CN105840494B - Single-shaft eccentric screw pump - Google Patents
Single-shaft eccentric screw pump Download PDFInfo
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- CN105840494B CN105840494B CN201510890515.8A CN201510890515A CN105840494B CN 105840494 B CN105840494 B CN 105840494B CN 201510890515 A CN201510890515 A CN 201510890515A CN 105840494 B CN105840494 B CN 105840494B
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- stator
- end portion
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- bulging
- screw pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
An object of the present invention is to provide a uniaxial eccentric screw pump in which, even when a flexible coupling member is used in a power transmission mechanism section, a reduction in pressure delivery performance or the like due to a deformation in the posture of a rotor caused by the influence of the restoring force, i.e., the reaction force, of the coupling member can be suppressed to a minimum; a uniaxial eccentric screw pump (10) is provided with a rotor (30), a stator (20) having a through hole (22), and a power transmission mechanism part (50); a connecting member (62) composed of a flexible rod and the like is provided in the power transmission mechanism part (50); the through hole (22) is opened so as to form an oblong opening region in a cross section transverse to the axis of the stator (20); the stator (20) has a bulging portion that bulges toward the inside in the width direction of the opening region at the longitudinal direction intermediate portion of the opening region.
Description
Technical Field
The present invention relates to a uniaxial eccentric screw pump in which a power transmission mechanism for transmitting rotational power input from a drive source to a rotor is provided with a flexible coupling member having a direction intersecting with an axial direction of the rotor.
Background
Conventionally, there is provided a uniaxial eccentric screw pump in which a flexible coupling member such as a flexible rod (flex rod) or a flexible wire is provided in a power transmission mechanism portion, as in the uniaxial eccentric screw pump disclosed in patent document 1 below. In the uniaxial eccentric screw pump of patent document 1, the rotational power input from the drive source can be transmitted to the rotor through the coupling member. This enables the rotor to eccentrically rotate while rotating inside the stator and revolving along the inner circumferential surface of the stator.
[ Prior art documents ]
[ patent document ]
Patent document 1: japanese laid-open patent publication No. 2012-154215
However, when a connecting member such as a flexible rod is used in the power transmission mechanism portion as described above, the posture of the rotor is deformed by the restoring force (reaction force) of the connecting member. Further details are described below with reference to fig. 8, namely: when the rotor 120 connected to the connection member 100 is inserted into the stator 110 and rotated, the restoring force of the connection member 100 acts on the rotor 120. Due to the restoring force, the rotor 120 attempts to change its posture so as to follow the connecting member 100 such as a flexible rod to be aligned in a straight line. However, the movement of the rotor 120 is restricted by the stator 110. Therefore, the rotor 120 does not become a posture aligned with the connection member 100.
Here, if the stator 110 is a rigid body such as a metal, the rotor 120 does not move and assumes the posture shown in fig. 8 (a). Specifically, even if the restoring force due to the deformation of the connection member 100 acts, the movement of the rotor 120 is completely restricted by the stator 110 as long as the stator 110 is a rigid body, and therefore the rotor 120 does not tilt with respect to the stator 110.
However, the stator 110, which is generally used, is formed of an elastic body such as rubber, and thus is elastically deformed. Therefore, when the restoring force of the link member 100 acts on the rotor 120, the rotor 120 is inclined such that the base end side (power source side: right side in the drawing) is lower than the tip end side (left side in the drawing) as in the example shown in fig. 8 (b).
In the uniaxial eccentric screw pump, the rotor 120 is linearly contacted in the stator 110, whereby a space (cavity) through which a fluid to be pressure-fed passes is formed in the stator 110. When a line contact portion (seal line) between the rotor 120 and the stator 110 forming the cavity is broken, the fluid may flow backward from the discharge side at a high pressure to the suction side at a low pressure. Further, when the rotor 120 performs an operation deviating from a geometrically ideal motion pattern, there is a high possibility that the pressure feed performance is lowered or the fluid pulsation is caused. Therefore, in the uniaxial eccentric screw pump, it is an important subject in terms of stabilizing the discharge performance that the rotor 120 is not inclined with respect to the stator 110.
However, when the stator 110 is elastically deformed, the posture of the rotor 120 is changed as shown in fig. 8(b) by the restoring force generated by the deformation of the connection member 100, and the seal line may be broken or the rotor 120 may perform an operation of deviating from a geometrically ideal motion form. Therefore, when the connection member 100 such as a flexible rod is used in the power transmission mechanism portion, there is a high possibility that problems such as backflow of fluid and pulsation of fluid may occur.
