KR101724657B1

KR101724657B1 - Twin circle positive-displacement pump

Info

Publication number: KR101724657B1
Application number: KR1020160170652A
Authority: KR
Inventors: 최병철
Original assignee: 최병철
Priority date: 2016-12-14
Filing date: 2016-12-14
Publication date: 2017-04-07

Abstract

The present invention relates to a twin circle positive-displacement pump. The twin circle positive-displacement pump comprises: a housing being vertically symmetric and having an upper displacement chamber and a lower displacement chamber communicating with each other; a rotary shaft including an upper and a lower rotary shaft to rotate in the upper and the lower displacement chamber in opposite directions; an eccentric rotor including an upper and a lower eccentric rotor into which the upper and the lower rotor are eccentrically inserted to be rotated; a cylinder member accommodating the upper and the lower eccentric rotor therein and including an upper and a lower cylinder member to perform an inscription motion in the upper and the lower displacement chamber and a partition membrane to connect the upper and the lower cylinder member to link the upper and the lower cylinder member to each other; and a flexible bearing disposed between the upper cylinder member and the upper eccentric rotor and between the lower cylinder member and the lower eccentric rotor to reduce friction and an impact applied to the cylinder member by rotation of the eccentric rotor. A cross section of the eccentric rotor is circular. A cross section of the flexible bearing is circular to come in contact with an outer circumferential surface of the eccentric rotor. A cross section of an inner circumferential surface of at least one among the upper and the lower cylinder member is elliptical to form an available space between the inner circumferential surface of the elliptical cylinder member and the flexible bearing.

Description

Twin circle positive-displacement pump < RTI ID = 0.0 >

The present invention relates to a volume pump, and more particularly, to a two-dimensional volumetric pump capable of minimizing a center-to-center distance deviation between upper and lower rotors which are inscribed in mutually opposite directions, thereby ensuring smooth driving.

The pump is a mechanical device that transports fluid of a liquid or a gas through a pipe by a pressure action, or pushes a fluid in a low-pressure container through a pipe to a high-pressure container.

Pumps can be classified as reciprocating pumps, rotary (rotary) pumps, centrifugal pumps, axial pumps, friction pumps, etc. when structurally classified.

Among these pumps, the rotary pump is configured such that the piston acting on the piston acts on the piston while the piston acts on the piston by the rotor (rotor), and can be used for various purposes, and is widely used as a hydraulic pump for automatic control .

There are various rotary pumps according to their structures. Among them, Patent Documents 1 to 3 are technologies related to twin or tandem rotary pumps.

Patent Document 1 discloses that the upper rotor is disposed in the upper volume chamber and the lower rotor is disposed in the lower volume chamber in a state where the upper rotor and the lower rotor are connected by the diaphragm so that the upper rotor rotates in an eccentric inscribed circle A tandem rotary pump in which a lower rotor in a lower volume chamber performs an eccentric inscribed circle movement in a direction opposite to an upper rotor so that fluid is sucked into an intake port of the housing and discharged through a discharge port, Wherein the rotor is mounted eccentrically to the upper shaft and the upper rotor includes an outer cylindrical member which performs an inscribed circle movement in the upper volume chamber and an intermediate cylindrical member which is disposed between the outer cylindrical member and the eccentric cam rotor, An outer rolling member is mounted on the inner circumferential surface of the member and an inner rolling member is mounted on the outer circumferential surface of the eccentric cam rotator to reduce friction And the lower rotor is configured to be symmetrical with the upper rotor.

In Patent Document 2, an upper volume chamber and a lower volume chamber are formed in a pumping block having an intake port and a discharge port, an upper rotor is disposed in the upper volume chamber, a lower rotor is disposed in the lower volume chamber, The upper end of the diaphragm is brought into close contact with the upper rotor, the lower end of the diaphragm is in close contact with the lower rotor, the upper shaft is eccentrically mounted to the upper rotor and the lower shaft is eccentrically mounted to the lower rotor, And the upper and lower support members press the upper and lower support members, which are fitted to the upper and lower ends of the vertical hole, so that the upper head and the lower head are fixed to the mounting groove formed at the upper and lower ends of the body, And the lower head portion are respectively fitted and fitted.

