JP2000320452A - Single thread pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a single thread pump, simplify the configuration, prevent wear of a rotor and a stator, and to maintain highly precise and stable performance. SOLUTION: Crankshafts 4a, 4b are attached to both ends of a rotor 3, while the crankshafts 4a, 4b are held by bearing 7a, 7b. By transmitting the rotating power to the crank shaft 4b via a coupling 9 arranged outside a stator 2, the rotor 3 makes eccentric rotation. The inside of the stator 2 is made of a metallic material. Suction ports 5, 6 are attached to the both end side surfaces of the stator 2 perpendicular to the side surfaces, in order to suck or discharge the fluid therefrom.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a single screw pump, and more particularly, to a single screw pump which moves a fluid by rotating a rotor.

[0002]

2. Description of the Related Art As one form of a pump for moving a fluid, there is a single screw pump for moving a fluid by rotating a torsional rotor housed in a stator.

FIG. 4 is a sectional view showing the configuration of a conventional single screw pump 100. As shown in FIG. Single screw pump 100
The rotor 101 has a single screw twist shape, the inside of which is made of an elastic material, has a double screw twist shape, and is attached to the stator 102 that accommodates the rotor 101 and is attached to the stator 102 to suck fluid or A suction port 108 for discharging, universal joints 104a and 104b for transmitting power to an eccentric rotation shaft of the rotor 101, a coupling rod 105, and a universal joint 10.
4b, a drive shaft 107 for transmitting rotational power to the rotary shaft 4b, a casing 103 accommodating the universal joints 104a, 104b and the coupling rod 105, a shaft sealing device 106 for preventing leakage of the fluid from the casing 103, and a suction of the fluid attached to the casing 103. Alternatively, it is constituted by a suction port 109 for performing discharge.

[0004] The rotational power transmitted to the drive shaft 107 is transmitted to the universal joint 104b.
The power is transmitted to the eccentric rotation shaft of the rotor 101 via the coupling rod 105 and the universal joint 104a. The rotor 101 to which power has been transmitted to the eccentric rotation shaft performs eccentric rotation while its position is maintained by the stator 102.

[0005] Inside the stator 102, a rotor 101 is provided.
A closed portion is formed by a combination of the single screw and the double screw of the stator 102, and the closed portion moves inside the stator 102 by the eccentric rotation of the rotor 101, and a fluid flows through the inside of the stator 102 by the movement of the closed portion. Moving. Here, when rotating the rotor 101 in the forward direction, the fluid taken in from the suction port 108 is sent to the casing 103 by the movement of the closing portion, and the fluid sent to the casing 103 is
After passing through the inside of 3, it is discharged from the suction port 109.

[0006]

However, in the conventional single screw pump 100, the universal joints 104a and 104b and the coupling rod 1 are attached to the stator 102.
Since the casing 103 accommodating the pump 05 is connected to the motor 103 for transmitting power to the drive shaft 107 outside the casing 103, there is a problem that the size of the entire pump becomes very large.

[0007] A rotor 10 having no bearings at both ends.
In (1), in order to flexibly follow the eccentric rotation of the rotor 101 and appropriately transmit power to the rotor 101, a complicated connection configuration using universal joints 104a and 104b and a coupling rod 105 is required.

Further, since the rotor 101 has a configuration in which the universal joint 104a is connected to one end face thereof and has no bearing, the rotor 101 itself is eccentrically rotated while its position is held by the stator 102. Thus, there is also a serious problem that the stator 102 and the rotor 101 are always slid, thereby the stator 102 is worn, and the performance of the pump is reduced in proportion to the operation time.

Further, since the rotor 101 and the stator 102 are always slid, there is also a problem that abrasion powder worn by the sliding is mixed into the fluid. Further, since the rotor 101 and the stator 102 are always slidable, a metal material cannot be used for the stator 102, and the accuracy of the pump cannot be improved.

The fluid is a universal joint 1
Since the inner joints 104a and 104b and the coupling rod 105 are moved inside the casing 103, the abrasion powder generated by the sliding at the joint between the universal joints 104a and 104b and the coupling rod 105 is mixed into the fluid. There is also a problem that it will.

Further, the fluid moves inside the casing 103 in which the universal joints 104a and 104b and the coupling rod 105 are stored, and
There is also a problem that the fluid remains in the casing 103 because no pushing force of the fluid is generated in the inside of the casing 103.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and has a small size, a simple structure, does not cause wear of a rotor and a stator, and can maintain high precision and stable performance. It is intended to provide a pump.