Disclosure of Invention
Therefore, an object of the present invention is to provide a uniaxial eccentric screw pump in which, even when a flexible connecting member such as a flexible rod or a cord is used in a power transmission mechanism section, the posture deformation of a rotor due to the influence of the restoring force (reaction force) of the connecting member, and the reduction in pressure delivery performance and pulsation of fluid caused by the deformation can be suppressed to the minimum.
Here, in general, as shown in fig. 8(c) to 8(e), the thickness of the stator is thinner on the outer side in the longitudinal direction of the opening region of the through hole and thicker on the outer side in the width direction. Therefore, a reaction force applied to the stator due to the rotor coming into contact with the stator in the through hole and applying a force outward in the stator radial direction from the rotor to the stator, that is, an influence of a restoring force acting on the stator from the connecting member on the posture of the rotor is small at both longitudinal end portions of the opening region of the through hole and large at the intermediate longitudinal portion. Based on such assumptions, the inventors have arrived at the following findings: if the force applied from the rotor to the stator toward the outside in the opening region width direction can be supported by the longitudinal intermediate portion of the opening region of the through hole, the posture deformation of the rotor due to the influence of the restoring force (reaction force) of the connecting member can be suppressed, and the reduction of the pressure-feed performance or the pulsation of the fluid can be suppressed to the minimum.
The uniaxial eccentric screw pump of the present invention provided based on the above-described findings includes: a rotor formed of a male screw shaft body, a stator formed of an elastic body having a female screw through hole into which the rotor can be inserted, and a power transmission mechanism for transmitting rotational power input from a drive source to the rotor; the power transmission mechanism unit includes a connection member that is flexible in a direction intersecting with an axial direction of the rotor, and that is capable of eccentrically rotating the rotor so as to revolve along an inner circumferential surface of the stator while rotating inside the stator; the through hole is opened so as to form an oblong opening region in a cross section intersecting an axis of the stator; a bulging portion bulging toward the inside in the width direction of the opening region at a longitudinal direction intermediate portion of the opening region is provided in at least a part of a region in the axial direction of the stator.
In the uniaxial eccentric screw pump of the present invention, a bulging portion bulging inward in the width direction of an opening region of a through hole provided in a stator is provided in at least a part of a region in the axial direction of the stator. With this configuration, the force applied from the rotor to the stator toward the outside in the width direction of the through hole can be supported by the bulging portion. This can suppress the deformation of the posture of the rotor due to the influence of the restoring force (reaction force) of the connecting member, and can suppress the reduction of the pressure-feed performance and the pulsation of the fluid to the minimum.
In the uniaxial eccentric screw pump of the invention described above, it is preferable that: the connecting member is constituted by a flexible rod or cord.
In the uniaxial eccentric screw pump of the present invention, the deformation of the posture of the rotor due to the influence of the restoring force of the coupling member composed of the flexible rod or the cord can be suppressed to the minimum. This makes it possible to minimize the reduction in the pressure feed performance and the pulsation of the fluid due to the deformation of the posture of the rotor.
The present inventors have conducted intensive studies and found the following: when the restoring force of the connecting member acts on the rotor, the rotor is in a state in which the movement of the rotor is restricted by the rigidity of the stator at an end portion (tip end portion) on the opposite side to the driving source side, and thus the rotor is likely to hang down toward the base end portion side with the tip end portion side as a fulcrum.
The uniaxial eccentric screw pump of the present invention provided based on the above findings is configured such that: the stator has a base end portion on the drive source side and a tip end portion on the opposite side of the drive source, and the bulge portion is provided at least in a region on the base end portion side of the stator.
With this configuration, the rotor can be kept in a state of hanging down from the distal end side toward the base end side, that is, in a state of being inclined with respect to the stator. This makes it possible to provide a uniaxial eccentric screw pump capable of minimizing the reduction in pressure feed performance and the pulsation of fluid.
In the uniaxial eccentric screw pump of the present invention, the amount of expansion of the expansion portion may be substantially uniform over the entire region in the stator axial direction from the viewpoint of stabilizing the posture of the rotor. However, in order to be able to take into consideration problems such as an increase in torque due to the installation of the bulging portion and an increase in wear rate due to deterioration of the lubricating property, it is preferable to further optimize the amount of bulging in the bulging portion.
