rotor, It is possible to easily and accurately adjust the tightening margin.

In the uniaxial eccentric screw pump of the present invention, it is possible to obtain an appropriate operating state according to the temperature, application, etc. of the fluid to be transferred by adjusting the tightening margin using the adjusting means. Therefore, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent damage to the stator due to excessive tightening allowance and deterioration of fluid transfer performance due to excessive tightening allowance.

The uniaxial eccentric screw pump of the present invention provided based on the same knowledge has a male screw type rotor and a stator through which the rotor can be inserted, and the stator has a female screw type inner peripheral surface. The liner portion, an outer cylinder portion that forms a liner portion mounting region in which the liner portion is accommodated in a non-adhered state, and the liner portion mounting region at least partially in the circumferential direction of the liner portion in the radial direction of the liner portion And adjusting means capable of being enlarged and / or reduced.

In the uniaxial eccentric screw pump of the present invention, the adjustment unit causes the liner portion mounting region formed inside the outer cylinder portion to radially expand and / or contract in the radial direction in a part of the circumferential direction of the liner portion. The contact pressure between the outer surface of the stator and the inner surface of the stator and the tightening allowance can be adjusted. As a result, it is possible to adjust the tightening margin as appropriate without replacing the stator or the rotor.

Further, in the uniaxial eccentric screw pump of the present invention, there is no need to replace the lining member except when the lining member is excessively worn, and even when the temperature change, usage, etc. of the fluid to be transferred change. There is no need to replace the lining member and rotor. Thereby, it is possible to minimize the replacement frequency of the lining member, and to minimize labor and running costs required for maintenance.

Further, as a result of intensive studies by the present inventors, the outer surface of the rotor and the inner surface of the liner portion can be reduced even when only the region corresponding to a part of the circumferential direction is enlarged or reduced on the inner peripheral surface of the outer cylinder portion. It was found that the contact pressure and the tightening allowance became substantially uniform regardless of the site. For this reason, the uniaxial eccentric screw pump of the present invention does not cause uneven wear of the lining member even when operated in a state where the liner portion mounting area is enlarged or reduced by the adjusting means. Therefore, according to the present invention, it is possible to minimize the replacement frequency and running cost of the liner portion.

Also, since uneven wear of the lining member does not occur, it is not necessary to match the central axis of the lining member and the rotor when adjusting the contact pressure and the tightening allowance using the adjusting member. Therefore, the single-shaft eccentric screw pump of the present invention can perform adjustment work such as a tightening margin very easily.

The uniaxial eccentric screw pump of the present invention provided based on the same knowledge has a male screw type rotor and a stator through which the rotor can be inserted, and the stator has a female screw type inner peripheral surface. A liner portion, an outer cylinder portion forming a liner portion mounting region in which the liner portion is accommodated in a non-adhered state, and a radial direction from the outer cylinder portion side to at least a partial region in the circumferential direction of the liner portion Adjustment means capable of expanding and / or reducing the liner portion mounting region in the radial direction of the liner portion at least in a circumferential direction of the liner portion by adjusting a pressing force acting on the liner portion. It is characterized by.

In the uniaxial eccentric screw pump of the present invention, by using the adjusting means, the pressing force acting on at least a partial region in the circumferential direction of the liner portion is adjusted from the outer tube portion side, thereby the radial direction of the liner portion mounting region. The contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance can be adjusted. As a result, it is possible to adjust the tightening margin as appropriate without replacing the stator or the rotor.

In the uniaxial eccentric screw pump of the present invention, except when the lining member is excessively worn, when the tightening margin is lowered due to wear of the lining member, when the temperature of the fluid to be transferred is changed, when the use is changed, etc. Even so, it is possible to optimize the tightening margin only by adjusting using the adjusting means. Therefore, according to the uniaxial eccentric screw pump of the present invention, it is possible to suppress the replacement frequency of the lining member to a minimum, and to reduce the labor and running cost required for maintenance.

In addition, when the present inventors diligently studied, even when adjusting the pressing force acting in the radial direction from the outer tube portion side to the circumferential portion of the region of the liner portion using the adjusting means, It has been found that the contact pressure between the outer surface of the rotor and the inner surface of the liner portion and the tightening allowance are substantially uniform regardless of the site. For this reason, in the uniaxial eccentric screw pump of the present invention, even when the tightening margin is adjusted using the adjusting means, the lining member does not wear unevenly. Therefore, according to the present invention, it is possible to minimize the replacement frequency and running cost of the liner portion.

In the uniaxial eccentric screw pump of the present invention, the tightening margin is adjusted according to the temperature, application, etc. of the fluid to be transferred by adjusting the pressing force acting on at least a partial region in the circumferential direction of the liner portion using the adjusting means. Etc. can be easily adjusted to appropriate values. Therefore, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent damage to the stator due to excessive tightening allowance and deterioration of fluid transfer performance due to excessive tightening allowance.

In the uniaxial eccentric screw pump of the present invention, it is preferable that the adjusting means is constituted by a shim that can be interposed and / or detached between the liner portion and the outer cylinder portion.

According to this configuration, it is possible to adjust the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance to an optimum state by inserting and removing the shim, adjusting the thickness of the shim, adjusting the number of shims, and the like. is there.

In the uniaxial eccentric screw pump of the present invention, the outer cylinder portion can be divided into a plurality of outer cylinder constituent members in the circumferential direction, and the outer cylinder constituent members have flange portions extending in the axial direction at both ends in the circumferential direction. The adjusting means is configured by a connecting body that connects the flange portions of the outer cylinder constituent members adjacent in the circumferential direction, and the interval between the flange portions can be adjusted. It is desirable.

According to such a configuration, the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance can be adjusted to an optimum state by adjusting the interval between the flange portions by the adjusting means.

In the uniaxial eccentric screw pump of the present invention, the connecting body may be constituted by a clamping member that clamps the flange portion.

According to such a configuration, by adjusting the clamping force acting on the flange portion by the clamping member, it is possible to easily adjust the interval between the flange portions and to adjust the tightening allowance with high accuracy.

The uniaxial eccentric screw pump of the present invention provided based on the same knowledge has a male screw type rotor and a stator through which the rotor can be inserted, and the stator has a female screw type inner peripheral surface. A liner portion and an outer cylinder portion that is disposed so as to surround the outer periphery of the liner portion and is attached to the liner portion in a non-adhered state, and is at least a part of the liner portion in the circumferential direction. In the region extending in the axial direction of the liner portion, a shim can be interposed and / or detached between the liner portion and the outer cylinder portion.