[0013]

According to the present invention, in order to solve the above problems, in a single screw pump in which a fluid is moved by rotation of a rotor housed in a stator, semicircles are arranged at both ends of a square. A stator in which a cavity having a cross-sectional shape is formed while being twisted, a rotor housed inside the cavity of the stator, having a torsional shape, and having a circular cross-sectional shape, and one at each end of the rotor. A single screw pump comprising: a crankshaft to be attached; and bearings attached to both ends of the stator to hold the crankshaft.

Here, the stator houses the rotor, the rotor performs eccentric rotation in the stator, the crankshaft applies eccentric rotation to the rotor, and the bearing holds the crankshaft.

[0015]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional configuration diagram showing a configuration of a single screw pump 1 in the present invention.

The single screw pump 1 has a double screw structure inside, a stator 2 in which a fluid moves inside, a single screw structure, and a rotor 3 arranged in a cavity inside the stator 2. , Arranged outside both ends of the stator 2.
Suction ports 5 and 6 connected to the inside, a crankshaft 4a attached to both ends of the rotor 3 to give eccentric rotation to the rotor 3,
4b, a bearing 7a for holding the crankshaft 4a, a bearing 7b for holding the crankshaft 4b, shaft sealing devices 8a and 8b for preventing leakage of the fluid, the prime mover 10 which is rotational power, and the rotational power of the prime mover 10 It is constituted by a coupling 9 for transmission.

The stator 2 has a cylindrical shape, and a cavity having a cross-sectional shape formed by arranging a semicircle at both ends of a square is arranged inside the stator 2 while twisting at an angle of 0 ° or more and 1440 ° or less. I have. Suction outlets 5 and 6 each having a cylindrical shape are attached to side surfaces of both end portions in the longitudinal direction of the stator 2 perpendicularly to the side surfaces.
Is connected to the cavity inside the stator 2. In the case of FIG. 1, the suction port 5 has a torsion angle 0 of the stator 2.
The suction port 6 is arranged at a twist angle of 1080 ° to 1440 ° of the stator 2.
It is arranged on the side surface in the following range. Various types of metal materials are used inside the cavity of the stator 2 according to the purpose. For example, when the purpose is corrosion resistance, stainless steel, stainless steel, or the like is used. , Nitrided steel, die steel, ceramic sprayed steel and the like.
Of course, an elastic material may be used as in the conventional case. And the rotor 3 is accommodated in such a cavity inside the stator 2.

The rotor 3 is made of a metal material. For example, stainless steel, stainless steel or the like is used for corrosion resistance, and nitrided steel is used for wear resistance.
Die steel, ceramic sprayed steel or the like is used. The rotor 3 has a continuous and uniform twist structure. In the case of the present embodiment, the rotor 3 has a twist structure having an angle of 0 ° or more and 1440 ° or less.

Crankshafts 4a and 4b are attached to both ends of the rotor 3 in the longitudinal direction, and are connected to each other so that the rotor 3 can rotate with respect to the crankshafts 4a and 4b about the rotation center of the rotor 3. You.

When the rotor 3 is arranged inside the stator 2, a part of the crankshafts 4a and 4b is arranged outside the stator 2, and the crankshaft 4a is
The crankshaft 4b is held by a bearing 7b arranged outside the stator 2 while the crankshaft 4b is held by a bearing 7a arranged outside the stator 2. Shaft sealing devices 8a and 8b are arranged at the contact points between the crankshafts 4a and 4b and the stator 2 to prevent leakage of fluid from inside the stator 2 at these contact points. The coupling 9 is connected to the crankshaft 4b, and the prime mover 10 is connected to the coupling 9.

The rotational power provided by the prime mover 10 is transmitted to the coupling 9, and the rotational power transmitted to the coupling 9 is transmitted to the crankshaft 4b. The crankshaft 4b converts the applied rotational power into eccentric rotation. And transmit it to the rotor 3. Then, the rotor 3 to which the eccentric rotation is given by the crankshaft 4b performs the eccentric rotation inside the stator 2 while being held by the crankshafts 4a and 4b.

Next, the operation of the rotor 3 inside the stator 2 will be described. 2 and 3 show the stator 2 of FIG.
It is AA sectional drawing in. The cross section of the stator 2 has a shape in which semicircles are arranged at both ends of a square, and the cross section of the rotor 3 is circular. The diameter of the cross section of the stator 2 in the y direction is about twice the diameter of the rotor 3 and has a clearance of about 0.1 mm or less with respect to the rotor 3. The x-direction diameter of the cross section of the stator 2 is
And has a clearance of about 0.1 mm or less with respect to the rotor 3.

The rotor 3 has a rotor rotation center 3a, and the rotor 3 rotates about the rotor rotation center 3a with respect to the crankshafts 4a and 4b in the rotation direction 3 of the rotor.
Rotate in the direction of b (counterclockwise). Further, the rotor rotation center 3a is rotated clockwise around the center coordinates of the stator 2 around the center coordinates ((x, y) = (0, 0)) of the stator 2 by the rotation of the crankshafts 4a and 4b. I do.