The present inventors have conducted intensive studies based on the above findings and then have found the following findings: by adopting a configuration in which the projection portion is not provided in a part of the region in the stator axial direction or by reducing the projection amount of the projection portion, it is possible to obtain an effect of improving the discharge performance or an effect of suppressing the fluid pulsation, and also to achieve an effect of reducing the wear rate or the like. Further, as described above, when the restoring force of the connecting member acts on the rotor, the rotor is likely to be in a state of drooping toward the base end side with the tip end side of the stator as a fulcrum. Therefore, it is preferable to adjust the amount of swelling of the swelling portion so that the effect of the swelling portion can be exhibited in the region on the base end side rather than the region on the tip end side.
The uniaxial eccentric screw pump of the present invention provided based on the above findings is configured such that: the stator has a base end portion on the drive source side and a tip end portion on the opposite side of the drive source, and the amount of bulging of the bulging portion in the base end portion side region is larger than the amount of bulging in the tip end portion side region.
With this configuration, the influence of the restoring force of the connecting member on the posture of the rotor can be minimized, and effects such as prevention of an increase in torque and reduction in wear rate can be obtained.
Further, the uniaxial eccentric screw pump of the present invention provided based on the same findings is configured such that: the stator has a base end portion positioned on the drive source side and a tip end portion positioned on the opposite side of the drive source, and the amount of projection of the projection portion gradually increases from the tip end portion side toward the base end portion side.
With this configuration, the influence of the restoring force of the connecting member on the posture of the rotor can be minimized. Further, the effects of improving the discharge performance and suppressing the fluid pulsation, and the effects of reducing the wear rate, etc. can be obtained.
(effect of the invention)
According to the present invention, it is possible to provide a uniaxial eccentric screw pump in which, even when a flexible connecting member such as a flexible rod or a cord is used in a power transmission mechanism section, the posture deformation of a rotor due to the influence of the restoring force (reaction force) of the connecting member, and the reduction in pressure delivery performance and pulsation of fluid caused by the deformation can be suppressed to the minimum.
Drawings
Fig. 1 is a sectional view of a uniaxial eccentric screw pump according to an embodiment of the present invention.
Fig. 2 (a) is a front view showing an example of the stator, (b) is a left side view, (c) is a cross-sectional view a1-a1, and (d) is a right side view; the rear view, the top view, and the bottom view are the same as the front view, and therefore, the illustration thereof is omitted.
Fig. 3 (a) is a sectional view taken along line B-B of fig. 2(C), and (B) is a sectional view taken along line C-C of fig. 2 (C).
Fig. 4 is an explanatory view of the postures of the rotor and the connecting member when the single-shaft eccentric screw pump of fig. 1 is operated.
Fig. 5 (a) is a front view showing a first modification of the stator, (b) is a left side view, (c) is a cross-sectional view a2-a2, and (d) is a right side view; the rear view, the top view, and the bottom view are the same as the front view, and therefore, the illustration thereof is omitted.
Fig. 6 (a) is a front view showing a second modification of the stator, (b) is a left side view, (c) is a cross-sectional view A3-A3, and (d) is a right side view; the rear view, the top view, and the bottom view are the same as the front view, and therefore, the illustration thereof is omitted.
Fig. 7 (a) is a front view showing a third modification of the stator, (b) is a left side view, (c) is a cross-sectional view a4-a4, and (d) is a right side view; the rear view, the top view, and the bottom view are the same as the front view, and therefore, the illustration thereof is omitted.
Fig. 8(a) is an explanatory view of the postures of the rotor and the connecting member when the stator is a rigid body, (b) is an explanatory view of the postures of the rotor and the connecting member in the related art, (c) is a left side view of (b), (d) is a P-P sectional view of (b), and (e) is a right side view of (b).
(symbol description)
10.. uniaxial eccentric screw pump
A stator
Front end portion of 20x
20y.
A through hole
22e, 22f
Opening area
A rotor
50. power transmission mechanism part
Connecting part
Detailed Description
Hereinafter, 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 positive displacement pump. As shown in fig. 1, the uniaxial eccentric screw pump 10 is configured such that: the stator 20, the rotor 30, the power transmission mechanism 50, and the like are assembled in the housing 12. The housing 12 is a metal cylindrical member. A tubular end member 12a is attached to one end side of the housing 12 in the longitudinal direction. The end part 12a is provided with a first opening 14 a. In addition, a second opening 14b is provided on the outer peripheral portion of the housing 12. The second opening 14b communicates with the internal space of the housing 12 at an intermediate portion 12d located at a lengthwise intermediate portion of the housing 12.
