KR20150142161A

KR20150142161A - Floid moving device

Info

Publication number: KR20150142161A
Application number: KR1020140070403A
Authority: KR
Inventors: 신호열
Original assignee: 신호열
Priority date: 2014-06-10
Filing date: 2014-06-10
Publication date: 2015-12-22

Abstract

The present invention provides a fluid transferring device for pumping or compressing a fluid to be transferred. The fluid transferring device comprises: an outer rotor; an inner rotor; a suction opening; a discharge opening; a first plate; and a second plate. The outer rotor has an interior with a cylindrical shape and an inner space allowing the fluid to be introduced thereinto and has at least three compression areas having an equal shape and formed on the inner space at equal intervals. The inner rotor has at least one compression wing. The compression wing is rotated about a central axis, arranged on the inner space of the outer rotor that is inserted into the compression areas, has sealing reference surfaces formed on both lateral sides to seal the compression area, and has an outer circumferential surface in contact with inner circumferential surfaces of the compression areas. The suction opening introduces the fluid from the outer rotor into the interior thereof. The discharge opening discharges the fluid in the compression areas to the outside. The first plate seals one side surface of the fluid transferring device from the outside. The second plate seals the other side surface of the fluid transferring device from the outside.

Description

FLOID MOVING DEVICE

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a process for treating a flow of a fluid, and more particularly, to a fluid transfer device.

BACKGROUND OF THE INVENTION Devices for transferring fluids are widely used in the industry. Particularly, there are a pump for pumping fluid, a compressor for compressing fluid, a blower for blowing gas, and the like.

A pump is a machine that receives mechanical energy from a motor such as an electric motor or an internal combustion engine, and changes the position of the liquid by applying motion and pressure energy to the liquid. The action of the pump is by suction and discharge. The inhalation action is to make the inside of the pump into a vacuum state, so that it can be inhaled to the theoretical 10.33 [m] at the standard atmospheric pressure. However, due to the friction loss in the suction pipe or the air contained in the water, no more than 7 [m] is worn. The types of pumps are divided into turbo type, volumetric type and special type according to the structure and operation principle, and there are water supply, drainage, circulation, fire extinguishing and oil for various purposes.

In addition, a compressor is a device that converts pressure and speed by applying pressure to a fluid. Although the compressor and the blower can not be strictly distinguished, generally, a pressure rise of 1 kgf / cm 2 or more is classified as a compressor. Various types of compressors are used depending on the capacity and pressure, from a low pressure of 1 to 2 kgf / cm 2 to a high pressure of more than 1,000 kgf / cm 2. Compressors can be broadly divided into reciprocating compressors, screw compressors, centrifugal compressors, and axial compressors.

In recent years, a ventilation system has been applied for a pleasant environment in many places of daily life as well as a high-rise building such as a building and a mansion. A ventilator for driving the impeller (fan) Essentially required. The blower is classified into various forms according to the purpose and the purpose of use. The blower may be a type that supplies wind generated by a fan rotating for the purpose of blowing air such as a fan, (Such as various industrial sites or plastic houses), there is a method of discharging air to the outside.

A blower or compressor is a universal device that is almost indispensable where a mechanical device is involved, and a pump is also a general-purpose device that is almost always used. However, low noise, high productivity pumps and compressors required in the industry are not easily developed. If a blower, compressor, or pump is developed that has a better performance than the current blower, compressor, or pump, it will be easier to increase productivity in various industries or at home.

The present invention provides a fluid transfer device for pumping or compressing fluid.

The present invention relates to an outer rotor having an inner cylindrical shape and having an inner space into which a fluid flows, wherein the outer rotor has at least three compression regions formed at equal intervals of the same shape at equal intervals, And a compression wing having an outer circumferential surface which is formed on both side surfaces and which is in contact with the inner circumferential surface of the compression region by rotation, is provided at least in the inner space of the outer rotor, A first plate for sealing one side of the outer rotor, a second plate for sealing one side of the outer rotor, a second plate for sealing one side of the outer rotor, And a second plate for sealing the other side surface of the outer rotor.

According to another aspect of the present invention, there is provided an internal combustion engine comprising: compression vanes formed at equal intervals, the compression vanes being formed by protruding at least two identical shapes and rotating around a central axis; and an outer circumferential surface of the compression vanes, Wherein the inner rotor is disposed inside the rotor, and the compression regions in which the compression blades of the inner rotor are inserted to form the closed space are formed at equal intervals of the same shape, and the number of the compression regions is larger than the number of the compression blades A discharge port for discharging the fluid of the closed space formed in the compression region to the outside and a discharge port for discharging fluid to the outside of the outer rotor, 1 plate and a second plate for sealing the other side of the outer rotor.

According to another aspect of the present invention, there is provided an internal combustion engine comprising: compression vanes formed at equal intervals, the compression vanes being formed by protruding at least two identical shapes and rotating around a central axis; and an outer circumferential surface of the compression vanes, Wherein a compression region formed by the hypotrochoid trajectory of the compression vane is formed with equal spacing in the same form and the number of compression zones is defined by the number of compression wings A first plate for sealing one side of the outer rotor, and a second plate for sealing one side of the outer rotor; and a second plate for sealing one side of the outer rotor, And a second plate for sealing the other side surface of the outer rotor.

According to another aspect of the present invention, there is provided an internal combustion engine comprising: an external rotor having a cylindrical interior and having an internal space into which fluid is introduced, wherein at least three compression regions are formed in the internal space, An inner rotor disposed in the inner space of the outer rotor and having at least one compression vane sequentially inserted into the compression regions each time one rotation is made about the central axis, A discharge port for discharging the fluid in the compressed region to the outside, a first plate for sealing one side of the outer rotor, and a second plate for sealing the other side of the outer rotor do.

In the fluid transferring apparatus of the present invention, in the transfer of the fluid, the internal components are minimized in friction, and there is only a surface where the friction surfaces are in contact with each other. Therefore, the fluid transfer device of the present invention generates little noise when transferring the fluid. If this is applied to various fields, too much noise is generated in compressing or pumping the fluid, which can completely solve the problematic part.

Further, in the fluid transferring apparatus of the present invention, since the portion where the internal components are frictioned is minimized in transferring the fluid, heat generation is greatly reduced, thereby realizing a highly durable pump or compressor have.

In addition, the fluid transfer device of the present invention can maintain high productivity in manufacturing since there are very few essential components required for transferring fluids and all the components are simple shapes.

In addition, the fluid transfer device of the present invention is advantageous in that it is compact because there are very few essential components required for transferring the fluid and all the components are simple shapes. Compressors and pumps having a conventional structure are too complicated to be made compact. However, since the fluid conveying apparatus of the present invention requires very few key components and all the components are simple, it can be implemented in a small size .