Patent Document 3 discloses a case; A first gear portion accommodated in the case and rotating together with a first head portion for pressing fluid or sludge; A third gear portion that is positioned below the first gear portion and rotates together with a second head portion that is directly or indirectly engaged with the first gear portion and pressurizes fluid or sludge; A pumping unit operatively associated with the third gear unit for pumping oil; And a transfer part connected to the pumping part and extending in the direction of the first gear part to supply oil to the first gear part.

The problems of the conventional tandem rotary pump will be described with reference to FIGS. 1, 2 and 3. FIG. Fig. 1 shows a perspective view of a general rotary pump. Fig. 2 shows an operating state of the upper and lower cylindrical members according to one rotation of the upper and lower eccentric rotors in the rotary pump shown in Fig. 1. Fig. Sectional view showing a change in the center distance of the upper and lower eccentric rotors according to the operating state of the upper and lower eccentric rotors.

1, the rotary pump includes a housing 1 having an upper volume chamber 16a and a lower volume chamber 16b which are vertically symmetrical and communicated with each other, And a lower rotor accommodated in the lower volumetric chamber and rotating in a direction opposite to the upper rotor.

At this time, the upper rotor and the lower rotor are symmetrical with respect to each other and have the same structure.

The upper rotor includes an upper cylindrical member 13a and a lower eccentric rotor 11a rotatably installed in the upper cylindrical member. The lower rotor includes a lower cylindrical member 13b and a lower eccentric rotor 11b rotatably installed inside the lower cylindrical member.

However, the upper cylindrical member constituting the upper rotor and the lower cylindrical member constituting the lower rotor are connected to each other by the diaphragm 13c, and the upper rotor and the lower rotor can be inscribed in opposite directions to each other.

At this time, the upper and lower volume chambers have a circular shape, and the outer and inner circumferential surfaces of the upper and lower cylindrical members are also circular. The outer peripheral surface of the upper and lower eccentric rotors is also circular.

Meanwhile, the upper and lower eccentric rotors are inserted and fixed to rotary shafts (14a, 14b) for transmitting rotational power from the guide portions. That is, the rotary shaft is inserted eccentrically to one side rather than the center of the upper and lower eccentric rotors, and is coupled to each other using a shaft coupling element such as a key.

In the case of such a structure, intermediate cylindrical members 12a and 12b are inserted and interposed between the respective eccentric rotors and the respective cylindrical members to reduce friction generated between them. As the intermediate cylindrical member, a rolling means using a ball or a rolling member is usually used.

Fig. 2 (a) is a sectional view showing a state in which the rotating shaft is aligned in line with the diaphragm in an initial state, Fig. 2 (b) is a sectional view showing the state in which the upper rotating shaft rotates 90 degrees clockwise, FIG. 2 (c) is a cross-sectional view showing a state in which the upper rotary shaft rotates 180 degrees in the clockwise direction and the lower rotary shaft rotates 180 degrees in the counterclockwise direction, FIG. 2 (d) 270 degrees in the clockwise direction, and 270 degrees in the counterclockwise direction in the lower rotation axis.

As described above, when the center of each eccentric rotor is located on the extension line connecting the upper and lower rotation shafts as shown in Figs. 2 (a) and 2 (c) The distances between the centers of the upper and lower eccentric rotors are different when the centers of the eccentric rotors are not located on the extension line connecting the upper and lower rotary shafts as shown in Figs. 2 (b) and 2 (d). For reference, it can be seen that the distance between the centers of the eccentric rotors is the longest in the case of Figs. 2 (b) and 2 (d).

3, the rotation of the two eccentric rotors 11a and 11b causes the two cylindrical members 13a and 13b to move from the inside to the inside of each of the volume chambers 13a and 13b, 3 (a), the distance between the centers of the two cylindrical members (red line D1) and the distance between the centers of the two cylindrical members in a direction opposite to each other as shown in Fig. 3 (b) (Red line, D2) of the two cylindrical members are different from each other at the point where the two cylindrical members are rotated by 90 degrees, and the difference between D1 and D2 becomes larger, the two cylindrical members connected by a diaphragm of a certain length are installed inside the cylindrical member The eccentric rotor and the rotary shaft receive a resistance and can not smoothly rotate.