FIG. 2A shows a state in which the rotor 3 is arranged at the uppermost part ((x, y) = (0, y10)) of the stator 2, and the rotor rotation center 3a is ( x,
y) = (0, y1).

Next, when the crankshaft 4b rotates and the rotation is transmitted to the rotor 3, the rotor rotation center 3a rotates clockwise around the center coordinate of the stator 2 according to the movement of the crankshaft 4b. FIG. 2B shows the positional relationship between the rotor 3 and the stator 2 displaced by the rotational motion transmitted to the rotor 3 from the crankshaft 4b. The rotor rotation center 3a displaced by the clockwise rotation of the crankshaft 4b moves to the position (x2, y2),
The rotor 3 reaches (0, y11) while rotating in the rotation direction 3b of the rotor. Further, as shown in FIG. 2 (c), the rotor rotation center 3a reaches (x3, 0) by clockwise rotation, and at the same time, the rotor 3 rotates in the rotor rotation direction 3b (0, 0). Reach the position. Then, as shown in FIG. 2D, the rotor rotation center 3a reaches (x2, -y2) and the rotor 3 reaches (0, -y11) by the same rotational movement. Thereafter, as shown in FIG. 3A, the rotor rotation center 3a is set to (0,-).
y1), and the rotor 3 reaches (0, -y10), which is the lowermost part of the stator 2. As shown in FIGS. 3B, 3C and 3D, the rotor 3 reaching the lowermost portion of the stator 2
The rotor rotation center 3a is defined as (-x2, -y2), (-x
3, 0) and (−x2, y2), and move the position of the rotor 3 to (0, −y11), (0, 0), (0, y1).
1), and then reaches the initial position shown in FIG.

The space formed between the stator 2 and the rotor 3 shown in FIG.
(B) Although the operation is completely closed by the operations of (c), (d) and FIG. 3 (a), the above operation can be similarly observed in other cross sections arranged with twist. ,
When the stator 2 and the rotor 3 are viewed three-dimensionally, FIG.
The space formed between the stator 2 and the rotor 3 is spirally arranged. Further, since this spiral space is constituted by the rotor 3 having a single screw structure and the stator 2 having a double screw structure inside, the spiral space is closed in a certain range. Specifically, the closing portion is formed in a range where the rotor 3 is twisted by 360 °. In the case of the present embodiment, a total of two hydraulic locks are formed inside the stator 2 by the closing portion.
Is configured.

By the operations described above with reference to FIGS. 2B, 2C, 2D and 3A, the closing portion moves inside the stator 2, thereby moving the fluid.

Referring to FIG. 1, the fluid introduced from the suction port 5 fills a closed portion, which is a spiral space closed in a certain range formed by the stator 2 and the rotor 3, and 2 (b), (c), (d) and FIG.
By the operation of (a), the closing portion moves, whereby the fluid filled in the closing portion is pushed out from the suction port 6. Also, during the operations of FIGS. 2 (b), (c), (d) and 3 (a), the fluid continues to be introduced from the suction port 5, and the introduced fluid is as shown in FIG. 3 (a). (B) and (c) of FIG. 3 fill the space surrounded by the stator 2 and the rotor 3 shown in FIG.
The fluid in this space is pushed out from the suction port 6 by the operation of (d) and FIG.

As described above, the fluid introduced from the suction port 5 is continuously blocked by the infinite piston motion caused by the eccentric rotation of the rotor 3 inside the stator 2, and the blocked fluid is It will be discharged from the suction port 6 without pulsation.

As described above, in this embodiment, a complicated universal joint mechanism as conventionally used is not used,
By mounting the crankshafts 4a and 4b at both ends of the rotor 3 and holding the crankshafts 4a and 4b with the bearings 7a and 7b, the rotor 3 is eccentrically rotated. Therefore, the whole pump can be simplified and the size can be reduced. Can be achieved.

Further, a crankshaft 4a is provided at both ends of the rotor 3.
4b and the crankshafts 4a, 4b at both ends are held by the bearings 7a, 7b, so that the rotation of the rotor 3 is stable, and it is possible to perform quiet, high-speed rotor rotation.

Further, a crankshaft 4 is provided at both ends of the rotor 3.
a, 4b, and the crankshafts 4a, 4b at both ends are held by bearings 7a, 7b.
There is no sliding between the rotor and the rotor 3, the wear of the stator 2 can be suppressed, and the running cost can be reduced.

Further, since there is no sliding between the stator 2 and the rotor 3 and the wear of the stator 2 can be suppressed, the friction powder generated by the sliding between the stator 2 and the rotor 3 is prevented from being mixed into the fluid. be able to.