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 and Fig. 2 show a fluid delivery device according to an embodiment of the present invention.
3 is an exploded perspective view showing a fluid transportation device according to an embodiment of the present invention;
4 is a detailed view illustrating an inner rotor of a fluid transportation device according to an embodiment of the present invention.
Figure 5 shows a hypotrochoid curve used to implement an outer rotor of a fluid transport device according to an embodiment of the present invention.
6 is a detail view showing an outer rotor of the fluid transportation device according to an embodiment of the present invention.
7 to 14 are diagrams for explaining the operation of the fluid transportation device according to the embodiment of the present invention.
15 to 18 are diagrams for explaining the operation of the fluid transportation device according to the second embodiment of the present invention.
19 is a view for explaining the operation of the fluid transportation device according to the third embodiment of the present invention.
20 and 21 are diagrams for explaining the operation of the fluid transportation device according to the third embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings, in order to facilitate a person skilled in the art to easily carry out the technical idea of the present invention. do.

1 and 2 are views showing a fluid transporting apparatus according to an embodiment of the present invention. FIG. 1 is a view showing one side of a fluid transfer device according to an embodiment of the present invention, and FIG. 2 is a view showing another side of a fluid transfer device according to an embodiment of the present invention. 3 is an exploded perspective view showing a fluid transportation device according to an embodiment of the present invention. 1 to 3, a fluid transfer device according to an embodiment of the present invention will be described.

The fluid transfer device according to the present embodiment is an apparatus that receives and transfers a fluid. The fluid supplied to the fluid transportation device according to the present embodiment includes all kinds of liquids and all kinds of gases. When the supplied fluid is a liquid, the fluid transfer device according to the present embodiment can be used for pumping or transferring the input liquid. In the case where the supplied fluid is a gas, Can be used to compress or transport.

In order to perform such operation, the fluid transfer device according to the present embodiment includes an outer rotor 100, an inner rotor 200, a power transmission portion 300, a first plate 400, a second plate 500, 600).

The outer rotor 100 is implemented in a form capable of rotating, and is implemented as a cylindrical shape having a predetermined width in order to enable efficient rotation. In addition, the outer rotor 100 has a predetermined space in which fluid is conveyed or compressed. The inner rotor 200 is configured to be included in the inner space of the outer rotor 100 and is configured to rotate inside the outer rotor 100 as the outer rotor 100 rotates. The inner rotor 200 is disposed inside the outer rotor 100 and rotates in the inner region of the outer rotor 100 as the outer rotor 100 rotates so that a portion of the inner region of the outer rotor 100 The shape is implemented so that it is hermetically sealed and the closed region is compressed. The outer rotor 100 and the inner rotor 200 are the essential elements of the fluid transfer device according to the present embodiment, and a detailed description will be described in detail later.

The power transmitting portion 300 is a device for rotating the outer rotor 100 and / or the inner rotor 200. In this case, the inner rotor 200 may be rotated in accordance with the rotation of the outer rotor 100 and the inner rotor 200 may be rotated at a predetermined ratio. Alternatively, as the inner rotor 200 rotates, (100) is rotated. For example, it is possible to use any type of gear, such as an internal gear as well as an external gear, and may be implemented using other types of mechanical devices such as timing belts, chains, and the like.

The power transmitting portion 300 according to the present embodiment includes an inner rotor gear 310, an inner rotor center shaft 320, and an outer rotor gear 330. The inner rotor center shaft 320 of the inner rotor gear 310 is connected to the inner rotor 200 and rotates the inner rotor 200 as the inner rotor gear 310 rotates. The outer rotor gear 330 is connected to the outer rotor 100 to allow the outer rotor 100 to rotate as the outer rotor gear 330 rotates.

The first plate 400 is a circular plate for sealing one side of the outer rotor 100 and includes a rotating plate 410 and a fixing plate 420. The rotary plate 410 is formed in a circular ring shape and is coupled with the outer rotor 100 and the outer rotor gear 330 so that the outer rotor 100 can rotate as the outer rotor gear 330 rotates . The fixing plate 420 is disposed inside the rotary plate 410 so that the hole provided therein can connect the center axis of the inner rotor 320 to the center axis of the inner rotor 200.

The second plate 500 is implemented as a circular plate for sealing the other side of the outer rotor 100. The second plate 500 includes a suction port 510, a first discharge hole 520, a check valve 530, a second discharge hole 550, a first discharge passage 540, and an outer rotor central axis 560 . When the first plate 400 and the second plate 500 are respectively attached to one side surface and the other side surface of the outer rotor 100, the inner region of the outer rotor 100 has a closed space do. And the fluid is compressed or pumped in the closed space.

The suction port 510 is a passage for supplying fluid to the inner space. Although implemented on the side of the second plate 500 in the form of four square passages here, it can be implemented in any position in any position as long as it can provide fluid to the interior space. Although the number of the intake ports 510 is four in this embodiment, the number can be adjusted to a desired number in some cases.

Each of the four first discharge holes 520 is provided with a corresponding check valve 530 and internally connected to the inner space and the second discharge hole 540, respectively. The check valve 530 is a valve that only flows in one direction to prevent backflow of the fluid. Here, the check valve 530 prevents the fluid to be pumped or compressed from flowing back into the inner space after being discharged through the four first and second discharge holes 520, 540.

The first and second discharge holes 520 and 540 are passages for discharging the fluid that is compressed or pumped in the internal space. Four of the first and second discharge holes 520 and 540 are arranged at 90 degrees apart from each other. The first discharge holes 520 are disposed on the side of the second plate 500 so as to penetrate the second plate 500, and a check valve is attached to each of them. The second discharge hole 540 is disposed on the circumferential surface of the second plate 500. The numbers and arrangement positions of the first and second discharge holes 520 and 540 can be determined according to the shape of the inner space. Here, since four compression spaces are formed in the inner space, four first and second ejection holes 520 and 540 corresponding to the four compression spaces are disposed. The number of compression spaces formed in the interior space will be described in detail later.

The first discharge passage 550 is an annular groove formed along the outer circumferential surface of the second plate 400. The first discharge passage 550 is a space where the fluid that is compressed or pumped in the inner space flows out through the second discharge hole 540 .

The discharge ring 600 is formed in a ring shape surrounding the outer circumferential surface of the second plate 500 and includes a second discharge passage 610 and an outlet 620. The second discharge passage 610 is formed as a ring-shaped groove along the inner circumferential surface of the discharge ring 600. The first discharge passage 550 and the second discharge passage 610 are coupled to each other to form an annular space in which the fluid discharged from the inner space through the second discharge hole 540 stays to be. The fluid staying in the annular space is discharged to the outside through the discharge port (620). The outlet 620 may be disposed at various locations as needed, and may be provided at a plurality of locations as needed.