In such a configuration, by interposing and / or detaching a shim between the liner portion and the outer cylinder portion, an area corresponding to at least a part of the inner circumferential surface of the outer cylinder portion is arranged on the liner portion. It is possible to offset in the radial direction. In other words, a region (liner portion mounting region) for mounting the liner portion formed inside the outer cylinder portion is enlarged and / or reduced in the radial direction of the liner portion in a part of the liner portion in the circumferential direction. It is possible. Therefore, in the uniaxial eccentric screw pump of the present invention, the contact pressure and tightening allowance between the outer surface of the rotor and the inner surface of the stator are adjusted by interposing and / or removing the shim between the liner portion and the outer cylinder portion. Is possible. Therefore, the single-shaft eccentric screw pump of the present invention can adjust the tightening margin appropriately according to the wear of the lining member, the temperature change of the fluid to be transferred, the application, etc. without replacing the stator or the rotor. is there. Moreover, it is possible to further suppress the replacement frequency and running cost of the lining member.

Further, as described above, as a result of intensive studies by the present inventors, when only the region corresponding to a part of the circumferential direction is offset on the inner peripheral surface of the outer cylinder portion, or the liner portion mounting region is Even in the case of expanding and / or contracting in the radial direction of the liner portion in a part of the circumferential direction, the contact pressure between the outer surface of the rotor and the inner surface of the liner portion, and the tightening allowance are substantially uniform regardless of the part. Turned out to be. Therefore, the uniaxial eccentric screw pump of the present invention is substantially free from uneven wear even when the fluid is transferred with the shim inserted and / or detached between the outer cylinder and the lining member. Wear evenly. 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. Further, since uneven wear of the liner portion does not occur, when the shim is interposed and / or detached between the liner portion and the outer cylinder portion, it is not necessary to perform an operation of matching the center axis of the lining member and the rotor. . Therefore, the uniaxial eccentric screw pump of the present invention can perform adjustment work such as tightening margin very easily.

In the single-shaft eccentric screw pump of the present invention, it is possible to obtain an appropriate operating state according to the temperature, application, etc. of the fluid to be transferred by adjusting the tightening margin using a shim. Therefore, according to the uniaxial eccentric screw pump of the present invention, it is possible to prevent damage to the stator due to excessive tightening allowance and deterioration of fluid transfer performance due to excessive tightening allowance.

The uniaxial eccentric screw pump of the present invention provided based on the same knowledge has a male screw type rotor and a stator through which the rotor can be inserted, and the stator has a female screw type inner peripheral surface. And an outer cylinder portion that is arranged so as to surround the outer periphery of the liner portion and is attached to the liner portion in a non-adhesive state, and the outer cylinder portion has a plurality of circumferential directions. It can be divided into outer cylinder constituent members, and the outer cylinder constituent members have flange portions extending in the axial direction at both ends in the circumferential direction, and connect the flange portions of the outer cylinder constituent members adjacent to each other in the circumferential direction. The outer cylinder part can be formed by connecting with a body, and the connection body can adjust the interval between the flange parts.

In the case of such a configuration, by adjusting the interval between the flange portions of the outer cylinder constituent member constituting the outer cylinder portion by using the coupling body, it corresponds to at least a part of the inner circumferential surface of the outer cylinder portion in the circumferential direction. The region can be offset in the radial direction of the liner portion. In other words, a region (liner portion mounting region) for mounting the liner portion formed inside the outer cylinder portion is enlarged and / or reduced in the radial direction of the liner portion in a part of the liner portion in the circumferential direction. It is possible. In addition, the pressing force acting on the liner portion can be changed in at least a partial region in the circumferential direction of the liner portion. Therefore, in the uniaxial eccentric screw pump of the present invention, the contact pressure and the tightening allowance between the outer surface of the rotor and the inner surface of the stator are adjusted by adjusting the interval between the flange portions of the outer cylinder constituent member using the connecting body. There is no need to replace the stator or rotor. Moreover, it is possible to further suppress the replacement frequency and running cost of the lining member.

As described above, according to the results of the intensive studies by the present inventors, when only the region corresponding to a part in the circumferential direction is offset on the inner peripheral surface of the outer cylinder part, in the part in the circumferential direction of the liner part. When the liner part mounting area is expanded and / or contracted in the radial direction of the liner part, and the pressing force acting on the liner part is changed in at least a part of the circumferential direction of the liner part In this case, the contact pressure between the outer surface of the rotor and the inner surface of the liner portion and the tightening allowance are substantially uniform regardless of the portion. Therefore, the uniaxial eccentric screw pump of the present invention is substantially uniform without uneven wear even when the fluid is transferred in a state where the interval between the flange portions of the outer cylinder constituent member is adjusted using the connecting body. Wear. 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. Further, since uneven wear of the liner portion does not occur, when the shim is interposed and / or detached between the liner portion and the outer cylinder portion, it is not necessary to perform an operation of matching the center axis of the lining member and the rotor. . Therefore, the uniaxial eccentric screw pump of the present invention can very easily perform adjustment work such as tightening allowance. *

In the uniaxial eccentric screw pump of the present invention, it is preferable that the coupling body is constituted by a clamping member that clamps the flange portion.

According to such a configuration, it is possible to easily adjust the coupling force acting on the flange portion by the clamping member. Thereby, it is possible to adjust the tightening margin and the like with high accuracy.

In the uniaxial eccentric screw pump of the present invention, a hook-like part protruding toward the radially outer side is provided at both ends of the liner part, and the outer cylinder part is arranged between the hook-like parts, It is preferable that an end portion of the outer cylinder portion is in contact with the flange portion.

In the uniaxial eccentric screw pump of the present invention, the outer cylinder portion is disposed between the flange portions provided at both ends of the liner portion, and the end portion of the outer cylinder portion is further abutted against the flange portion. The structure is in contact. For this reason, the outer cylinder portion plays a role as a support for preventing the liner portion from contracting in the axial direction, and the inner diameter of the liner portion can be maintained substantially uniform. Thereby, it is possible to avoid uneven wear of the liner portion and to stabilize the discharge amount.

The uniaxial eccentric screw pump of the present invention has an end stud to which one end of the stator is connected, a pump casing to which the other end of the stator is connected, and a stay bolt that connects the end stud and the pump casing. The end stud and / or the pump casing is provided with a nut portion that can be screwed with the stay bolt, and the end stud and the pump are rotated by relatively rotating the stay bolt and the nut portion. It is desirable to be able to change the spacing of the casings.

The uniaxial eccentric screw pump of the present invention can change the interval between the end stud and the pump casing by relatively rotating the stay bolt and the nut portion. Adjustment can be easily performed.

In the uniaxial eccentric screw pump of the present invention, the outer shape of the liner portion may be a polygonal shape.