The first opening 14a and the second opening 14b are portions that function as a suction port or a discharge port of the uniaxial eccentric screw pump 10, respectively. Further details are as follows: in the uniaxial eccentric screw pump 10 of the present embodiment, by rotating the rotor 30 in the normal direction, the fluid (fluid) can be pressurized and conveyed so that the first port 14a functions as the discharge port and the second port 14b functions as the suction port. In contrast, in the uniaxial eccentric screw pump 10, the rotor 30 is rotated in the reverse direction, whereby the fluid can be pressurized and conveyed so that the first port 14a functions as the suction port and the second port 14b functions as the discharge port.
The stator 20 is made of an elastomer typified by rubber, resin, or the like. As the stator 20, a cylindrical stator having a polygonal cross-sectional shape can be used in addition to a cylindrical stator. In the present embodiment, as shown in fig. 2, a stator having a substantially cylindrical external shape is used as the stator 20. The material of the stator 20 may be appropriately selected according to the type, characteristics, and the like of the fluid as the object to be conveyed by the uniaxial eccentric screw pump 10.
As shown in fig. 1, the stator 20 is disposed at a position adjacent to the end part 12 a. As shown in fig. 3, the stator 20 is configured such that an inner tube 20t is disposed inside a substantially cylindrical outer tube 20 s. A protruding portion 21 protruding outward in the radial direction is provided at an end portion of the inner tube 20 t. The protruding portion 21 protrudes in the longitudinal direction of the stator 20 more than the end portion of the outer tube 20s, and abuts against the end portion of the stator 20 in the longitudinal direction. The inner tube 20t is formed in a shape (counterbored shape) in which a spot facing process is performed in a spot facing portion 23 provided in the vicinity of an end portion. In the present embodiment, the example in which the spot facing 23 is provided in the stator 20 is illustrated, but the stator 20 may not necessarily be provided with the spot facing 23.
The stator 20 is fixed by: at the end position of the housing 12, the protruding portions 21 at both ends are sandwiched by the end part 12a and the housing 12, and the stay bolt 16 is installed between the end part 12a and the housing 12 and fastened, thereby fixing the stator 20.
The stator 20 has a through hole 22 extending in the axial direction for inserting a rotor 30, which will be described later, therethrough. The through-holes 22 are formed in a single-stage or multi-stage female screw shape of n pieces. In the present embodiment, the through-hole 22 is formed in a two-step female screw shape. As shown in fig. 2, the through-hole 22 has a substantially identical cross-sectional shape when viewed in cross section at any position in the longitudinal direction (axial direction). The cross-sectional shape of the through-hole 22 and the opening shape of the end are formed as follows: a long circle having a length in one direction (hereinafter, also referred to as "H direction") longer than a length in a direction intersecting the H direction (hereinafter, also referred to as "B direction").
As shown in fig. 2, the through-hole 22 is opened so as to form an oval opening region 22g in a cross section transverse to the axis of the stator 20. Further details are as follows: the cross-sectional shape of the through-hole 22 is a shape having curved portions 22a, 22b curved in an arc shape at both end sides in the H direction and intermediate portions 22c, 22d connecting the curved portions 22a, 22 b.
The intermediate portions 22c and 22d are provided with bulging portions 22e and 22f (substantially central portions of the intermediate portions 22c and 22d in the present embodiment). The bulging portions 22e and 22f bulge inward of the opening region 22g. More specifically, the bulging portions 22e and 22f bulge inward in the width direction of the through hole 22. In the present embodiment, the bulging portions 22e and 22f are formed to be gently curved from both end portions of the intermediate portions 22c and 22d toward a substantially central portion, and to project most inwardly of the opening region 22g at the substantially central portion. Thus, the opening region 22g has a so-called gourd-like shape in which a constricted portion is formed substantially at the center of the intermediate portions 22c and 22 d.
The bulging portions 22e and 22f are provided in at least a part of the region in the axial direction of the stator 20. In the present embodiment, the bulging portions 22e, 22f are provided substantially over the entire region in the axial direction of the stator 20.
The amount of projection of the projection portions 22e and 22f toward the inside of the opening region 22g may be the same at any position (region) in the axial direction of the stator 20, or may be different depending on the position. Specifically, the bulge portions 22e and 22f are preferably provided in the stator 20 in a region on the base end portion 20y side in preference to the tip end portion 20x side. In the present embodiment, the bulging portions 22e and 22f are formed so that the amount of bulging in the proximal end portion 20 y-side region is larger than the amount of bulging in the distal end portion 20 x-side region.