That is, the upper outer circumferential surface of the eccentric rotor presses the upper inner circumferential surface of the cylindrical member, so that an impact is generated. At the same time, the eccentric rotor is caught by the inner circumferential surface of the cylindrical member,

1) Korea Patent No. 10-0801247 2) Korean Patent No. 10-0876547 3) Korean Patent No. 10-1621067

SUMMARY OF THE INVENTION Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and it is an object of the present invention to minimize the deviation in the distance between the centers of the upper and lower eccentric rotors, And to provide a two-dimensional volumetric pump capable of achieving this.

That is, in the process of operation of the upper eccentric rotor and the lower eccentric rotor, the error of the center distance between the two eccentric rotors is reduced to smoothly operate, thereby maintaining a constant output and improving the durability of the components And a pump for supplying the pump.

According to an aspect of the present invention, there is provided a dual-use volumetric pump comprising: a housing having an upper volumetric chamber and a lower volumetric chamber which are symmetric with each other and communicate with each other; A rotary shaft including an upper rotary shaft and a lower rotary shaft which rotate in opposite directions in the upper and lower volume chambers respectively; An eccentric rotor including an upper eccentric rotor and a lower eccentric rotor in which the upper rotary shaft and the lower rotary shaft are eccentrically inserted and rotated, respectively; An upper cylindrical member and a lower cylindrical member accommodating therein the upper eccentric rotor and the lower eccentric rotor, respectively, and inserting and moving in the upper and lower volume chambers, respectively, and a lower cylindrical member and a lower cylindrical member, A cylindrical member including a diaphragm for interlocking with each other; And a flexible bearing provided between the upper cylindrical member and the upper eccentric rotor and between the lower cylindrical member and the lower eccentric rotor to reduce friction and impact on the cylindrical member due to rotation of the eccentric rotor, Wherein a cross section of the eccentric rotor is circular and the flexible bearing is circular in cross section so as to contact the outer peripheral surface of the eccentric rotor, and at least one of the upper cylindrical member and the lower cylindrical member has an elliptical cross- A clearance may be formed between the inner peripheral surface of the member and the flexible bearing.

Here, the elliptic cylindrical member may have an elliptical shape having a vertical axis in a vertical direction so that a clearance space is formed on the upper side in an upright state, or an elliptical shape having a long axis so that a clearance space is formed on a side surface thereof.

At this time, the radius of curvature of the upper inner circumferential surface of the elliptical cylindrical member whose longitudinal axis is vertical may be smaller than the radius of curvature of the eccentric rotor.

And the radius of curvature of the side surface of the elliptical cylindrical member whose major axis is horizontal may be smaller than the radius of curvature of the eccentric rotor.

In addition, the rolling means of the flexible bearing may be any one of a ball, a roller, a hollow pin, and a hollow cutting pin, and a retainer for maintaining an interval between the inner ring and the outer ring and the rolling means for supporting the inside and outside of the rolling means, (Flexible) material.

The inner ring and the outer ring may be cylindrically shaped or may have a shape in which the strap is wound in a spiral shape.

The rolling means of the flexible bearing may be formed of a cylindrical and flexible resin material.

According to the present invention constructed as described above, the eccentric rotor and the flexible bearing are formed in an elliptic shape, thereby forming a clearance space between the flexible bearing and the inner circumferential surface of the cylindrical member, thereby changing the distance between the centers of the two eccentric rotors So that the output of the pump can be prevented from being lowered.

In other words, since the eccentric rotor can be smoothly operated without being caught by the cylindrical member by reducing the center distance error of the two eccentric rotors, the present invention has an advantage that the durability of the components can be improved as well as the output of the pump .