By adopting such a configuration, it is possible to prevent the displacement of the liner portion in the circumferential direction and further stabilize the operating state of the uniaxial eccentric screw pump.

Further, in the uniaxial eccentric screw pump of the present invention, it is preferable that the outer cylinder portion is bent in a shape along the outer shape of the liner portion.

By adopting such a configuration, it is possible to more reliably prevent the liner portion from being displaced in the circumferential direction, and the operating state of the uniaxial eccentric screw pump can be further stabilized.

According to the present invention, the stator can be easily separated into the outer cylinder and the lining member, and the contact pressure between the outer surface of the rotor and the inner surface of the stator and the tightening allowance can be adjusted easily and accurately. It is possible to provide a simple uniaxial eccentric screw pump.

It is sectional drawing which shows the uniaxial eccentric screw pump concerning one Embodiment of this invention. FIG. 2A is an enlarged view of a portion α in FIG. 1, and FIG. It is a disassembled perspective view of a stator. It is a figure which shows the stator employ | adopted in the uniaxial eccentric screw pump of FIG. 1, (a) is a front view, (b) is a side view, (c) is BB sectional drawing of (d), (d) FIG. 2A is a cross-sectional view taken along the line AA in FIG. It is a figure which shows the liner part employ | adopted as the stator of FIG. 3, (a) is a front view, (b) is a side view, (c) is DD sectional drawing of (b), (d) is ( It is CC sectional drawing of a). It is explanatory drawing explaining the attachment method of the clamping piece with respect to the holding part at the time of clamp coupling | bonding an outer cylinder structural body. (A) is sectional drawing of the stator in the state which mounted | wore the shim, (b) is sectional drawing of the stator in the state which removed the shim. (A), (b) is a side view of a clamping piece, (c) is sectional drawing of the stator in the state which mounted | wore with the clamping piece shown to (a).

Subsequently, a uniaxial eccentric screw pump 10 according to an embodiment of the present invention will be described in detail with reference to the drawings. The uniaxial eccentric screw pump 10 is a so-called rotary displacement pump, and includes a stator 20, a rotor 50, a power transmission mechanism 70, and the like as shown in FIG. Further, the uniaxial eccentric screw pump 10 includes a metal-made cylindrical pump casing 12 and an end stud 13, and has a structure in which both are connected and integrated. Specifically, in the uniaxial eccentric screw pump 10, swivel nuts 12x and 13x are provided in the pump casing 12 and the end stud 13, respectively. The pump casing 12 and the end stud 13 are connected and integrated through stay bolts 18 connected to the swivel nuts 12x and 13x. Accordingly, the uniaxial eccentric screw pump 10 can expand and contract the interval between the pump casing 12 and the end stud 13 by rotating the swivel nuts 12x and 13x.

The uniaxial eccentric screw pump 10 has a first opening 14 a in the end stud 13 and a second opening 14 b in the outer peripheral portion of the pump casing 12. The first opening 14 a is a through hole penetrating in the axial direction of the uniaxial eccentric screw pump 10. The second opening 14 b communicates with the internal space of the pump casing 12 at an intermediate portion 12 a located at the intermediate portion in the longitudinal direction of the pump casing 12.

The first and second openings 14a and 14b are portions that function as a suction port and a discharge port of the uniaxial eccentric screw pump 10, respectively. More specifically, in the uniaxial eccentric screw pump 10 of the present embodiment, the first opening 14a functions as a discharge port and the second opening 14b functions as a suction port by rotating the rotor 50 in the forward direction. It is possible to pump fluid into On the other hand, the uniaxial eccentric screw pump 10 rotates the rotor 50 in the reverse direction so that the first opening 14a functions as a suction port and the second opening 14b functions as a discharge port. It is possible to pump.

As shown in FIGS. 1 and 2, the pump casing 12 is formed in a portion (end portion 12 b) facing the end stud 13 side in the assembled state of the uniaxial eccentric screw pump 10 so that the cross-sectional shape is stepped. It has a fitting portion 12c. The end stud 13 also has a fitting portion 13b formed so that the cross-sectional shape is stepped at a portion (end portion 13a) facing the pump casing 12 side in the assembled state of the uniaxial eccentric screw pump 10. The

fitting portions

12c and 13b are portions provided for fitting a flange portion 26 of the stator 20, which will be described in detail later. The widths h1 (length in the axial direction) of the

fitting portions

12c and 13b are substantially the same as the thickness (length in the axial direction) of the flange portion 26, and the opening diameter at the portion where the

fitting portions

12c and 13b are provided. h <b> 2 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 is connected to the pump casing 12 and the end stud 13 via the stator 20 by mounting the stay bolt 18 in a state where the stator 20 is disposed on the stator mounting portion 15. A series of flow paths connecting the two openings 14a and 14b are formed.

The stator 20 is the most characteristic part of the uniaxial eccentric screw pump 10, and is roughly divided into a liner portion 22, an outer cylindrical portion 24, and a shim 25 as shown in FIGS. The liner portion 22 is integrally formed of an elastic body typified by rubber or resin. The material of the liner portion 22 can be appropriately selected according to the type and properties of the fluid that is the object to be transferred using the uniaxial eccentric screw pump 10, but can be selected from fluoro rubber, fluorosilicone rubber, or silicone. Rubber can be preferably used. Further, as a characteristic of the liner part 22, a small test piece is compressed under a condition in which a compression ratio is 25% by using a measuring method described in JIS K6262, and the temperature is kept at 100 ° C. for 72 hours. It is preferably formed of a rubber material having a compression set of 20% or less when exposed. The hardness of the liner portion 22 is preferably in the range of 60 to 80 as measured by a type A durometer described in JIS K6253 in a temperature atmosphere of 23 ± 1 ° C.

The liner portion 22 has flange portions 26 and 26 (saddle-shaped portions) projecting outward in the radial direction at both end portions in the axial direction, and an outer portion for mounting the outer cylinder portion 24 between the

flange portions

26 and 26. This is a cylinder including a cylinder mounting portion 28. The liner portion 22 is formed by integrally forming

flange portions

26 and 26 and an outer cylinder mounting portion 28, and has a step 30 at a boundary portion between the

flange portions

26 and 26 and the outer cylinder mounting portion 28. The

flange portions

26 and 26 have a substantially circular outer shape (cross-sectional shape), and the outer cylinder mounting portion 28 has a polygonal shape (substantially regular decagonal shape in this embodiment). . Further, as described above, the thickness of the

flange portions

26, 26 is the same as or greater than the width h1 of the

fitting portions

12c, 13b provided in the

end portions

12b, 13a of the pump casing 12 and the end stud 13. ing. The thickness of the

flange portions

26, 26 is desirably 5% to 15% thicker than the width h1. As a result, the

flange portions

26 and 26 are firmly pressed and fixed between the pump casing 12 and the end stud 13 to be in a sealed state. The outer diameters of the

flange portions

26 and 26 are substantially the same as the opening diameters h2 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, respectively.