Specifically, as shown by the broken line in fig. 2(d), the bulging portions 22e and 22f provided on the distal end portion 20x side have a shape bulging inward of the opening region 22g. On the other hand, as shown by the solid line in fig. 2(d), the bulging portions 22e and 22f provided on the proximal end portion 20y side have a shape bulging further toward the inside of the opening region 22g than the bulging portions 22e and 22f provided on the distal end portion 20x side. The amount of projection of the projection portions 22e and 22f is adjusted to gradually increase from the distal end portion 20x side toward the proximal end portion 20y side.
As shown in fig. 1, the rotor 30 is a shaft body inserted into the through hole 22 of the stator 20. The rotor 30 is formed of a raw material such as metal, resin, or ceramic, and has a shape of n-1 single-stage or multi-stage male threads. In the present embodiment, the rotor 30 is formed in a single multistage male screw shape. The rotor 30 is a shaft body connected to a connecting member 62 described later in detail. The rotor 30 is eccentrically rotated by the power transmitted through the connection member 62.
More specifically, the rotor 30 rotates inside the stator 20 and revolves along the inner circumferential surface 24 of the stator 20 constituting the through hole 22. The rotor 30 is formed to have a substantially perfect circular cross-sectional shape when viewed from any position in the longitudinal direction. The rotor 30 is inserted into the through hole 22 formed in the stator 20 and is capable of eccentrically rotating freely inside the through hole 22.
When the rotor 30 is inserted into the stator 20, the outer peripheral surface 32 of the rotor 30 and the inner peripheral surface 24 of the stator 20 are in contact with each other along a tangent line therebetween. In this state, the fluid transfer path 40 is formed between the inner circumferential surface 24 of the stator 20 and the outer circumferential surface 32 of the rotor 30, which form the through-hole 22. When the length L of the lead (lead) of the stator 20 is set to the reference length S, the fluid transfer path 40 is a multi-stage (d-stage) flow path having a length d times the reference length S of the lead in the axial direction of the stator 20.
The fluid transfer path 40 extends spirally along the longitudinal direction of the stator 20 or the rotor 30. When the rotor 30 is rotated in the through hole 22 of the stator 20, the fluid transfer path 40 advances in the longitudinal direction of the stator 20 while rotating in the stator 20. Therefore, when the rotor 30 is rotated, the fluid can be sucked into the fluid transfer passage 40 from one end side of the stator 20, transferred toward the other end side of the stator 20 in a state of being enclosed in the fluid transfer passage 40, and discharged at the other end side of the stator 20. That is, when the rotor 30 is rotated in the forward direction, the fluid sucked through the second opening 14b can be pressurized and delivered and discharged through the first opening 14 a. When the rotor 30 is rotated in the reverse direction, the fluid sucked through the first opening 14a can be discharged through the second opening 14 b.
The power transmission mechanism 50 is provided to transmit power from a drive source (not shown) such as a motor provided outside the housing 12 to the rotor 30. The power transmission mechanism 50 includes a power connection portion 52 and an eccentric rotation portion 54. The power connection portion 52 is provided in the shaft housing portion 12c, and the shaft housing portion 12c is provided on one end side in the longitudinal direction of the housing 12, more specifically, on the opposite side of the stator 20 (hereinafter, also simply referred to as "base end side"). The eccentric rotation portion 54 is provided in the intermediate portion 12d formed between the shaft housing portion 12c and the stator 20.
The power connection unit 52 includes a drive shaft 56, and the drive shaft 56 is rotatably supported by two bearings 58a and 58 b. The drive shaft 56 projects outward from the closed portion on the base end side of the housing 12 and is connected to a power source. Therefore, by driving the power source, the drive shaft 56 can be rotated. A shaft seal device 60, for example, formed of a mechanical seal or a gland packing, is provided between the shaft housing portion 12c provided with the power connecting portion 52 and the intermediate portion 12d, so that the fluid as the object to be conveyed does not leak from the intermediate portion 12d side to the shaft housing portion 12c side.