1 is a perspective view of a general rotary pump;
Fig. 2 is an operational view of upper and lower cylindrical members according to one rotation of the upper and lower eccentric rotors in the rotary pump shown in Fig. 1. Fig.
3 is a sectional view showing a change in the center distance of the upper and lower eccentric rotors according to the operating state of the conventional rotary pump.
4 is an overall cross-sectional view of a dual-volume volumetric pump in accordance with one embodiment of the present invention.
Figure 5 is an enlarged cross-sectional view of an enlarged view of the upper components of the present invention shown in Figure 4;
6 is a sectional view showing a flexible bearing according to the present invention;
7 is a cross-sectional view and side view showing the type of rolling means of the flexible bearing shown in Fig. 6;
8 is a cross-sectional view and a side view showing the inner ring and the outer ring type of the flexible bearing shown in Fig. 6;
9 is a sectional view showing another embodiment of the flexible bearing of the present invention.
10 is a sectional view showing an operating state of the present invention.
11 is an enlarged cross-sectional view of a dual-use volumetric pump according to another embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a pump according to the present invention will be described in detail with reference to the accompanying drawings.

For a better understanding of the present invention, the description with reference to the drawings is not intended to limit the scope of the present invention. In the following description, a detailed description of related arts will be omitted when it is determined that the gist of the present invention may be unnecessarily blurred.

FIG. 4 shows an overall cross-sectional view of a dual-use volumetric pump according to the present invention, and FIG. 5 shows an enlarged cross-sectional view of an enlarged view of the upper components of the present invention shown in FIG.

Referring to FIG. 1, an embodiment of the present invention includes a housing 100, a rotary shaft 200, an eccentric rotor 300, a cylindrical member 400, and a flexible bearing 500. The center of the upper eccentric rotor 300a and the center of the lower eccentric rotor 300b (hereinafter referred to as the " center distance ") generated during the operation are minimized, and the flexible bearing 500 and the cylindrical member 400 are circular in cross section so as to form a clearance S between the inner circumferential surface of the cylindrical member and the inner circumferential surface of the cylindrical member is elliptical and vertically long and elliptical .

First, the housing 100 is provided with an upper volume chamber 100a capable of receiving the upper cylindrical member 400a and a lower volume chamber 100b capable of receiving the lower cylindrical member 400b on the upper side thereof And the upper and lower volume chambers 100a and 100b communicate with each other.

The upper and lower volume chambers 100a and 100b have the same shape, so that the housing 100 can be vertically symmetrical as a whole.

Fluid inlet (i) and outlet (o) are formed on both sides of the housing (100).

Next, the upper rotary shaft 200a and the lower rotary shaft 200b are horizontally disposed in the upper and lower volume chambers 100a and 100b, respectively, and rotate in opposite directions.

At this time, the rotation shaft 200 is rotated by external power and is coupled with the upper eccentric rotor 300a and the lower eccentric rotor 300b, respectively, to rotate the eccentric rotors 300 in opposite directions.

The eccentric rotor 300 includes an upper eccentric rotor 300a coupled to the upper rotary shaft 200a and a lower eccentric rotor 300b coupled to the lower rotary shaft 200b.

The eccentric rotor 300 and the rotary shaft 200 may be axially coupled by a key-groove coupling method, but are not limited thereto and may be mutually coupled by various shaft coupling methods.

When the rotary shaft 200 is inserted into the eccentric rotor 300, the eccentric rotor 300 is inserted into the eccentric rotor 300 such that the eccentric rotor 300 is eccentrically inserted into one side thereof. Therefore, when the rotary shaft 200 rotates, the eccentric rotor 300 is eccentrically rotated as a cam. At this time, the eccentric rotors 300 may all be circular.

Next, the cylindrical member 400 will be described.

The cylindrical member 400 includes an upper cylindrical member 400a that receives the upper eccentric rotor 300a and is accommodated in the upper volume chamber 100a and a lower cylindrical member 400b that houses the lower eccentric rotor 300b, A lower cylindrical member 400b accommodated in the chamber 100b and a diaphragm 400c connecting the upper cylindrical member 400a and the lower cylindrical member 400b and interlocking the upper cylindrical member 400a and the lower cylindrical member 400b.