The inner peripheral surface 32 of the liner portion 22 has a single-stage or multi-stage female thread shape with n strips. In the present embodiment, the inner peripheral surface 32 of the liner portion 22 has a multistage female screw shape. More specifically, an internal thread-shaped through hole 34 that extends along the longitudinal direction of the liner portion 22 and is twisted at a predetermined pitch is provided inside the liner portion 22. The through hole 34 is formed so that its cross-sectional shape (opening shape) is substantially oval even when viewed in cross section at any position in the longitudinal direction of the liner portion 22.

As shown in FIGS. 3 and 4, the outer cylinder portion 24 covers the outer periphery of the liner portion 22 in the outer cylinder mounting portion 28 of the liner portion 22 described above, and is mounted in a non-adhered state. Specifically, the outer cylinder portion 24 is attached to the outer periphery of the liner portion 22 in a pressed state, and is integrated with the liner portion 22 without using an adhesive, both in the circumferential direction and in the axial direction. It will be positioned.

As shown in FIG. 3, the outer cylinder portion 24 includes a plurality (two in the present embodiment) of

outer cylinder components

36 and 36 and clamps 38 and 38. Can be formed. The

outer cylinder components

36, 36 are metal members that cover substantially half of the region in the circumferential direction in the outer cylinder mounting portion 28 of the liner portion 22, and are curved so as to have a shape along the outer cylinder mounting portion 28. (Bent). Therefore, the outer cylinder constituting body 36 is attached to the liner portion 22 so that the outer cylinder attaching section 28 is accommodated in the liner portion attaching area 27, so that the outer cylinder constituting body 36 is prevented from rotating in the circumferential direction. Become. Further, as shown in FIG. 4C, the thickness of the outer cylinder constituting body 36 is larger than the step 30 formed in the liner portion 22 between the flange portion 26 and the outer cylinder mounting portion 28. Therefore, when the outer cylinder component 36 is mounted on the outer cylinder mounting portion 28, the outer cylinder component 36 protrudes outward in the radial direction of the liner portion 22 from the flange portion 26 as shown in FIGS. 1 and 4. It becomes a state.

Further, the length of the outer cylinder constituting body 36 is substantially the same as the length of the outer cylinder mounting portion 28. Therefore, when the outer cylinder constituting body 36 is attached to the outer cylinder attaching portion 28, both end portions of the outer cylinder constituting body 36 are located at the portion where the step 30 of the liner portion 22 is formed as shown in FIGS. 1, 2, and 4. It will be in the state contact | abutted with respect to the

flange parts

26 and 26. FIG. Therefore, when a compressive stress acts in the axial direction (longitudinal direction) in a state where the outer cylinder component 36 is attached to the liner portion 22, the outer cylinder portion 24 applies this stress to the outer cylinder component 36. It is possible to prevent receiving, compressive deformation of the liner portion 22, and deformation of the through hole 34 formed in the liner portion 22.

The gripping portions 40 and 40 (flange portions) are formed at both circumferential ends of the outer cylinder mounting portion 28 so as to extend in the longitudinal direction. Pin insertion holes 42 and 42 are provided on one end side of the

grip portions

40 and 40, and

engagement grooves

44 and 44 are formed on the other end side. The pin insertion holes 42 and 42 and the engaging

grooves

44 and 44 are used for mounting

clamps

38 and 38, respectively, which will be described in detail later. The engaging groove 44 is formed so as to extend obliquely rearward (on the other end side) from the edge of the grip portion 40.

The clamp 38 includes a sandwiching piece 46 having a substantially “U” -shaped cross section and a pin 48. The sandwiching piece 46 is mounted so as to sandwich the gripping

portions

40, 40 that are in an overlapped state when the outer cylinder component 36 is mounted on the outer cylinder mounting portion 28. The sandwiching piece 46 has substantially the same length as the gripping portion 40, a pin insertion hole 46 a is provided on one end side in the longitudinal direction, and a protrusion 46 b is provided on the other end side. 6, the protrusion 46b is slid along the engagement groove 44 formed so as to extend obliquely in the grip portion 40 as indicated by an arrow X in FIG. 6, and the protrusion 46b is an end portion of the engagement groove 44. The pin insertion hole 46a can be brought into communication with the pin insertion holes 42 and 42 on the

gripping portions

40 and 40 side by rotating around the protrusion 46b as indicated by the arrow Y in the state of being in contact with It is. In this state, by inserting the pin 48 over the

pin insertion holes

46a, 42, 42, the

grip portions

40, 40 can be clamped and fixed by the clamp 38 (clamped state). It is.

As shown in FIG. 3, the shim 25 (adjusting means, pressing force adjusting means) is formed 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 a member. The thickness of the shim 25 is preferably about 1/30 to 1/100 of the diameter of the rotor 50. In the present embodiment, the thickness of the shim 25 is about 0.1 mm to 0.4 mm. The lateral width of the shim 25 is the length corresponding to the length in the axial direction of the outer cylinder mounting portion 28 in the liner portion 22 described above, in other words, the length of the liner portion mounting area 27 of the outer cylinder portion 24. The vertical width of the shim 25 is a length corresponding to a part of the outer circumference 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 1/8 of the length of the outer periphery of the outer cylinder mounting portion 28. In other words, the vertical width of the shim 25 is a length corresponding to a length of 30 degrees to a length of 45 degrees in the circumferential direction of the outer cylinder mounting portion 28.

As shown in FIG. 3, the shim 25 is mounted over substantially the entire width of the outer cylinder mounting portion 28 in the liner portion 22. Further, as shown in FIGS. 3, 4 and 7A, the shim 25 has a partial area in the circumferential direction of the outer cylinder mounting portion 28 (in this embodiment, 1/12 to 1/8 of the outer circumference). Is mounted over a certain area). Further, the shim 25 can be mounted in a state where a plurality of shims 25 are mounted in a stacked state, if necessary, in addition to a single sheet. Furthermore, when the shim 25 is already mounted in a stacked state, a part of the shim 25 can be detached as necessary. The shim 25 can be arranged on the outer cylinder mounting portion 28 as it is, but the shim 25 is prevented from falling off from the outer cylinder mounting portion 28, and the displacement due to the influence of vibration or the like accompanying the operation of the uniaxial eccentric screw pump 10 is prevented. In consideration of prevention and the like, it is also possible to mount the outer cylinder mounting portion 28 using an adhesive material or the like.