The eccentric rotation portion 54 is a portion that connects the drive shaft 56 and the rotor 30 to each other through a connection member 62 so as to be able to transmit power. The coupling member 62 is coupled to the drive shaft 56 and the rotor 30 by a screw coupling or shrink fit coupling method. The connecting member 62 may be any member as long as it has flexibility in a direction intersecting the axial direction of the rotor 30. Specifically, the connection member 62 can use a flexible rod or a flexible wire. In the present embodiment, the flexible rod is used as the connecting member 62. Thus, the eccentric rotating portion 54 can transmit the rotational power transmitted via the drive shaft 56 to the rotor 30, thereby eccentrically rotating the rotor 30.
In the uniaxial eccentric screw pump 10, the rotor 30 is rotated in the normal direction by driving the drive source constituted by the motor or the like, so that the fluid can be sucked from the base end portion 20y side and pressurized and conveyed to the tip end portion 20x side, and the fluid can be discharged from the first opening 14a provided in the tip end member 12 a. Here, in the uniaxial eccentric screw pump 10, as described above, the stator 20 is provided with the bulging portions 22e and 22f. The bulging portions 22e and 22f bulge inward in the width direction at the longitudinal direction intermediate portion of the opening region 22g of the through hole 22. By providing the bulging portions 22e and 22f, the restoring force applied to the stator 20 from the connecting member 62 can be supported by the bulging portions 22e and 22f, and the posture deformation of the rotor 30 can be suppressed (see fig. 4). Therefore, in the uniaxial eccentric screw pump 10, the decrease in the pressure feed performance and the pulsation of the fluid due to the restoring force of the coupling member 62 can be suppressed to the minimum.
In the uniaxial eccentric screw pump 10 described above, the connecting member 62 may be any member as long as it has flexibility in a direction intersecting the axial direction of the rotor 30, and for example, a flexible rod, a cord, or the like can be used as appropriate. In addition to the flexible rod and the like, a coupling or the like having a characteristic of allowing flexure in a direction intersecting the axial direction and suppressing torsional deformation in the axial direction, such as a so-called flexible coupling, can be used as the connecting member 62.
In the uniaxial eccentric screw pump 10, the amount of expansion of the expansion portions 22e and 22f provided in the stator 20 is larger in the base end portion 20y side region than in the tip end portion 20x side region. With this configuration, the influence of the restoring force of the connecting member 62 on the posture of the rotor 30 can be minimized, and the adverse effect of the provision of the bulging portions 22e and 22f can be prevented.
That is, in the uniaxial eccentric screw pump 10, the amount of expansion of the expansion portions 22e, 22f is adjusted in accordance with the positions of the expansion portions 22e, 22f in the axial direction of the stator 20 in consideration of the following problems: due to the influence of the restoring force of the connecting member 62, there are problems such as a tendency that the rotor 30 is easily in a state of drooping toward the base end portion 20y side with the tip end portion 20x side of the stator 20 as a fulcrum, an increase in torque due to the provision of the bulging portions 22e and 22f, and an increase in wear speed due to deterioration of the lubricating property. Therefore, in the uniaxial eccentric screw pump 10, not only the problems of the decrease in the pressure feed performance, the pulsation of the fluid, and the like due to the restoring force of the coupling member 62 are suppressed, but also the effects of the decrease in the wear rate of the stator 20 and the like can be obtained.
In the stator 20 shown in the present embodiment, the amount of projection of the projection portions 22e and 22f gradually increases from the distal end portion 20x side toward the proximal end portion 20y side. Therefore, the amount of the bulge 22e and 22f provided in the stator 20 is larger in the base end portion 20y side region than in the tip end portion 20x side region, regardless of the position in the axial direction of the stator 20.
However, the present invention is not limited to this, and may be formed, for example, as follows: when the amount of projection of the projection portions 22e and 22f in the distal end portion 20x side region is set to a fixed amount α with reference to a predetermined position in the axial direction of the stator 20, and the amount of projection of the projection portions 22e and 22f in the proximal end portion 20y side region is set to a fixed amount β with reference to the predetermined position, a relationship of α < β is established. That is, the amount of projection of the projection portions 22e and 22f is not limited to be varied in a non-stepwise manner (steples) as in the present embodiment, and may be varied in a stepwise manner. When the amount of projection of the projection portions 22e and 22f is changed on the side of the distal end portion 20x and the side of the proximal end portion 20y with reference to the predetermined position, it is preferable to appropriately adjust the position or the amount of change in the amount of projection according to the conditions such as the liquid property and the pressure of the fluid to be treated.