The fluid that is compressed or pumped in the internal space moves to the first discharge hole 520 provided in the second plate 500 and the moved fluid is discharged to the first discharge hole 520 connected to the first discharge hole 520 2 to the annular space formed by the first discharge passage (550) and the second discharge passage (610) through the discharge hole (540). The fluid that has been moved into the annular space is discharged to the outside through the discharge port 620. In this process, the fluid moved from the inner space to the annular space is prevented from flowing back to the inner space by the check valve 530 disposed in the first discharge hole 520.

The second plate 500 is a circular plate disposed on the side of the outer rotor to make sealing of the inner space. The suction port 510, the discharge hole 540, and the first discharge passage 550 provided in the second plate 500 may be implemented in different forms as the case may be, and may be disposed elsewhere. If the suction port 510, the discharge hole 540 and the discharge passage 550 provided in the second plate 500 are realized in different forms, the discharge port 610 having the second discharge passage 610 and the discharge port 620, Ring 600 may be modified and implemented accordingly.

The outer rotor center shaft 560 is installed at the center of the second plate 500 and at a position coinciding with the center of the outer rotor 100 and the outer rotor gear 410. The inner rotor center shaft 320 is installed at the center of rotation of the inner rotor gear 310 and the inner rotor 200. The inner rotor gear 310 and the inner rotor 200 rotate in the same direction by the inner rotor center shaft 320. The outer rotor gear 330 is connected to the rotating plate 410 and the outer rotor 100 and rotates in the same direction. Also, the second plate 500 is connected to the outer rotor 100 and rotates in the same direction. The second plate 500, the discharge ring 600, and the fixing plate 420 are fixed without being rotated, and are provided with fixing members (not shown) for coupling them.

When the inner rotor gear 310 is rotated by external power, the inner rotor 200 rotates and the outer rotor gear 330 rotates in the opposite direction. Therefore, the outer rotor 100 connected to the outer rotor gear 330 by the rotating plate also rotates in the direction opposite to the inner rotor 200. When the outer rotor 100 rotates, the second plate 500 rotates in the same direction.

On the contrary, when the outer rotor gear 330 rotates by external power, the inner rotor gear 310 rotates in the opposite direction. Therefore, the rotating plate 410, the outer rotor 100 and the second plate 500 connected to the outer rotor gear 330 rotate in the same direction and the inner rotor gear 310 and the inner rotor 200 ).

The fluid transfer device according to the present embodiment is a key operation in which the inner rotor 200 rotates inside the outer rotor 100 to compress or pump the fluid provided in the inner space. In this process, the inner rotor gear 310 may be rotated or the outer rotor gear 330 may be rotated. It is possible to transmit the power from the outside to rotate the inner rotor gear 310 or the outer rotor gear 330 so that the connected parts rotate in the same direction.

Next, how the inner rotor 200 and the outer rotor 100 are implemented will be described.

4 is a detailed view showing an inner rotor of the fluid transportation device according to an embodiment of the present invention.

4, the inner rotor 200 of the fluid transfer device according to the embodiment of the present invention includes a first compression vane 210, a second compression vane 220, a third compression vane 230, (240). The first compression vane 210, the second compression vane 220 and the third compression vane 230 are all formed in the same shape and are disposed at an interval of 120 degrees between the center holes 240 . In addition, the first compression vane 210, the second compression vane 220, and the third compression vane 230 are all formed asymmetrically. The compression wing can be implemented in various numbers, and the case of three compression wings is mainly described here. Even when three or more compression vanes are provided, they are spaced apart from each other at regular intervals with respect to the center hole 240. For example, if four compression vanes are arranged, they are spaced apart by 90 degrees each.

Since all three compression wings are implemented in the same form, one compression wing is discussed in detail. The first compression vane 210 includes a left wing surface 211, a first hermetic surface 212, an upper wing surface 213, a right wing surface 214, a second hermetic surface 215, . The left wing surface 211 is a curved surface formed on the left side with respect to the upper wing surface 213. The left wing surface 211 may not protrude from the first hermetic surface 212. The first hermetic reference surface 212 is embodied in the form of an arc with a surface occupying an edge between the left wing surface 211 and the upper wing surface 213. The first hermetic reference surface 212 serves as a part for maintaining a sealing force at a certain portion of the internal space. The upper wing surface 213 is embodied in the form of an arc that is a portion of the outer circumference that the inner rotor can form with respect to the center hole 240. The right wing surface 214 may be implemented in the form of a convex curve, which is implemented as an involute curve here. An involute curve is a trace drawn by a point on a line when a straight line moves without a slip on the distal. The second sealing reference plane 215 is the corner point at the point where the right wing surface 214, which is an involute curve, ends. The second sealing reference surface 215 serves as a part for maintaining the sealing force in the inner space constant portion together with the first sealing reference surface 212. The wing hole 216 is a portion of the first compression vane 210 that is opened in a certain region of the first compression vane 210 and is not a portion that influences the rotation operation of the inner rotor 200 of the fluid transfer device according to the present embodiment . However, in order to reduce the weight of the inner rotor 200, the wing hole 216 is formed by removing the inside of the compression wing.

The compression wing 210 constituted by the first hermetic reference surface 212, the upper wing surface 213, the right wing surface 214 and the second hermetic surface 215 has a diameter larger than that of the upper wing surface 213 A certain moving area is formed in the reference circle when the reference circle is touched in the reference circle with reference to the center hole 240 in a certain reference circle. When the inner rotor 200 having a plurality of compression vanes 210 is moved in contact with the inner circumference of the reference circle implemented by the outer rotor 100 as described above, And the remaining region is realized in the form of an outer rotor 100. The outer rotor 100 may be formed as an outer rotor. This is based on the principle of the hypotrochoid curve. The movement of the inner rotor 200 compression vane 210 is shown in detail in FIG.

5 is a diagram showing a hypotrochoid curve used to implement an outer rotor of a fluid transportation device according to an embodiment of the present invention.

A trochoid curve is a trace drawn by a point connected to a circle as the circle rolls. A trace drawn by a point connected to the inscribed circle while inscribing the reference circle in the trochoid curve is called a hypotrochoid curve. A trace drawn by a circumscribed circle circumscribing a reference circle and connected to the circumscribed circle of the trochoid curve is called an epitrochoid curve. The cycloid curve is the point when the point on the curve is on the circumference of the inscribed circle or circumscribed circle. Among these curves, the outer rotor 100 of the fluid transfer device according to the present embodiment is implemented using a hypo-trochoid curve. The inscribed circle in which the compression wing 210 constituted by the first hermetic surface 212, the upper wing surface 213, the right wing surface 214 and the second hermetic surface 215 is embodied by the upper wing surface 213, When the outer rotor 100 is moved in contact with the reference circle implemented by the inner space with respect to the outer rotor 100, the outer rotor 100 is moved to the region where the compression wing 210 passes in the region within the reference circle implemented by the inner space Is implemented as an internal space. And forms an outer rotor 100 in an area within the reference circle where the compression vane 210 does not pass.