Further, a crankshaft 4 is provided at both ends of the rotor 3.
Since a and b are attached and the position of the rotor 3 is held from both ends, the pulsation of the fluid can be reduced and the quantitativeness can be improved.

Further, suction ports 5, 6 are provided at both ends of the stator 2.
Is provided, so that the fluid does not pass through the universal joint which is the rotary power transmission unit as in the related art, and the abrasion powder of the rotary power unit does not mix with the fluid.

Further, suction outlets 5 are provided at both ends of the stator 2.
6, the fluid passes only through the inside of the stator 2, and the problem of the fluid remaining as in the prior art does not occur. The eccentric rotation of the rotor 3 is controlled by the crankshaft 4a,
4b, and power transmission to the crankshaft 4b is performed by the coupling 9 arranged outside the stator 2, so that the pump configuration can be simplified.

Further, since there is no sliding between the stator 2 and the rotor 3 and a metal material can be used for the stator 2, the clearance between the stator 2 and the rotor 3 can be kept constant and the pump performance can be maintained stably. It becomes possible.

In this embodiment, the stator 2 and the rotor 3 have a twisted structure having an angle of 0 ° or more and 1440 ° or less.
By these two hydraulic locks
However, a high-pressure configuration in which the length of the stator 2 and the rotor 3 is further increased to increase the number of hydraulic locks may be adopted.

Conversely, a low pressure configuration may be adopted in which the lengths of the stator 2 and the rotor 3 are reduced and the number of hydraulic locks is reduced to one.

[0040]

As described above, in the present invention, the crank is mounted on both ends of the rotor and the eccentric rotation of the rotor is performed by holding the crankshaft with bearings, so that the entire pump can be simplified. It is possible to reduce the size.

Further, since the crankshafts are attached to both ends of the rotor, the rotation of the rotor is stable, quiet,
High-speed rotor rotation can be performed. In addition, since the crankshaft was attached to both ends of the rotor,
There is no sliding between the stator and the rotor, the wear of the stator can be suppressed, and the running cost can be reduced.

Also, there is no sliding between the stator and the rotor,
Since the wear of the stator can be suppressed, it is possible to prevent frictional powder generated by sliding between the stator and the rotor from being mixed into the fluid.

Further, since the crankshafts are attached to both ends of the rotor, the rotation of the rotor is stabilized, the pulsation of the fluid can be reduced, and the quantitativeness can be improved.
In addition, since the suction ports are provided at both ends of the stator, the abrasion powder of the rotating power unit does not mix into the fluid.

Further, since the suction ports are provided at both ends of the stator, the fluid passes only through the inside of the stator, so that the problem of the fluid remaining as in the conventional case does not occur. Also, the eccentric rotation of the rotor is performed by the crankshaft,
Since the power transmission to the crankshaft is performed by the coupling disposed outside the stator, the configuration of the pump can be simplified.

Further, since there is no sliding between the stator and the rotor and a metal material is used for the stator, the clearance between the stator and the rotor can be kept constant and the pump performance can be maintained stably.

[Brief description of the drawings]

FIG. 1 is a sectional view showing the configuration of a single screw pump according to the present invention.

FIG. 2 is a sectional view taken along line AA of the stator of FIG.

FIG. 3 is a sectional view taken along line AA in the stator of FIG. 1;

FIG. 4 is a sectional configuration diagram showing a configuration of a conventional single screw pump.

[Explanation of symbols]

1 ... single screw pump, 2 ... stator, 3 ... rotor,
4a: crankshaft, 4b: crankshaft, 5: suction outlet, 6: suction outlet, 7a: bearing, 7b: bearing, 9.
··Coupling

Claims (5)

[Claims] 1. A single screw pump in which a fluid is moved by rotation of a rotor housed in a stator, wherein a cavity having a cross-sectional shape in which a semicircle is arranged at both ends of a square is arranged while being twisted. A rotor that is housed inside the cavity of the stator, has a twisted shape, and has a circular cross-sectional shape; a crankshaft that is attached to each end of the rotor one by one; A single screw pump, comprising: a bearing for holding a crankshaft; 2. The single screw pump according to claim 1, wherein the stator has suction ports at both ends thereof for sucking or discharging the fluid. 3. The single screw pump according to claim 1, wherein a coupling for transmitting rotational power to one of the crankshafts is provided outside the stator. 4. The single screw pump according to claim 1, wherein the stator is made of a metal material. 5. The method according to claim 1, wherein the stator and the rotor have an angle of zero.
The twisting portion has a twist of not less than 1 ° and not more than 1440 °, and the suction portion is disposed at a portion of the stator having a twist angle of 0 ° or more and 360 ° or less and a portion having a twist angle of 1080 ° or more and 1440 ° or less. Item 1. A single screw pump according to Item 1.