In the present embodiment, the example is shown in which the amount of projection of the projection portions 22e and 22f is gradually increased from the distal end portion 20x side toward the proximal end portion 20y side, and the amount of projection of the projection portions 22e and 22f in the proximal end portion 20y side region is larger than the amount of projection in the distal end portion 20x side region.
Specifically, the amount of projection of the projection portions 22e and 22f may be increased stepwise (discontinuously) in each region from the distal end portion 20x side toward the proximal end portion 20y side. In addition, when it is not necessary to consider problems such as an increase in torque due to the provision of the bulging portions 22e and 22f, an increase in wear rate due to deterioration of the lubricating property, and the like, the bulging amounts of the bulging portions 22e and 22f may be formed so as to be substantially uniform over the entire region in the axial direction of the stator 20.
The bulging portions 22e and 22f are formed in the following shapes: a substantially mountain-like shape gradually protruding inward of the opening region 22g from both end portions of the intermediate portions 22c and 22d toward a substantially central portion, but the present invention is not limited thereto. That is, the bulging portions 22e and 22f may have shapes that bulge inward of the opening region 22g at the intermediate portions 22c and 22d, respectively.
Specifically, as shown in fig. 5, the bulging portions 22e and 22f may protrude in a semicircular shape toward the inside of the opening region 22g at substantially central portions of the intermediate portions 22c and 22 d. As shown in fig. 6, the bulging portions 22e and 22f may protrude from both end sides of the intermediate portions 22c and 22d by a substantially uniform amount toward a substantially central portion. Even if the bulging portions 22e and 22f have the shapes shown in fig. 5 and 6, as long as the bulging portions 22e and 22f can support the restoring force acting on the connecting member 62 of the stator 20, the posture deformation of the rotor 30 can be suppressed, and the reduction of the pressure-feed performance and the pulsation of the fluid due to the restoring force can be suppressed to the minimum.
In the present embodiment, the examples are shown in which the bulging portions 22e and 22f are provided at substantially central portions of the intermediate portions 22c and 22d, but the bulging portions 22e and 22f may be provided at positions that are offset from substantially central portions of the intermediate portions 22c and 22 d.
The stator 20 may have any shape as long as the cross-sectional shape of the through-hole 22 is oval. That is, the cross-sectional shape of the through-hole 22 is not limited to a track (loop) shape in which the arc-shaped curved portions 22a and 22b disposed to face each other are connected by the linearly extending intermediate portions 22c and 22d, and may be, for example, an elliptical shape or an elliptical coin shape. More specifically, as shown in fig. 7, the stator 20 may be a member or the like in which the bulging portions 22e and 22f are provided in the elliptical through-hole 22. Even in such a configuration, the restoring force acting on the connecting member 62 of the stator 20 is supported by the bulging portions 22e and 22f, whereby the posture deformation of the rotor 30 can be suppressed, and the reduction of the pressure-feed performance and the pulsation of the fluid can be suppressed to the minimum.
(availability in industry)
The present invention can be applied to all of the following uniaxial eccentric screw pumps: all uniaxial eccentric screw pumps of the type having a flexible connecting member oriented in a direction intersecting the rotor axis direction are employed in a power transmission mechanism portion for transmitting rotational power input from a drive source to a rotor.
Claims (5)
1. A uniaxial eccentric screw pump is characterized in that,
the disclosed device is provided with:
a rotor composed of a male screw type shaft body,
a stator composed of an outer cylinder and an elastic body having a female screw type through hole into which the rotor can be inserted, and
a power transmission mechanism portion for transmitting rotational power input from a drive source to the rotor;
the power transmission mechanism unit includes a connection member having flexibility in a direction intersecting with an axial direction of the rotor, and is capable of eccentrically rotating the rotor while rotating inside the stator and revolving along an inner circumferential surface of the stator;
the through hole is opened so as to form an oblong opening region in a cross section intersecting an axis of the stator;
the thickness of the elastic body is thinner on the outer side in the longitudinal direction of the opening region of the through hole and thicker on the outer side in the width direction;
a bulge portion formed in the entire region from one end to the other end of the through hole, the bulge portion bulging toward the inside in the width direction of the opening region at a longitudinal direction intermediate portion of the opening region, and a bulging amount of the bulge portion is the same over the entire region or a bulging amount on the base end portion side is larger than a bulging amount on the tip end portion side;
the connecting component is a flexible rod or a flexible wire.