5 shows a reference circle C-100 in which an inscribed circle C-200, in which the compression blade 210 of the inner rotor 200 is embodied as the upper blade surface 213, is formed by the inner space of the outer rotor 100, A trajectory T in which a line L connected to the inscribed circle C-200 moves when touched with the reference circle C-100 is shown in FIG. By using such a trajectory T, the trajectory of the movement of the compression vane 210 can be obtained. That is, the trajectory of the first hermetic surface 212, the upper wing surface 213, the right wing surface 214, and the second hermetic surface 215 of the compression vane 210 is calculated to obtain the reference circle C-100 ) It is possible to define the moving area inside.

The locus of movement of the first hermetic reference surface 212, the upper wing surface 213, the right wing surface 214 and the second hermetic surface 215 of the compression vane 210 is determined to be a space, When the inner shape of the outer rotor 100 is realized, the shape as shown in FIG. 6 can be derived.

6 is a detailed view showing an outer rotor of the fluid transfer device according to an embodiment of the present invention.

6, the outer rotor 100 of the fluid transfer device according to the embodiment of the present invention includes a first compression region 110, a second compression region 120, a third compression region 130, And a compression region 140. The first compression region 110, the second compression region 120, the third compression region 130 and the fourth compression region 140 are all implemented in the same form, and the inner shape of the outer rotor 100 is a first The compression region 110, the second compression region 120, the third compression region 130, and the fourth compression region 140 may be formed in a manner as shown in FIG. Since the first compression region 110, the second compression region 120, the third compression region 130, and the fourth compression region 140 are all the same, only one will be described in detail and the remaining description will be omitted.

The first compression region 110 is formed by a left interfacing surface 111, a left side surface 112, a compression surface 113, a right side surface 114 and a right side surface 115. The second compression zone 120 is also formed by a left interface 121, a left side 122, a compression surface 123, a right side 124 and a right side 125.

The left interface 111 of the first compression region 110 is for connecting the boundary portion between the first compression region 110 and the second compression region 120. The left interface 111 of the first compression region 110 may be implemented in a straight line or a curve such that the compression wings 210-230 of the inner rotor 200 do not hinder the trajectory of the hypotrochoid curve . The left side surface 112, the compression surface 113, the right side surface 114 and the right side surface 115 of the first compression region 110 are connected to the first sealing reference surface 212 of the compression vane 210, The first wing surface 213, the right wing surface 214, and the second sealing reference surface 215 are implemented corresponding to the trajectory of a hypotrochoid curve moving. The boundary of the left side surface 112 of the first compression region 110 is defined according to the trajectory of the first hermetic surface 212 of the compression vane 210, The boundary of the compression surface 113 of the first compression region 110 is determined. And the boundary of the right side surface 114 of the first compression region 110 is determined according to the trajectory of the right wing surface 214 moving. The boundary of the right boundary surface 115 of the first compression region 110 is determined according to the locus of movement of the second hermetic reference plane 215. [

Next, the inner rotor 200 rotates inside the outer rotor 100 to see how the fluid in the inner space is compressed or pumped.

FIGS. 7 to 14 are views for explaining the operation of the fluid transfer device according to the embodiment of the present invention, and particularly showing the inner rotor and the outer rotor.

The inner rotor 200 of the fluid transfer device according to the present embodiment is configured to rotate clockwise inside the outer rotor 110. The inner rotor 200 may be rotated in the counterclockwise direction in the outer rotor 110. In this case, the inner rotor 200 may be modified to be symmetrical to the one shown in FIG. 7 to FIG.

The center of rotation of the inner rotor 200 rotates clockwise about the center hole 240 and the outer rotor 100 rotates clockwise about the outer rotor center shaft 560. The first to third compression vanes 210 to 230 of the inner rotor 200 rotate about the center axes of the outer rotor 100 and the outer rotor 100, 4 compression regions 110 to 140, and then repeatedly performs the operation of exiting. Herein, the operation of compressing or pumping the fluid in the first compression zone 110 by inserting the first compression vane 210 into the first compression zone 110 will be described in detail.

As shown in FIG. 7, when the inner rotor 200 rotates clockwise about the center hole 240, the first compression vane 210 starts to be inserted into the first compression region 110. That is, the first sealing reference surface 212 of the first compression vane 210 approaches the left side 112 of the first compression zone 110 and the second sealing reference surface 215 of the first compression vane 210, 0.0 > 115 < / RTI > of the first compression zone 110. At this time, the first compression region 110 is a free open space state in which the fluid introduced through the suction port 510 is filled.

8, when the first compression vane 210 is inserted into the first compression region 110, the first hermetic surface 212 of the first compression vane 210 is compressed into the first compression region 110, The second sealing reference surface 215 of the first compression vane 210 contacts the right boundary surface 115 of the first compression region 110 B). That is, the upper blade surface 213, the right blade surface 214 of the first compression blade 210, the left side surface 112 of the first compression region 110, the compression surface 113, 1 < / RTI > compression region 110 is closed.

As shown in FIG. 9, when the inner rotor 200 and the outer rotor 100 further rotate at the time when the closed space is formed as shown in FIG. 8, the upper wing surface The sealed space in the first compression region 110 between the right wing surface 214 and the left side surface 112 of the first compression region 110, the compression surface 113 and the right side surface 114 is sealed . Specifically, the first sealing reference surface 212 of the first compression vane 210 moves while contacting the left side surface 112 of the compression region 110 (see A), and the first sealing vane 210 of the first compression vane 210 A portion of the right wing surface 214 remains in contact with a portion of the right side surface 214 (see B) after the second hermetically sealed reference surface 215 abuts the right side interface 215 of the first compression region 110, , The upper wing surface 213 of the first compression wing 210 comes close to the compression surface 113 side. Thus, the first wing surface 213, the right wing surface 214 of the first compression wing 210, the left side surface 112 of the first compression zone 110, the compression surface 113, the right side surface 114, The closed space between the compression regions 110 is kept closed while the closed space is reduced. In this process, the fluid in the closed space is moved to the outside through the first and second discharge passages (550, 610) and the discharge port (620) through the first and second discharge holes (520, 540). If the fluid in the closed space is a gas, compression occurs and is discharged to the first and second discharge holes 520 and 540. If the fluid in the closed space is a liquid, it is pumped into the first and second discharge holes 520 and 540. Here, the first sealing reference surface 212 of the first compression vane 210 is rounded in the form of an arc. The first sealing reference surface 212 of the first compression vane 210 moves while touching the left side surface 112 of the compression region 110 (see A), and in this case, The contact of the first hermetic reference surface 212 in contact with the first hermetic seal 112 moves along a circular arc that is rounded. This applies in common to the first sealing reference surface provided in each of the three compression vanes.