The stator 20 inserts or removes the shim 25 between the liner portion 22 and the outer cylinder portion 24 to thereby remove a portion corresponding to a part of the outer cylinder portion 24 in the circumferential direction, that is, the outer cylinder structure 36. 22 can be offset in the radial direction.

Specifically, in a situation where the shim 25 is not inserted, the entire inner peripheral surface of the outer cylinder portion 24 is substantially in close contact with the outer cylinder mounting portion 28 of the liner portion 22 as shown in FIG. It is in the state. In this situation, when the shim 25 is inserted between the liner portion 22 and the outer cylinder portion 24, the outer cylinder constituting body 36 on the side where the shim 25 is inserted becomes the diameter of the liner portion 22 as shown in FIG. The state is offset toward the outside in the direction. Further, when the shim 25 is detached from between the liner part 22 and the outer cylinder part 24, the entire inner peripheral surface of the outer cylinder part 24 comes into close contact with the outer cylinder mounting part 28 of the liner part 22. As a result, the outer cylinder constituting body 36 is offset toward the radially inner side of the liner portion 22 by the thickness of the detached shim 25. In this way, by inserting or removing 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.

Further, the stator 20 has a diameter of the liner portion 22 at least at a part in the circumferential direction of the liner portion 22 by inserting or removing the shim 25 between the liner portion 22 and the outer cylinder portion 24. It is possible to enlarge and / or reduce in the direction. Further, by inserting or removing the shim 25, it is possible to adjust the pressing force acting in the radial direction from the outer tube portion 24 side on a partial region in the circumferential direction of the liner portion 22. Specifically, when the shim 25 is inserted and removed between the liner portion 22 and the outer cylinder portion 24, the liner portion mounting region 27 has a diameter corresponding to the thickness of the shim 25 in the region where the shim 25 is inserted and removed. Scaled in or out. Moreover, since the outer cylinder part 24 is mounted so as to be pressed against the liner part 22, when the shim 25 is inserted between the liner part 22 and the outer cylinder part 24, in the region where the shim 25 is inserted. The pressing force acting on the liner portion 22 locally increases. On the contrary, when the shim 25 is detached, the pressing force acting on the liner portion is locally reduced by that amount.

Further, the number of shims 25 inserted between the liner portion 22 and the outer cylinder portion 24 is not necessarily single, and may be inserted in a state where a plurality of shims are stacked. When inserting a plurality of shims 25 in an overlapped state, the number of shims 25 to be overlapped is adjusted to adjust the offset amount of the outer cylinder constituting body 36, the degree of expansion / contraction of the liner portion mounting region 27, and the liner portion 22. It is possible to further finely adjust the balance of the pressing force acting on the.

The stator 20 is used in such a state that the outer

cylinder constituting bodies

36 and 36 are covered with the liner portion 22 and the

gripping portions

40 and 40 are coupled by the

clamps

38 and 38. The stator 20 is incorporated in the stator attachment portion 12b in the pump casing 12 at a position adjacent to the first opening 14a. Specifically, the stator 20 is configured such that

flange portions

26 and 26 provided at both ends of the liner portion 22 are inserted into

fitting portions

12 c and 13 b provided in the pump casing 12 and the end stud 13, and the end stud 13 and the intermediate portion are inserted. 12a (stator mounting portion 12b) and is fixed by attaching and tightening a stay bolt 18 across the end stud 13 and the main body portion of the pump casing 12.

When the stator 20 is attached as described above, one flange portion 26 is sandwiched between the end stud 13 and the outer cylinder portion 24 on one end side of the liner portion 22 as shown in FIG. It becomes a state. Further, as shown in FIG. 2B, the other flange portion 26 is sandwiched between the intermediate portion 12 a and the outer cylinder portion 24 on the other end side. Further, the outer cylinder portion 24 is in contact with the flange portion 26 and the end stud 13 on one end side and in contact with the flange portion 26 and the end portion of the pump casing 12 on the other end side. Therefore, the stator 20 does not cause a positional shift or the like in the stator mounting portion 12b of the pump casing 12 in both the liner portion 22 and the outer cylinder portion 24.

As shown in FIG. 1, the rotor 50 is a metal shaft, and has a single-stage or multi-stage female screw shape with n-1 strips. In the present embodiment, the rotor 50 has a single-threaded multi-stage eccentric male screw shape. The rotor 50 is formed so that the cross-sectional shape thereof is almost a perfect circle when viewed in cross section at any position in the longitudinal direction. The rotor 50 is inserted through the through hole 34 formed in the stator 20 described above, and can be freely eccentrically rotated 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 peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the stator 20 are in contact with each other over the tangent line therebetween. In this state, a fluid conveyance path 60 is formed between the inner peripheral surface 32 of the stator 20 and the outer peripheral surface of the rotor 50.

The fluid conveyance path 60 extends in a spiral shape in the longitudinal direction of the stator 20 and the rotor 50. Further, when the rotor 50 is rotated in the through hole 34 of the stator 20, the fluid conveyance path 60 advances in the longitudinal direction of the stator 20 while rotating in the stator 20. 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 transferred toward the other end side of the stator 20 in a state of being confined in the fluid conveyance path 60. It is possible to discharge at the other end side of the stator 20. That is, when the rotor 50 is rotated in the forward direction, the fluid sucked from the second opening 14b can be pumped and discharged from the first opening 14a. Further, when the rotor 50 is rotated in the reverse direction, the fluid sucked from the first opening 14a can be discharged from the second opening 14b.

The power transmission mechanism 70 is provided to transmit power from the power source (not shown) such as a motor provided outside the pump casing 12 to the rotor 50 described above. The power transmission mechanism 70 includes 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, more specifically, the side opposite to the end stud 13 and the stator mounting portion 12b described above (hereinafter also simply referred to as “base end side”). ) Is provided in the shaft accommodating portion 12c. Moreover, 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 connection 72 has a drive shaft 76 that is supported by two

bearings

78a and 78b so as to be freely rotatable. The drive shaft 76 is taken out from the closed portion on the proximal end side of the pump casing 12 and connected to a power source. Therefore, the drive shaft 76 can be rotated by operating the power source. Between the shaft accommodating portion 12c provided with the power connection portion 72 and the intermediate portion 12a, a shaft sealing device 80 made of, for example, a mechanical seal or a gland packing is provided, whereby the shaft accommodating portion is accommodated from the intermediate portion 12a side. The fluid that is the object to be conveyed does not leak to the portion 12c side.