Note that, in the present invention, at least one of the two cylindrical members 400 may have an elliptical cross-sectional shape in its inner peripheral surface. That is, only the upper cylindrical member 400a may have an elliptical cross-section, or only the lower cylindrical member 400b may have an elliptical cross-section, or both of the upper and lower cylindrical members 400a and 400b may have an elliptical cross- . It is preferable that both of the upper and lower cylindrical members 400a and 400b be made elliptical.

In this case, the elliptical shape refers to a shape in which one side diameter (major axis) is longer than the other side diameter (minor axis), not a true circle. In the present invention, as shown in FIG. 5 or 8, The vertical shape or the major axis may be elliptical in the form of a horizontal shape.

The circular cylindrical eccentric rotor 300 rotates the upper cylindrical member 400a in the upper volume chamber 100a and the lower cylindrical member 400b in the lower volume chamber 100b, Each comes in contact with each other.

Next, the flexible bearing will be described with reference to FIG. 6 is a cross-sectional view showing a flexible bearing according to the present invention. 6 (a) shows the shape of the flexible bearing when there is no external force, and Fig. 6 (b) shows the shape of the flexible bearing deformed into the ellipse when there is external force.

And FIG. 7 is a cross-sectional view and a side view showing the type of rolling means of the flexible bearing shown in FIG. 6, and FIG. 8 is a cross-sectional view and a side view showing the kind of the inner ring and the outer ring of the flexible bearing shown in FIG.

A flexible bearing 500 having a circular cross section may be coupled to the outer periphery of the eccentric rotor 300 between the respective eccentric rotors 300 and the cylindrical member 400.

The flexible bearing 500 prevents friction between the eccentric rotors 300 and the eccentric rotors 300 when the eccentric rotors 300 rotate in the cylindrical members 400 to smoothly rotate the eccentric rotors 300. In addition, as the center distance between the upper and lower eccentric rotors increases while rotating inside the elliptic cylindrical members 400, the cylindrical member 400 is impacted. However, the flexible bearing 500 cushions the impact It plays a role.

6, the flexible bearing 500 includes an inner ring 510 supporting the ball, a roller or a hollow pin or a hollow cutting pin, an outer ring 520, and a ball or roller or a hollow pin or a hollow cutting pin And a retainer 530 that can maintain the gap.

The flexible bearing 500 according to the present invention has a flexible material such as the inner ring 510, the outer ring 520 and the retainer 530 so as to have an elastic force so as to be deformable into an elliptical shape (L1 <L2) . For this, the inner ring 510 and the outer ring 520 may be made of steel, synthetic resin, or the like having sufficient elasticity and restoring force, and the retainer 530 may be made of synthetic resin or rubber having elasticity and restoring force .

The types of the rolling means 540, the inner ring 510 and the outer ring 520 constituting the flexible bearing will be described in more detail.

A ball, a roller, a hollow pin, and a hollow cutting pin may be used as the rolling means 540 interposed between the inner and outer rings, as shown in FIG. 7 (a) is a view, (b) is a roller, (c) is a hollow pin, and (d) is a hollow cutting pin.

The ball has a spherical shape, and the roller has a round bar shape and may be made of a steel material.

The hollow pin may have a shape of an empty hollow, and the hollow cutting pin may have a shape cut at one side of the hollow pin and may be made of steel.

Particularly, the hollow cutting pin can be deformed and restored by an external force due to the cut portion, thereby being flexible.

The inner ring 510 and the outer ring 520 may have the same shape as shown in FIG. Here, Fig. 8 (a) shows a cylinder shape, and Fig. 8 (b) shows a shape in which a strap is wound in a spiral shape.

When the inner ring 510 and the outer ring 520 have a cylindrical shape, they are made to have a proper thickness by being made flexible so that they can be deformed and restored by an external force. That is, even if a steel material is used, a flexible action is possible.

In addition, the inner ring 510 and the outer ring 520 can be formed into a shape in which a strip-shaped long strap is wound in a helix shape as shown in (b). This is more flexible than the cylinder shape, so that it can cope with external force much more flexibly.