10, the inner rotor 200 and the outer rotor 100 continue to rotate, respectively, so that the sealed compression between the upper wing surface of the first compression wing 210 and the compression surface 113 The area 110 is further reduced in a sealed state.

A portion of the upper wing surface 213 of the first compression vane 210 continues to approach the compression surface 113 of the compression region 110 and eventually contacts the compression surface 113 of the first compression region 110, The contraction of the confined space continues to occur, whereby the fluid in the confined space continues to move to the outlet 620. [ A portion of the upper wing surface 213 of the first compression wing 210 contacting the compression surface 113 of the first compression zone 110 is sequentially moved so that the hermetically closed space formed in the first compression zone 110 is minimized The fluid movement is completed. After the first wing surface 210 of the first compression wing 210 has abutted against the compression surface 113 of the first compression zone 110, the sealed space on the compression surface 113 is moved from the right side surface 114 to the left side surface Since the upper wing surface 213 of the first compression wing 210 continues to be squeezed in the direction of the compression surface 113, the fluid in the closed space on the compression surface 113 is entirely moved to the outside. In addition, since the direction in which the fluid finally moves to the outside is the left upper surface of the closed space, it is preferable that the first and the second discharge holes 520, 540 are disposed corresponding to this direction OUT. That is, it is preferable that the first and the second discharge holes 520 and 540 are disposed corresponding to the upper left surface of the first to fourth compression regions 110 to 140.

On the other hand, while the first compression vane 210 performs the operation of moving the fluid to the last in the closed space of the first compression zone 110, the second compression vane 220 is moved close to the second compression zone 120 do. The second compression vane 220 is also close to the second compression zone 120 to create a hermetic zone with the second compression zone 120 and to move the fluid therein while reducing the hermetic zone created.

As shown in FIG. 11, as the outer rotor 100 and the inner rotor 200 continue to rotate, fluid movement is completed in the closed space of the first compression region 110 formed by the first compression vane 210 The first compression vane 210 is separated from the first compression region 110 while the right wing surface 214 of the first compression vane 210 is separated from the right side surface 114 of the first compression region 110 Start.

The first sealing reference surface 222 of the second compression vane 220 is brought into contact with a certain portion of the lower end portion of the left side surface 122 of the second compression region 120 The second sealing reference surface 225 abuts against the right interface 125 of the second compression region 120 (see D) and the upper wing surface 223, the right wing surface 224, A closed space is created in the second compression region 120 between the left side 122, the compression side 123 and the right side 124 of the second compression region 120.

12, as the outer rotor 100 and the inner rotor 200 continue to rotate, the right wing surface 214 of the first compression wing 210 is pressed against the right side surface of the first compression zone 110 The first compression vane 210 is spaced apart from the left side 112 of the first compression zone 110 after the left wing surface 211 of the first compression vane 210 is spaced from the first compression zone 110, And continues to depart from the main body 110.

On the other hand, between the upper wing surface 223 of the second compression vane 220, the right wing surface 224 and the left side surface 122 of the second compression zone 120, the compression surface 123 and the right side surface 124 The sealed compression region 120 is reduced in the closed state. Specifically, the first sealing reference surface 222 of the second compression vane 220 moves while touching the left side surface 122 of the second compression zone 120 (see C), and the second compression vane 220 After a portion of the right wing surface 224 is in contact with a part of the right side surface 124 after the second sealing reference surface 225 of the second compression reference surface 225 contacts the right boundary surface 125 of the second compression region 120 The upper wing surface 223 of the second compression vane 220 is brought close to the compression surface 123 side. Therefore, the closed space between the upper wing surface 223 of the second compression vane 220 and the compression surface 123 is kept closed, and the closed space is reduced. In this process, the fluid in the closed space is moved to the outside through the first and second discharge passages (550, 610) and the discharge port (620) through the first and second discharge holes (520, 540).

13, as the outer rotor 100 and the inner rotor 200 continue to rotate, the left wing surface 211 of the first compression wing 210 moves to the left side of the first compression region 110 The first compression vane 210 is further away from the first compression vane 210 and the upper vane surface 213 of the first compression vane 210 passes ahead of the right boundary surface 115 of the first compression zone 110, 1 < / RTI >

On the other hand, a portion of the upper wing surface 223 of the second compression vane 220 continues to approach the compression surface 123 of the second compression zone 120 and eventually reaches the compression surface 123 of the second compression zone 120, So that the fluid in the closed space continues to be moved to the discharge port 620. [ A portion of the upper wing surface 223 of the second compression vane 220 which is also in contact with the compression surface 123 of the second compression zone 120 is moved in a sequential manner as in the operation of the first compression vane 210 described above The closed space formed in the second compression region 120 is minimized or eliminated to complete the fluid movement (see C). Second Compression Blade 220 After a portion of the upper winging surface 223 contacts the compression surface 123 of the second compression region 120 the sealed space on the compression surface 123 is moved from the right side surface 124 to the left side surface Since the upper wing surface 223 of the second compression vane 220 continues to be squeezed in the direction of the compression surface 123, the fluid in the closed space on the compression surface 123 is entirely moved outward.

As shown in FIG. 14, as the outer rotor 100 and the inner rotor 200 continue to rotate, the first compression vane 210 completely deviates from the first compression region 110, The first compression region 140 is closely adjacent to the fourth compression region 140 to form a closed region between the upper wing surface 213 of the first compression region 110 and the compression surface of the fourth compression region 140 in the region 140 do.

On the other hand, when the fluid movement is completed in the closed space of the second compression region 120 formed by the second compression vane 220, the right wing surface 224 of the second compression vane 220 moves to the second compression region 120 The second compression vane 220 begins to depart from the second compression zone 120 while being spaced from the right side 124 of the second compression zone 220. [

Also, the first sealing reference surface of the third compression vane 230 is brought into contact with a certain portion of the lower left end surface of the third compression region 130 (see E), and the second sealing reference surface of the third compression vane 230 (See F), a closed space is formed in the third compression region 130 between the upper wing surface of the third compression vane 230 and the compression surface. The subsequent operation is the same as the above-described operation in which the first or second compression vanes 210 and 220 close the first and second compression regions 110 and 120 to create a closed space and to discharge the fluid in the closed space to the outside.

7 to 14, as the outer rotor 100 and the inner rotor 200 continue to rotate, the first to third compression vanes 210 to 230 provided in the inner rotor 200, Sequentially approach the first to fourth compression regions 110 to 140 provided in the outer rotor 100 to form a closed region. As the outer rotor 100 and the inner rotor 200 continue to rotate, the first to third compression vanes 210 to 230 approach the first to fourth compression regions 110 to 140, , The fluid in the closed region is discharged to the outside. The fluid sucked into the inner region through the inlet port 510 is sent to the first to fourth compression zones 110 to 140 by the first to third compression vanes 210 to 230 of the inner rotor 200, The fluid to be placed in the closed region formed on the first to third compression vanes 210 to 230 is discharged to the outside while the closed region is reduced.