The eccentric rotating part 74 is a part that connects the drive shaft 76 and the rotor 50 described above so that power can be transmitted. The eccentric rotating part 74 has a connecting shaft 82 and two connecting

bodies

84 and 86. The connecting shaft 82 is configured by 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. Each of the

coupling bodies

84 and 86 is configured by a conventionally known universal joint or the like, and can transmit the rotational power transmitted through the drive shaft 76 to the rotor 50 to rotate the rotor 50 eccentrically. is there.

The uniaxial eccentric screw pump 10 has a shim 25 interposed or detached between the liner portion 22 and the outer cylinder portion 24 in the stator 20, and the offset amount of the outer cylinder portion 24 (outer cylinder structure 36), the liner portion mounting region. The contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance can be adjusted by adjusting the enlargement / reduction of 27 and the balance of the pressing force acting on the liner portion 22. Is possible.

Specifically, when it is necessary to improve the contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 due to wear of the liner portion 22 or the like, the outer cylinder portion 24 is A part or all of the outer cylinder constituting body 36 is removed from the liner portion 22, and the shim 25 is disposed on the outer peripheral surface of the liner portion 22. If the shim 25 has already been arranged, the shim 25 is further overlapped. The shim 25 is mounted over the entire width (the entire axial direction) in a partial region in the circumferential direction of the outer tube mounting portion 28 of the liner portion 22. By mounting the removed outer cylinder structure 36 in this state, the outer cylinder structure 36 is offset radially outward in the region where the shim 25 is mounted. Further, 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. As a result, the contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance are increased.

On the other hand, when the contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance need to be reduced due to the high temperature of the fluid, the outer cylinder portion 24 is formed. A part or all of the outer cylinder constituting body 36 is removed from the liner portion 22, and the shim 25 disposed on the outer peripheral surface of the liner portion 22 is removed. When a plurality of shims 25 are arranged in a stacked state, it is possible to remove some shims 25 in addition to removing all the shims 25. After the shim 25 is removed in this manner, the outer cylinder constituting body 36 is attached, so that the outer cylinder constituting body 36 is offset radially inward by the amount of the shim 25 being removed. Moreover, in the area | region where the shim 25 was removed, the liner part mounting area | region 27 expands to radial direction, and the pressing force which acts on the liner part 22 becomes low. Thereby, the contact pressure with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance are reduced.

As described above, in the uniaxial eccentric screw pump 10 of this embodiment, the contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance are adjusted by attaching and detaching the shim 25. it can. Further, the shim 25 can be detached by detaching a part or all of the outer cylinder constituting body 36 constituting the outer cylinder portion 24, and it is not necessary to remove and disassemble all of the stator 20 and the rotor 50. Further, in the uniaxial eccentric screw pump 10, the interval between the pump casing 12 and the end stud 13, that is, the stator mounting portion 15, can be expanded and contracted by rotating the swivel nuts 12x and 13x. There is no need for trouble in the 36 desorption work. Therefore, the uniaxial eccentric screw pump 10 can easily adjust the tightening allowance by the shim 25, and is excellent in maintainability.

In the uniaxial eccentric screw pump 10, the contact pressure between the rotor 50 and the liner portion 22, and the tightening allowance, even when operated with the shim 25 attached or detached as described above, It becomes almost uniform regardless of the part. Therefore, in the uniaxial eccentric screw pump 10, the liner portion 22 is worn substantially uniformly without uneven wear. Further, even if the shim 25 is inserted between the liner portion 22 and the outer cylinder portion, it is not necessary to perform an operation for matching the center axes of the liner portion 22 and the rotor 50. Accordingly, the uniaxial eccentric screw pump 10 can minimize the frequency of replacement of the liner portion 22 and the work required for maintenance.

The single-shaft eccentric screw pump 10 can be operated with a tightening margin or the like in an appropriate state by attaching or removing the shim 25 according to the operating conditions such as the temperature and application of the fluid to be transferred. It is. Therefore, according to the uniaxial eccentric screw pump 10, it is possible to prevent damage to the stator 20 due to excessive tightening allowance and deterioration of fluid transfer performance due to excessive tightening allowance.

The thickness, vertical width, and horizontal width of the shim 25 described above are not limited to those described above, and can be appropriately adjusted. When the width of the shim 25 is made shorter than the length of the outer cylinder mounting portion 28 in the axial direction, the outer cylinder is mounted by measures such as arranging a plurality of shims 25 side by side in the axial direction of the outer cylinder mounting portion 28. By having the shim 25 mounted over substantially the entire axial direction of the portion 28, the same effect as that obtained when the shim 25 of the present embodiment described above is used can be obtained.

In the present embodiment, the shim 25 is inserted or removed between the liner portion 22 and the outer cylinder portion 24 to remove the offset amount of the outer cylinder portion 24 (outer cylinder structure 36), and the liner portion mounting region 27. Although the example used as an adjustment member for adjusting the balance of the pressing force acting on the enlargement / reduction and the liner portion 22 is shown, the present invention is not limited to this. Specifically, the clamps 38 provided for holding the holding

portions

40, 40 provided at both ends in the circumferential direction of the outer cylinder constituting body 36 may be configured to be used as the adjusting member described above. Specifically, as shown in FIG. 8, gripping

pieces

46x and 46y having different intervals between two opposing clamping surfaces 46p and 46q are prepared, and the

gripping pieces

46x and 46y are selectively used according to the tightening margin or the like. Also good.

Specifically, when the outer

cylinder constituting bodies

36 and 36 are connected using the gripping piece 46x having the interval d1 shown in FIG. 8A, the liner portion mounting region 27 is expanded as shown in FIG. 8C. In addition, the pressing force acting on the liner portion 22 becomes gentle. Further, a part of the outer cylinder part 24 surrounding the liner part 22, that is, the outer cylinder constituting body 36 is offset toward the radially outer side of the liner part 22. Thereby, the contact pressure with the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance are reduced.

On the contrary, when the outer cylinder mounting portion 28 is connected using the gripping piece 46y whose interval shown in FIG. 8B is d2 smaller than d1, the outer cylinder portion 24 of the outer cylinder portion 24 is connected as shown in FIG. 7B. The entire inner peripheral surface is in close contact with the outer cylinder mounting portion 28 of the liner portion 22. In this state, the liner portion mounting region 27 is reduced as compared with the case where the gripping piece 46x is used, and the pressing force acting on the liner portion 22 is increased. Further, a part of the outer cylinder part 24 surrounding the liner part 22, that is, the outer cylinder component 36 is offset toward the radially inner side of the liner part 22 as compared with the case where the gripping piece 46 x is used. Become. As a result, the contact pressure between the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 32 of the liner portion 22 and the tightening allowance are increased.