Meanwhile, the balls, rollers, hollow pins, and hollow cut-out pins are usually installed in less than the number of flexible bearings used in mechanical devices, so that a sufficient distance is maintained between balls, rollers, hollow pins, It is desirable to allow the eccentric rotors to be easily deformed into an elliptical shape when rotating.

9, another form of the flexible bearing can be used. 9 is a cross-sectional view showing another embodiment of the flexible bearing of the present invention.

The rolling means 540 may be formed as an integral cylindrical shape without a retainer. At this time, the rolling means 540 may be made of a flexible resin material.

A solid lubricant-dispersible resin using a tetrafluoroethylene (PTFE) resin can be preferably used. This can be used in air, underwater, and sea water. Even if the oil is attached to the bearing sliding surface, the friction characteristics are not deteriorated, and lubricant film is formed even under a small exercise condition, thereby exhibiting excellent friction characteristics. It has the load-bearing characteristics of metal bracket class due to the double structure of sliding layer and back material (FRP), and it is easy to set the dimensions because the swelling rate is low.

However, it is needless to say that the present invention is not limited to the above-described embodiment, and other types and types of resin bearings can be used.

The space S can be formed between the elliptical cylindrical member 400 and the flexible bearing 500. That is, the clearance space S may be formed on the extended line side connecting the center of the rotation axis in the initial state in which the eccentric rotors 300 are aligned as shown in FIG. The flexible bearing 500 and the inner circumferential surface of the cylindrical member 400 may be in contact with each other on both sides of the cylindrical member 400 in which the clearance S is formed, . The contact may be a line or a plane contact, and mathematically may refer to a line contact or a substantially plane contact.

The eccentric rotor 300 can be freely rotated within the cylindrical member 400 by providing the clearance S as described above. That is, the clearance S serves to compensate for the center distance deviation of the eccentric rotor 300.

The operating state of the present invention will be described in detail with reference to FIG. 2 and FIG. 9 is a cross-sectional view showing an operating state of the present invention.

When the eccentric rotor 300 vertically installed in the initial state starts to rotate to one side and rotates by 90 degrees, the deviation of the center distance between the eccentric rotors 300 is changed to the maximum, The side surface of the rotor 300a is impacted or mechanically engaged with the upper inner circumferential surface of the upper cylindrical member 400a and the rotation is not smooth. Similarly, even when the eccentric rotor 300 is rotated by 270 degrees, the center distance deviation becomes maximum and the same phenomenon occurs.

However, since the cylindrical member 300 is elliptical and the eccentric rotor 300 and the flexible bearing 500 are circular, as described above, when the eccentric rotor 300 rotates 90 degrees, the flexible bearing 500 Since the clearance S is formed between the upper and lower eccentric cylindrical members 400 and 400, even if the center distance between the upper and lower eccentric rotors increases, the side surface of the eccentric rotor 300 moves to the clearance S There is a possibility of being able to do.

Accordingly, since the clearance space S serves as a buffering function while accommodating a part of the eccentric rotor 300 and the flexible bearing 500, it is possible to smoothly rotate without any occurrence of a shock or a phenomenon during rotation .

In addition, since the flexible bearing 500 is coupled to the eccentric rotor 300, friction is reduced and shock is absorbed, and since the flexible bearing 500 is made of a flexible material, if the volume is reduced due to compression at some point, So that a smooth rotation motion can be further ensured.

The radius of curvature of the upper inner circumferential surface of the cylindrical member 400 is greater than the radius of curvature of the inner circumferential surface of the cylindrical member 400 in the initial state, Is smaller than the radius of curvature.

That is, the radius of curvature of the upper portion of the inner circumferential surface may be smaller than the radius of curvature of the outer circumferential surface of the upper or lower eccentric rotors 300a and 300b when the upper or lower cylindrical members 400a and 400b are vertically elliptical.

Therefore, when the upper eccentric rotor 300a is rotated by 90 degrees, the upper eccentric rotor 300a is moved to the upper inner peripheral surface of the upper cylindrical member 400a together with the flexible bearing 500, that is, The center distance deviation can be compensated for by being partially pushed into the movable member S, but the pressure loss is not generated because it is not completely accommodated, and the rotation is smooth. The same applies to the case of the lower eccentric rotor 300b.