Since the outer rotor 100 and the inner rotor 200 are continuously rotating, one of the first to third compression vanes 210 to 230 is always in the first to fourth compression regions 110 to 140 One is closed to create a closed area, and as it narrows, the fluid in it is discharged to the outside. In this case, one of the first to third compression vanes 210 to 230 always approaches one of the first to fourth compression regions 110 to 140 at about 12 o'clock to make a closed region. In addition, it reduces the airtight area made at about 2 o'clock, minimizes or eliminates the airtight area made at about 4 o'clock, and discharges the fluid inside it to the outside. Then, from about 5 o'clock to 10 o'clock, the compression wing which made the closed region deviates from the compression region and prepares for compression next time. That is, since the outer rotor 100 and the inner rotor 200 according to the present embodiment continuously rotate and have a plurality of compression regions and compression vanes respectively, the first to third compression vanes 210 to 230 are always in contact with the outer rotor 100, One of the first to fourth compressed regions 110 to 140 may be made close to the closed region and the fluid may be transported while narrowing it. This makes it possible to compress or pump many fluids quickly. Therefore, a discharge area for discharging the sealed fluid is required to correspond to the compression area in a one-to-one correspondence, and its position may be arranged at the last point where the closed area in the compression area is minimized as described above. In this case, a device for discharging may be disposed at the left upper end of the compression region. Also, as described above, the first to third compression vanes 210 to 230 are formed asymmetrical curved surfaces on both sides thereof, which are inserted into one of the first to fourth compression areas 110 to 140, The most effective way to create an enclosure is to create.

The essential components of the fluid transfer device according to the embodiment of the present invention are the outer rotor 100 and the inner rotor 200. The shapes of the first to fourth compression regions 110 to 140 of the outer rotor 100 are determined according to the shapes of the first to third compression blades 210 to 230 of the inner rotor 200. The first to third compression vanes 210 to 230 provided in the inner rotor 200 are rotated about the central axis of the inner rotor 200 while being rotated in contact with the inner circle space generated by the outer rotor 100, A hypotrochoid curve created by each of the first to third compression vanes 210 to 230 is determined and the first to fourth internal vanes 210 to 230 of the outer rotor 100 are defined on the basis of the boundary point of the locus of the hypotrochoid curve. And the compressed areas 110 to 140 are implemented.

As described above, a curve in which points connected to an inscribed circle are drawn when an inscribed circle in contact with a reference circle moves while inscribing the reference circle is called a hypotrochoid curve.

Therefore, when the first to third compression vanes 210 to 230 rotate about the central axis of the inner rotor 200 while contacting the inner circle space generated by the outer rotor 100, The trajectory generated by the third compression vanes 210 to 230 is the hypotrochoid curve. The shapes of the first to fourth compression regions 110 to 140 are determined by using the hypotrochoid curve.

In other words, the first to fourth compression wings 210 to 230 are provided with the first sealing reference surface, the upper wing surface, the right wing surface, and the second sealing reference surface, respectively, by the hypotrochoid curve, The first left side, the first compressed side, and the second right side, which are respectively provided in the first and second sides 110 to 140, respectively. Since the first to third compression vanes 210 to 230 are realized in the same form, it can be considered that the first to fourth compression regions 110 to 140 are defined by the hypotrochoid curve generated by one compression vane . Such a hypotrochoid curve can be obtained by the following equations (1) and (2). Where r is the radius of the inner rotor, R is the radius of the reference circle, and in this case is the circle given by the inner space of the outer rotor 100. Here, d is a point connected to the inscribed circle, and here refers to a point on the outer circumference of the inner rotor 200 compression wing.

Equation 1: X (?) = R (k-1) cos? + D cos (

Equation 2: Y (?) = R (k-1) sin? - d sin ((k-

[r: radius of inscribed circle, R: radius of reference circle, k: R / r, d:

Continue to examine the surface of the compression wing. The left wing surface (for example, 211) of the first to third compression wings 210 to 230 is concave. When the right wing surface 214 is embossed, the first to fourth compression areas 110 to 140 are formed on the left side and the right side. For efficient operation, the right wing surface of the compression vane of the fluid delivery device according to the present embodiment is implemented with involute curves. The first sealing reference surface (e.g., 211) abuts the left side (e.g., 112) of the compression region and the second sealing reference surface (e.g., 215) A portion of the curved right-handed wing surface (e.g., 214) must be in continuous contact with the mouth of the right-handed surface (e.g., 114) while touching the right bounding surface 115. One of the appropriate curves for this condition is the involute curve.

The fluid conveying apparatus according to the embodiment of the present invention described above is for the case where the inner rotor has three compression blades and the outer rotor has four compression regions. In addition to such a case, the fluid transfer device of the present invention can be variously implemented in a manner of determining the internal compression region shape of the outer rotor by the hypotrochoid curve generated by the locus of the compression wing of the inner rotor.

First, in the above-described embodiment in which the inner rotor has three compression wings and the inner rotor has four compression regions, it is possible to implement only two or one compression wings instead of three. That is, any one of the three internal blades of the rotor shown in FIG. 4 may be removed and only two of them may be implemented, or two of them may be eliminated to realize only one. As described above, even if the inner rotor has one or two compressing blades, it is not difficult to implement the above-described fluid movement operation. However, the compression vane approaches the compression region and the number of times of making the closed region is reduced, so that the efficiency of transferring the fluid may be relatively decreased.

In addition, the number of inner rotor compression vanes and the number of outer rotor compression regions can be continuously increased. For example, the number of compression regions provided in the outer rotor can be increased to five, and the number of compression wings can be increased to four. In this case as well, the compression vane described in FIGS. 7 to 14 can perform the operation of transferring the fluid while creating a closed space in the compression region and reducing the closed space. It is also possible to increase the number of compression zones provided in the outer rotor by six or more and increase the number of compression wings by five or more.

The number of inner rotor compression vanes and the number of outer rotor compression regions can be increased by the same number. In this case, the inner rotor compression vanes may be arranged so that their positions are equally spaced. And four compression wings are disposed at 90 degrees.

Although the number of the compression blades provided in the inner rotor is only one less than the number of the compression regions provided in the outer rotor, the number of the compression blades may be at least one to implement the fluid transfer device of the present invention.

In the fluid transfer device in which the compression blades provided in the inner rotor are maintained at equal intervals, the number of the compression blades provided in the inner rotor is only one less than the number of compression regions provided in the outer rotor, It can achieve the most optimal efficiency, but at least it can work well enough. That is, the number of compression blades provided in the inner rotor should be smaller than the number of compression regions provided in the outer rotor. The number of compression wings should be reduced to one or more in the number of compression zones (n) (number of compression wings = < number of compression zones-1) (The number of compression wings = the number of compression zones-1). If the number of compression zones is n, the number of compression wings is from 2 to n-1.