As described above, the shim 25 can be used in combination when the gripping

pieces

46x and 46y having different intervals are properly used according to the tightening allowance or the like. By using the gripping

pieces

46x, 46y and the shim 25 in combination, the offset amount of the outer cylinder constituting body 36 which is a part of the outer cylinder portion 24, the enlargement / reduction of the liner portion mounting region 27, and the pressing force acting on the liner portion 22 are reduced. It is possible to perform the balance adjustment more finely.

Further, the uniaxial eccentric screw pump 10 is constituted by bolts or the like at a plurality of positions in the longitudinal direction of the grip portion 40 of the outer cylinder constituting body 36 instead of using the clamps 38 having different intervals between the holding

surfaces

46p and 46q as shown in FIG. It is good also as a structure fixed using the fixing tool 47 which can adjust the clamping force made. In the case of such a configuration, by adjusting the clamping force acting on the gripping portion 40 by the fixing tool 47, the offset amount of the outer cylinder constituting body 36, the enlargement / reduction of the liner portion mounting region 27, and the liner portion 22 are affected. It is possible to optimize the tightening allowance by adjusting the pressing force. In addition, also when using the fixing tool 47, it becomes possible to adjust a fastening allowance etc. further finely by using the shim 25 mentioned above together.

As described above, the stator 20 of the uniaxial eccentric screw pump 10 of the present embodiment has the outer cylinder portion 24 attached to the integrally formed liner portion 22 in an unbonded state. Specifically, due to the influence of the clamping force generated by attaching the clamps 38 to the

gripping portions

40, 40 of the outer

cylinder constituting bodies

36, 26, the radially inner direction of the liner portion 22 with respect to the outer cylinder portion 24. The pressing force is applied. The outer cylinder portion 24 is attached to the outer periphery of the liner portion 22 by this pressing force in a pressed state, and is positioned in the axial direction and the circumferential direction of the liner portion 22. Therefore, the uniaxial eccentric screw pump 10 can be easily separated into the liner part 22 and the outer cylinder part 24 by removing the

outer cylinder components

36, 36 and the

clamps

38, 38, and this is an environmental problem. It is possible to pay sufficient attention to

Further, 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 a flange. The structure abuts against the portion 26 and can prevent the liner portion 22 from contracting in the axial direction. That is, the outer cylinder part 24 plays the role of a column for preventing the liner part 22 from contracting in the axial direction. As a result, even if a compressive force in the axial direction acts on the stator 20 due to the influence of the discharge pressure or the like, the inner diameter of the liner portion 22 can be maintained substantially uniform regardless of the portion. It is possible to avoid wear and stabilize the discharge amount. In the present embodiment, the configuration in which the flange portions 26 are provided at both ends of the liner portion 22 is exemplified from the viewpoint of preventing the liner portion 22 from contracting in the axial direction, but the present invention is not limited thereto. In addition, either one or both of the flange portions 26 may be omitted.

In the uniaxial eccentric screw pump 10, since the outer cylinder portion 24 can be divided into a plurality of outer cylinder constituent bodies 36 in the circumferential direction, the detachment operation of the outer cylinder portion 24 with respect to the liner portion 22 can be easily performed. . Further, the above-described outer cylinder portion 24 is formed by integrating the outer cylinder constituent bodies 36 with each other by using a clamp 38 (clamp connection), and the holding piece 46 and the pin 48 with respect to the

gripping portions

40 and 40. It is possible to attach and detach the outer cylinder part 24 only by attaching and detaching the.

In the present embodiment, the example in which the outer cylinder portion 24 is configured by the two outer cylinder components 36 is illustrated, but the present invention is not limited to this, and is configured by a larger number of outer cylinder components 36. It may be done. Moreover, in this embodiment, although the example which couple | bonded the outer cylinder

structural bodies

36 and 36 with the clamp 38 in the circumferential direction two places was illustrated, this invention is not limited to this, For example, the outer cylinder structural bodies 36, It is also possible to have a structure in which one circumferential end of 36 is connected by a hinge or the like and the other end is connected by a clamp 38 or other methods. Furthermore, in this embodiment, the example which used the clamp 38 comprised by the clamping piece 46 and the pin 48 in order to couple | bond the outer cylinder

structural bodies

36 and 36 was illustrated, but this invention is not limited to this. As long as the

outer cylinder components

36 and 36 can be fixed so as not to be displaced, the

outer cylinder components

36 and 36 may be coupled by any other method.

In the uniaxial eccentric screw pump 10 of this embodiment, an end stud 13 is disposed on one end side of a stator 20, and the stator 20 is integrated with the pump casing 12 together with the end stud 13 using a fastening force generated by a stay bolt 18. It is connected. In addition, the stator 20 is in a state in which the outer cylinder portion 24 is in contact with the end stud 13 and the

end portions

12 b and 13 a of the pump casing 12. Therefore, in the state where the stator 20 is assembled, the fastening force by the stay bolt 18 preferentially acts on the outer cylinder portion 24 rather than the liner portion 22, and a large compressive force acts on the liner portion 22 in the axial direction. This can prevent the liner portion 22 from being compressed and deformed. Thereby, it is possible to prevent uneven wear of the liner portion 22 and stabilize the discharge amount.

In the uniaxial eccentric screw pump 10 of the present embodiment,

fitting portions

12c and 13b into which the flange portion 26 can be fitted are provided at the end portion 12b of the pump casing 12 and the end portion 13a of the end stud 13, respectively. The flange portion 26 of the fitted liner portion 22 is sandwiched between the outer cylinder portion 24, the end stud 13 and the pump casing 12. Thereby, it is possible to reliably prevent the position shift of the liner portion 22 in the axial direction, and it is possible to further stabilize the operating state of the uniaxial eccentric screw pump 10.

As described above, the outer cylinder mounting portion 28 of the liner portion 22 has a polygonal shape (substantially decagonal in this embodiment). Further, the outer

cylinder constituting bodies

36 and 36 are both bent in a shape along the outer cylinder mounting portion 28, and the gripper 40 is gripped by the clamp 38 and coupled to each other so as to have substantially the same shape as the outer cylinder mounting portion 28 ( In the present embodiment, a cylindrical outer cylinder portion 24 having a substantially regular decagon) is formed. Accordingly, even when a load in the circumferential direction is applied to the liner portion 22, only the liner portion 22 is prevented from being displaced in the circumferential direction, and the operation state of the uniaxial eccentric screw pump 10 is stabilized. Is possible.

Further, since the liner portion 22 is formed in a polygonal shape, the shim 25 can be easily placed at a desired position and region. Further, since the outer cylinder constituting body 36 is formed in a shape along the outer shape of the liner portion 22, even when the shim 25 is arranged across a plurality of surfaces beyond the corner formed on the outer periphery of the liner portion 22. The shim 25 can be securely bent in a shape along the surface of the liner portion 22 so as not to be displaced.