However, if the radius of curvature of the upper inner circumferential surface of the upper cylindrical member 400a is larger, when the upper eccentric rotor 300 rotates 90 degrees, the upper surface of the upper eccentric rotator 300 moves in the clearance S A gap is formed between the inner peripheral surface of the upper and lower volume chambers 100a and 100b of the housing 100 and the outer peripheral surface of the upper and lower cylindrical members 400a and 400b, There arises a problem that leakage occurs due to the pressure action of the pressure sensor.

Hereinafter, another embodiment of the present invention will be described with reference to FIG. Figure 10 shows an enlarged cross-sectional view of a dual-use volumetric pump according to another embodiment of the present invention.

Referring to the drawings, another embodiment of the present invention includes a housing 100, a rotating shaft 200, an eccentric rotor 300, a cylindrical member 400, and a flexible bearing 500, The center of the upper eccentric rotor 300a and the center of the lower eccentric rotor 300b (hereinafter referred to as the " center distance ") generated during the operation are minimized, and the flexible bearing 500 and the cylindrical member 400 and the flexible bearing 500 are circular and the inner peripheral surface of the cylindrical member 400 is elliptical in cross section and the left and right long sides And it is an elliptical shape.

The description of the housing, the rotating shaft, the eccentric rotor, and the flexible bearing is largely different from that described above, so that a detailed description thereof will be omitted and the cylindrical member 400 having a structural difference will be described in detail.

The cross section of at least one of the upper cylindrical member 400a and the lower cylindrical member 400b may be horizontally elliptical. That is, the eccentric rotor 300 and the flexible bearing 500 are circular, and when the cylindrical member 400 is aligned in the initial state, the long axis is an elliptical shape.

In such a structure, a clearance S is formed between the flexible bearing 500 and the elliptical cylindrical member 400.

That is, the clearance S may be formed on both sides of the extension line connecting the center of the rotation axis in the initial state in which the eccentric rotors are aligned as shown in FIG. The flexible bearing 500 and the inner circumferential surface of the cylindrical member 400 may be in contact with each other without the spacing space on the inner circumferential surface of the cylindrical member where the clearance S is not formed, have. The contact may be a line or a plane contact, and mathematically may refer to a line contact or a substantially plane contact.

More specifically, when the eccentric rotor 300 starts rotating to one side and is rotated by 90 degrees or 270 degrees, the center distance deviation between the eccentric rotors 300 becomes maximum, The side of the electron 300 is closely attached to the upper part of the inner circumferential surface of the cylindrical member 400. At this time, the flexible bearing 500 is pressed and elastically stretched. At this time, the enlarged portion can be accommodated in the clearance space S.

Since the eccentric rotor 300 can be rotated in a state of being in close contact with the inner circumferential surface of the cylindrical member 400 because the space S accommodates a portion of the expanded flexible bearing 500 and functions as a buffer, It is possible to rotate smoothly without causing any phenomenon of impact or rotation.

Preferably, the radius of curvature of the inner surface of the side surface of the cylindrical member 400 is smaller than the radius of curvature of the eccentric rotor 300.

That is, the radius of curvature of the outer circumferential surface of the upper or lower eccentric rotors 300a and 300b may be smaller than that of the upper or lower cylindrical members 400a and 400b.

Therefore, when the upper eccentric rotor 300a is rotated 90 degrees, the upper eccentric rotor 300a is moved to the side inner peripheral surface of the upper cylindrical member 400a together with the flexible bearing 500, that is, (S), the pressure loss is not generated and the rotation is smooth. The same applies to the case of the lower eccentric rotor 300b.

However, if the radius of curvature of the inner circumferential surface of the side surface of the cylindrical member 400 is larger, when the eccentric rotor 300 rotates 90 degrees, the outer circumferential surface of the eccentric rotor 300 moves into the clearance space S A gap is formed between the inner peripheral surface of the upper and lower volume chambers 100a and 100b of the housing 100 and the outer peripheral surface of the upper and lower cylindrical members 400a and 400b, There arises a problem that leakage occurs in the liquid.