2. The uniaxial eccentric screw pump of claim 1,
the stator has a base end portion on the driving source side and a tip end portion on the opposite side of the driving source;
the bulge portion is provided at least in a region on the base end portion side of the stator.
3. Uniaxial eccentric screw pump according to claim 1 or 2,
the stator has a base end portion on the driving source side and a tip end portion on the opposite side of the driving source;
the amount of bulging of the bulging portion in the base end portion side region is larger than the amount of bulging in the tip end portion side region.
4. Uniaxial eccentric screw pump according to claim 1 or 2,
the stator has a base end portion on the driving source side and a tip end portion on the opposite side of the driving source;
the amount of bulging of the bulging portion gradually increases from the distal end portion side toward the base end portion side.
5. The uniaxial eccentric screw pump of claim 3,
the stator has a base end portion on the driving source side and a tip end portion on the opposite side of the driving source;
the amount of bulging of the bulging portion gradually increases from the distal end portion side toward the base end portion side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-019036 | 2015-02-03 | ||
| JP2015019036A JP6761980B2 (en) | 2015-02-03 | 2015-02-03 | Uniaxial eccentric screw pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105840494A CN105840494A (en) | 2016-08-10 |
| CN105840494B true CN105840494B (en) | 2021-06-22 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510890515.8A Active CN105840494B (en) | 2015-02-03 | 2015-12-04 | Single-shaft eccentric screw pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6761980B2 (en) |
| KR (1) | KR102439444B1 (en) |
| CN (1) | CN105840494B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6761980B2 (en) * | 2015-02-03 | 2020-09-30 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
| CN111075710B (en) * | 2019-12-25 | 2021-11-26 | 黄山黄泵单螺杆泵有限公司 | 3-to-4-equal-wall-thickness single-screw pump |
| JP7138382B1 (en) | 2022-01-18 | 2022-09-16 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
| JP7138383B1 (en) * | 2022-01-18 | 2022-09-16 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
| JP7199128B1 (en) * | 2022-01-18 | 2023-01-05 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4397619A (en) * | 1979-03-14 | 1983-08-09 | Orszagos Koolaj Es Gazipari Troszt | Hydraulic drilling motor with rotary internally and externally threaded members |
| GB2272730A (en) * | 1992-11-11 | 1994-05-25 | Arnold Jaeger | Eccentric screw pump |
| CN201843778U (en) * | 2010-11-04 | 2011-05-25 | 韩全伟 | Iso-wall-thickness rubber stator screw pump |
| JP2012154215A (en) * | 2011-01-25 | 2012-08-16 | Heishin Engineering & Equipment Co Ltd | Single-shaft eccentric screw pump |
| JP2016142188A (en) * | 2015-02-03 | 2016-08-08 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4086270B2 (en) * | 2000-11-13 | 2008-05-14 | 株式会社リコー | Powder pump and image forming apparatus having the powder pump |
| DE10243675B3 (en) * | 2002-09-20 | 2004-01-29 | Netzsch-Mohnopumpen Gmbh | Eccentric screw pump with exchange unit |
-
2015
- 2015-02-03 JP JP2015019036A patent/JP6761980B2/en active Active
- 2015-12-04 CN CN201510890515.8A patent/CN105840494B/en active Active
-
2016
- 2016-02-02 KR KR1020160012741A patent/KR102439444B1/en active IP Right Grant
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4397619A (en) * | 1979-03-14 | 1983-08-09 | Orszagos Koolaj Es Gazipari Troszt | Hydraulic drilling motor with rotary internally and externally threaded members |
| GB2272730A (en) * | 1992-11-11 | 1994-05-25 | Arnold Jaeger | Eccentric screw pump |
| DE4237966A1 (en) * | 1992-11-11 | 1994-05-26 | Arnold Jaeger | Eccentric screw pump |
| CN201843778U (en) * | 2010-11-04 | 2011-05-25 | 韩全伟 | Iso-wall-thickness rubber stator screw pump |
| JP2012154215A (en) * | 2011-01-25 | 2012-08-16 | Heishin Engineering & Equipment Co Ltd | Single-shaft eccentric screw pump |
| JP2016142188A (en) * | 2015-02-03 | 2016-08-08 | 兵神装備株式会社 | Uniaxial eccentric screw pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6761980B2 (en) | 2020-09-30 |
| KR20160095632A (en) | 2016-08-11 |
| KR102439444B1 (en) | 2022-09-02 |
| JP2016142188A (en) | 2016-08-08 |
| CN105840494A (en) | 2016-08-10 |
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