In the present embodiment, the outer cylinder mounting part 28 and the outer cylinder part 24 are each formed in a polygonal shape for the purpose of preventing the positional deviation of the liner part 22 with respect to the outer cylinder part 24 and facilitating the arrangement of the shim 25. However, it is different from the case described above when another configuration capable of preventing the positional deviation in the circumferential direction, etc., or when it is not necessary to consider the positional deviation in the circumferential direction, etc. It is good also as a structure. Specifically, the outer cylinder mounting portion 28 and the outer cylinder portion 24 have substantially the same cross-sectional shape, but for example, the outer cylinder mounting portion 28 is a substantially regular decagon and the outer cylinder portion 24 is substantially correct. In a category that functions as a detent for the liner portion 22 such as a dodecagon, the cross-sectional shapes of the two may be different.

Further, a projection is provided on the inner peripheral side of the outer cylinder portion 24, and the outer cylinder portion 24 is mounted on the outer cylinder mounting portion 28 so that the above-described projection is pressed against the outer peripheral surface of the liner portion 22. It is good also as a structure which does. According to such a configuration, the protrusion is caught by the outer peripheral surface of the liner portion 22 and the shim 25, and it is possible to prevent the displacement of the liner portion 22 in the circumferential direction and the axial direction, the shim 25 falling off, and the like. The configuration in which the protrusions are provided in this way is not only when the outer cylinder mounting portion 28 and the outer cylinder portion 24 are polygonal as in this embodiment, but also when the outer shape of the liner portion 22 is cylindrical. This is also effective when there is a concern about the displacement of the liner portion 22 or the shim 25 falling off.

DESCRIPTION OF SYMBOLS 10 Uniaxial eccentric screw pump 12 Pump casing

12b End part

12c Insertion part 13 End stud 13b Insertion part 15 Stator attachment part 20 Stator 22 Liner part 24 Outer cylinder part 25 Shim (Adjustment means)
26 Flange part (saddle-shaped part)
27 Liner part mounting area 28 Outer cylinder mounting part 36 Outer cylinder component 46 Clamping piece 50 Rotor

Claims

A male threaded rotor,
A stator through which the rotor can be inserted,
The stator is
A cylindrical liner portion having an inner peripheral surface of a female screw type;
An outer cylinder portion arranged so as to surround the outer periphery of the liner portion and mounted in a non-adhered state on the liner portion;
An uniaxial eccentric screw pump, comprising: an adjusting unit capable of offsetting the outer cylinder portion in a radial direction of the liner portion at least in a region corresponding to a part in a circumferential direction.
A male threaded rotor,
A stator through which the rotor can be inserted,
The stator is
A cylindrical liner portion having an inner peripheral surface of a female screw type;
An outer cylinder part forming a liner part mounting region in which the liner part is accommodated in a non-adhered state;
An uniaxial eccentric screw pump characterized by comprising adjustment means capable of expanding and / or reducing the liner portion mounting region in the radial direction of the liner portion at least in a circumferential direction of the liner portion.
A male threaded rotor,
A stator through which the rotor can be inserted,
The stator is
A cylindrical liner portion having an inner peripheral surface of a female screw type;
An outer cylinder part forming a liner part mounting region in which the liner part is accommodated in a non-adhered state;
By adjusting the pressing force acting in the radial direction from the outer tube part side on at least a part of the liner part in the circumferential direction, the liner part mounting region is at least partly in the circumferential direction of the liner part. A single-shaft eccentric screw pump, characterized by comprising adjusting means capable of being enlarged and / or reduced in the radial direction of the liner portion.
The uniaxial eccentric screw pump according to any one of claims 1 to 3, wherein the adjusting means is configured by a shim that can be interposed and / or detached between the liner portion and the outer cylinder portion.
The outer cylinder part can be divided into a plurality of outer cylinder constituent members in the circumferential direction,
The outer cylinder constituent member has flange portions extending in the axial direction at both circumferential ends,
The said adjustment means is comprised by the coupling body which connects the flange parts of the said outer cylinder structural member adjacent to the circumferential direction, and can adjust the space | interval of the said flange parts. 5. A uniaxial eccentric screw pump according to any one of 1 to 4.
The uniaxial eccentric screw pump according to claim 5, wherein the coupling body is constituted by a clamping member that clamps the flange portion.
A male threaded rotor,
A stator through which the rotor can be inserted,
The stator is
A cylindrical liner portion having an inner peripheral surface of a female screw type;
An outer cylinder portion that is arranged so as to surround the outer periphery of the liner portion, and is attached to the liner portion in a non-adhesive state;
A shim can be interposed and / or detached between the liner part and the outer cylinder part in at least a part of the liner part in the circumferential direction and extending in the axial direction of the liner part. A uniaxial eccentric screw pump characterized by that.
A male threaded rotor,
A stator through which the rotor can be inserted,
The stator is
A cylindrical liner portion having an inner peripheral surface of a female screw type;
An outer cylinder portion that is arranged so as to surround the outer periphery of the liner portion, and is attached to the liner portion in a non-adhesive state;
The outer cylinder part can be divided into a plurality of outer cylinder constituent members in the circumferential direction,
The outer cylinder constituent member is
Has flanges extending in the axial direction at both circumferential ends,
The outer cylinder part can be formed by connecting flange parts of the outer cylinder constituent members adjacent to each other in the circumferential direction by a connecting body,
The uniaxial eccentric screw pump, wherein the connecting body is capable of adjusting a distance between the flange portions.
The uniaxial eccentric screw pump according to claim 8, wherein the coupling body is constituted by a clamping member that clamps the flange portion.
At both ends of the liner portion, a hook-like portion protruding outward in the radial direction is provided,
10. The outer cylinder portion is disposed between the flange portions, and an end portion of the outer cylinder portion is in contact with the flange portions. Uniaxial eccentric screw pump.
An end stud to which one end of the stator is connected;
A pump casing to which the other end of the stator is connected;
A stay bolt for connecting the end stud and the pump casing;
The end stud and / or the pump casing is provided with a nut portion that can be screwed with the stay bolt,
The uniaxial shaft according to any one of claims 1 to 10, wherein an interval between the end stud and the pump casing can be changed by relatively rotating the stay bolt and the nut portion. Eccentric screw pump.
The uniaxial eccentric screw pump according to any one of claims 1 to 11, wherein an outer shape of the liner portion is a polygonal shape.
The uniaxial eccentric screw pump according to claim 12, wherein the outer cylinder portion is bent into a shape along the outer shape of the liner portion.