Preferably, the radius of curvature of the side surface of the elliptic eccentric rotor is the same as the radius of curvature of the top inner circumferential surface of the elliptic cylindrical member with respect to the initial state in which the elliptical eccentric rotor 300 is vertically erected.

That is, when the elliptical upper eccentric rotor 300a is rotated by 90 degrees, an inner clearance Si is formed at the upper portion, and at this time, a portion of the upper cylindrical member 400a adjacent to the portion where the inner clearance Si is formed, The radius of curvature of the inner circumferential surface may be the same as the radius of curvature of the side surface in a state where the oval upper eccentric rotor 300a is vertically erected.

This is because when the upper eccentric rotor 300a is rotated by 90 degrees, the side surface of the upper eccentric rotor 300a is completely brought into close contact with the upper inner peripheral surface of the upper cylindrical member 400a together with the flexible bearing 500, As the space Si disappears, the flexible bearing 500 is pressed, and the expanded flexible bearing is accommodated in the external clearance So. Thus, smooth rotation can be achieved.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed exemplary embodiments.

100: Housing
100a: upper volume chamber 100b: lower volume chamber
i: Fluid inlet o: Fluid outlet
200:
200a: upper rotating shaft 200b: lower rotating shaft
300: eccentric rotor
300a: upper eccentric rotor 300b: lower eccentric rotor
400: cylindrical member 400a: upper cylindrical member
400b: lower cylindrical member 400c: diaphragm
410: Surface
500: Flexible bearing
510: inner ring 520: outer ring
530: retainer 540: rolling means
S: Free space

Claims

A housing having upper and lower symmetric upper and lower volume chambers communicating with each other;
A rotary shaft including an upper rotary shaft and a lower rotary shaft which rotate in opposite directions in the upper and lower volume chambers respectively;
An eccentric rotor including an upper eccentric rotor and a lower eccentric rotor in which the upper rotary shaft and the lower rotary shaft are eccentrically inserted and rotated, respectively;
An upper cylindrical member and a lower cylindrical member accommodating therein the upper eccentric rotor and the lower eccentric rotor, respectively, and inserting and moving in the upper and lower volume chambers, respectively, and a lower cylindrical member and a lower cylindrical member, A cylindrical member including a diaphragm for interlocking with each other; And
A retainer for retaining the inner and outer rings of the rolling means and the outer ring and the rolling means is provided between the upper cylindrical member and the upper eccentric rotor and between the lower cylindrical member and the lower eccentric rotor, And a flexible bearing which is made of one material and reduces the friction and impact on the cylindrical member due to rotation of the eccentric rotor,
Wherein a cross section of the eccentric rotor is circular and the flexible bearing is circular in cross section so as to contact the outer peripheral surface of the eccentric rotor, and at least one of the upper cylindrical member and the lower cylindrical member has an elliptical cross- And a clearance is formed between the inner peripheral surface of the member and the flexible bearing.

The method according to claim 1,
Wherein the rolling means of the flexible bearing is one of a ball, a roller, a hollow pin, and a hollow cutting pin.

3. The method of claim 2,
Wherein the inner ring and the outer ring have a cylindrical shape or a shape in which the strap is wound in a spiral shape.

The method according to claim 1,
Wherein the rolling means of the flexible bearing is made of a cylindrical and flexible resin material.

The method according to claim 1,
Wherein the elliptical cylindrical member is vertically erected,
And an elliptical shape having a long axis so that a clearance space is formed on the upper side or an elliptical shape having a long axis with a long axis so that a clearance is formed on the side surface.

6. The method of claim 5,
Wherein the curvature radius of the upper inner circumferential surface of the elliptical cylindrical member whose vertical axis is vertical is smaller than the curvature radius of the eccentric rotor.

6. The method of claim 5,
Wherein the radius of curvature of the side surface of the elliptical cylindrical member whose major axis is horizontal is smaller than the radius of curvature of the eccentric rotor.