The fluid transfer device according to the present invention will now be described with reference to the case where a plurality of compression vanes provided in the inner rotor are arranged at equal intervals and the interval is equal to the interval between pressure regions provided in the outer rotor will be. However, in implementing the fluid transfer device of the present invention, the distance between the compression blades of the inner rotor may be equal to or smaller than the interval between the compression region and the compression region of the outer rotor. In the case of achieving the optimum efficiency, the distance between the compression blades of the inner rotor is equal to the interval between the compression region and the compression region provided in the outer rotor.

The relationship between the inner rotor and the outer rotor, which is a key feature of the fluid transfer device of the present invention, can be described as follows. The length of the outer circumferential surface divided by the number of compression regions has the greatest amount of fluid movement effect when the length of the outer circumferential surface of the inner rotor is equal to the length divided by the number of compression blades. That is, it is possible to realize a fluid transfer device capable of performing fluid movement most efficiently when the interval between compression vanes is equal to the interval between compression zones. In this case, the ratio of the number of compression blades to the number of compression regions is equal to the ratio of the outer peripheral surface of the inner rotor to the outer peripheral surface of the outer rotor.

The central axis of the outer rotor and the central axis of the inner rotor rotate while rotating the outer rotor and the inner rotor while the central axis of the outer rotor rotates with the center axis of the inner rotor. .

FIGS. 15 to 18 are views for explaining the operation of the fluid transfer device according to the second embodiment of the present invention, particularly showing the inner rotor and the outer rotor.

15 to 18, the fluid transfer device according to the second embodiment of the present invention is for a case where three compression blades of the inner rotor and four compression regions of the outer rotor are used. And the inner rotor is rotated by transmitting the power using the inner rotor center axis. When the inner rotor is rotated, the compression vanes of the inner rotor are inserted into the compression regions of the outer rotor, thereby creating a sealed space in the compression regions corresponding to the raised compression vanes (see FIGS. 15A and 15B). As the inner rotor continues to rotate, the closed space formed at this time is reduced as the upper wing surface of the compression wing becomes closer to the compression region (see FIGS. 16A and 16B).

The upper wing face of the compression vane then contacts the compression face of the compression zone, and the face contacting the compression face moves to minimize or eliminate the hermetically closed space (see FIGS. 17 and 18A). In this process, the fluid in the closed space can be discharged to the outside. Subsequently, the compression wing which has been inserted after minimizing or eliminating the confined space escapes the compression region. The operation shown in FIGS. 15 to 18 is the same as the formation and disappearance of the closed space in FIGS. 7 to 14, so that the detailed description of the operation will be omitted.

FIG. 19 is a view for explaining the operation of the fluid transfer device according to the third embodiment of the present invention, particularly showing the inner rotor and the outer rotor.

As shown in Fig. 19, the upper wing surface 213A of the compression wing of the inner rotor 200A can be flattened instead of making a circular arc. Thus, if the upper blade surface 213A of the compression blade of the inner rotor 200A is made flat, the compression surface 113A of the compression area of the outer rotor 100A should have a convex curved surface or a flat surface accordingly . Here, the compression surface 113A of the compression region of the outer rotor 100A is formed into a convex curved surface.

As such, the inner rotor having a plurality of compression vanes rotates in an outer rotor having a plurality of compression zones, and the compression vanes create an enclosed area inside the compression zone, reduce the created hermetic zone, If it can be transported to the outside, it is possible to implement compression wings in various forms.

FIGS. 20 and 21 are views for explaining the operation of the fluid delivery device according to the third embodiment of the present invention.

The outer rotor 100 and the inner rotor 200, which are core components of the fluid transfer device of the present invention, rotate with different center axes. The outer rotor 100 rotates around the outer rotor center axis 560 and the inner rotor 200 rotates about the inner rotor center axis 320. 7 to 14, the inner rotor 200 has three compression vanes 210 to 230 alternately inserted into the compression regions 110 to 140 of the outer rotor 100, Thereby reducing the airtightness of the airtight space, thereby compressing and transporting the fluid in the airtight space. Accordingly, the outer rotor 100 and the inner rotor 200 must rotate in conjunction with each other.

The fluid transfer device according to the present embodiment provides the outer rotor 100 and the inner rotor 200 to rotate in conjunction with each other using the belt unit 700. [ The belt portion 700 includes a first belt 710, a second belt 720, and a belt connecting shaft 730. The first belt 710 interlocks with the outer rotor center shaft 560 of the outer rotor 100 and the belt connecting shaft 730. The second belt 720 interlocks the inner rotor center axis 320 of the inner rotor 200 with the belt connecting shaft 730. The rotation of the belt connecting shaft 730 is interlocked with the rotation of the outer rotor central axis 560 of the outer rotor 100 and the inner rotor center axis 320 of the inner rotor 200, The inner rotor 100 and the inner rotor 200 can be interlocked with each other. Here, the outer rotor 100 and the inner rotor 200 can be interlocked with each other by using two belts as examples. In the present invention, the outer rotor 100 and the inner rotor 200 can be interlocked Various types of mechanical devices are available.

In the fluid conveying apparatus of the present invention, the inner rotor is provided inside the outer rotor. In some cases, when the inner rotor is relatively smaller than the outer rotor, a plurality of inner rotors may be provided. A plurality of inner rotors are provided, and each of the inner rotors is rotatable about a rotation axis, and sequentially inserted into a plurality of compression regions provided in the outer rotor to form a closed region in the compression region. Such a plurality of internal rotors is more advantageous when a high-pressure pumping operation is required.

In the above-described fluid transporting apparatus of the present invention, in transferring the fluid, a portion where friction of the internal components occurs is minimized. There is only an area where friction wings of the inner rotor contact with each other in the process of performing an escape operation after being inserted into the compression region of the outer rotor. Therefore, the fluid transfer device of the present invention generates little noise when transferring the fluid. If this is applied to various fields, too much noise is generated in compressing or pumping the fluid, which can completely solve the problematic part. For example, when driving a home appliance, a compressor used in a factory, a blower blowing a gas, an oil or a pump for pumping water, too much noise was generated, but there were many restrictions. However, the fluid transfer device of the present invention can realize various compressors and pumps for household appliances or factories with little noise.

Further, in the fluid transferring apparatus of the present invention, since the portion where the friction of the internal components is minimized in transferring the fluid, the generation of heat is greatly reduced, and therefore, the blower, the pump, or the compressor Can be implemented.

In addition, the fluid transfer device of the present invention is advantageous in that it is compact because there are very few essential components required for transferring the fluid and all the components are simple shapes. Although the conventional structure of the blower, the compressor and the pump is too complicated to be compact, the fluid transfer device of the present invention has a very small number of essential components and all the components are simple shapes, Can be implemented in a small size. Since the fluid transfer device of the present invention is realized with low noise and small size, it can be realized as a desk or a product necessary for a personal computer.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of limitation, I will understand. Therefore, the scope of the present invention should not be limited to the described embodiments, but should be determined by the scope of the appended claims, as well as the appended claims.

Claims

An outer rotor having a cylindrical interior and having an inner space into which fluid is introduced and having at least three compression regions formed in the inner space at regular intervals of the same shape;
An outer circumferential surface which is rotatable about the central axis and which is disposed in the inner space of the outer rotor and which is formed at both sides of the sealing reference surface for sealing the compression region inserted into the compression region and which is in contact with the inner circumferential surface of the compression region by rotation An inner rotor having at least one compression vane formed therein,
A suction port for sucking the fluid into the inside of the outer rotor,
A discharge port for discharging the fluid in the compression region to the outside,
A first plate for sealing one side of the outer rotor,
A second plate for sealing the other side surface of the outer rotor,
And a fluid passage.

The method according to claim 1,
Wherein the compression vane of the inner rotor is embodied as an asymmetric curved surface on both sides.

The method according to claim 1,
Further comprising a power transmitting portion for rotating the central axis of the inner rotor.

The method according to claim 1,
Further comprising a power transmission part for interlocking and rotating the inner rotor and the outer rotor.

5. The method according to any one of claims 2 to 4,
Wherein the power transmitting portion is constituted by using at least one of a gear, a timing belt, and a chain.

The method according to claim 1,
And the suction port and the discharge port are formed on the second plate.

The method according to claim 1,
Wherein the discharge port is formed to be equal to the number of the compression regions, and a check valve corresponding thereto is attached to the discharge port.

The method according to claim 1,
Wherein the compressed region is formed in a 'C' shape by a left side, a compressed side, a right side and a right side.

8. The method of claim 7,
Wherein the first sealing reference surface of the compression vane is in contact with the left side surface of the compression region and the second sealing reference surface of the compression vane is in contact with the right side or right side surface of the compression region to form a closed space.

The method according to claim 1,
Wherein the number of the compression blades is one or more smaller than the number of the compression regions and is formed so as to maintain equal intervals in the case of a plurality of compression blades.

The method according to claim 1,
Wherein the ratio of the number of the compression zones to the number of the compression blades is equal to the ratio of the circumferential length of the outer circumferential surface of the outer rotor to the circumferential length of the outer circumferential surface of the inner rotor.

An inner rotor rotating around a central axis and formed with at least two compression protrusions protruding in the same shape at equal intervals and having an outer peripheral surface of the compression vanes rotating about the central axis in a cylindrical shape;
Wherein the inner rotor is disposed in the inner rotor, and the compression regions in which the compression vanes of the inner rotor are inserted to form the closed space are formed at equal intervals of the same shape, and the number of the compression regions is at least 1 With many external rotors,
A suction port for sucking the fluid into the inside of the outer rotor,
A discharge port for discharging the fluid in the closed space formed in the compression region to the outside,
A first plate for sealing one side of the outer rotor,
A second plate for sealing the other side surface of the outer rotor,
And a fluid passage.

13. The method of claim 12,
Wherein the compression vane of the inner rotor is embodied as an asymmetric curved surface on both sides.

13. The method of claim 12,
Further comprising a power transmitting portion for rotating the central axis of the inner rotor.

13. The method of claim 12,
Further comprising a power transmission part for interlocking and rotating the inner rotor and the outer rotor.

16. The method according to any one of claims 13 to 15,
Wherein the power transmitting portion is constituted by using at least one of a gear, a timing belt, and a chain.

13. The method of claim 12,
And the suction port and the discharge port are formed on the second plate.

13. The method of claim 12,
Wherein the discharge port is formed to be equal to the number of the compression regions, and a check valve corresponding thereto is attached to the discharge port.

13. The method of claim 12,
Wherein the compression vane is formed in a "C" shape by a left wing surface, a first hermetic surface, an upper wing surface, a right wing surface, and a second hermetic surface.

20. The method of claim 19,
Wherein the compressed region is formed in a 'C' shape by a left side, a compressed side, a right side and a right side.

20. The method of claim 19,
Wherein the first sealing reference surface of the compression vane is in contact with a left side surface of the compression region and the right side surface or the second closing reference surface of the compression vane is in contact with a right side surface or a right side surface of the compression region to form a closed space. Fluid transfer device.

20. The method of claim 19,
Wherein the first sealing reference surface of the compression vane is formed in the form of an arc.

13. The method of claim 12,
Wherein the compressed surface of the compression zone of the outer rotor also has a convex curved surface when the upper wing surface has a flat surface.

13. The method of claim 12,
Wherein the compressed surface of the compression zone of the outer rotor has a corresponding concave curved surface accordingly if the upper wing surface has a curved surface.

13. The method of claim 12,
Wherein the ratio of the number of the compression zones to the number of the compression blades is equal to the ratio of the circumferential length of the outer circumferential surface of the outer rotor to the circumferential length of the outer circumferential surface of the inner rotor.

13. The method of claim 12,
The center axis of the outer rotor and the center axis of the inner rotor are determined such that the outer rotor and the inner rotor have center axes at different positions and the inner surface of the outer rotor and the outer circumferential surface of the inner rotor are in contact with each other. .

13. The method of claim 12,
Wherein the distance between the compression blades of the inner rotor is equal to the distance between the compression region and the compression region formed in the outer rotor.

An inner rotor rotating around a central axis and formed with at least two compression protrusions protruding in the same shape at equal intervals and having an outer peripheral surface of the compression vanes rotating about the central axis in a cylindrical shape;
Wherein an inner rotor is disposed in the inner rotor and a compression region formed by the hypotrochoid trajectory of the compression vane is formed at equal intervals of the same shape and the number of compression regions is at least With more than one outer rotor,
A suction port for sucking the fluid into the inside of the outer rotor,
A discharge port for discharging the fluid in the compression region to the outside,
A first plate for sealing one side of the outer rotor,
A second plate for sealing the other side surface of the outer rotor,
And a fluid passage.

29. The method of claim 28,
Wherein the compression vane of the inner rotor is embodied as an asymmetric curved surface on both sides.

29. The method of claim 28,
And a left side, a compressed side, and a right side of the compressed region are generated by a hypotrochoid curve in which the sealing reference surface, the upper wing surface, and the right wing surface of the compression wing move.

32. The method according to any one of claims 29 to 30,
The hypotrochoid curve can be expressed by the following Equation 1 and Equation 2
Equation 1: X (?) = R (k-1) cos? + D cos (
Equation 2: Y (?) = R (k-1) sin? - d sin ((k-
(r: radius of the inner rotor, R: circle given by the inner space of the outer rotor, and d: one point on the outer line of the compression wing of the inner rotor)
And wherein the fluid flow rate is obtained by the following equation (1).

29. The method of claim 28,
Wherein the right wing surface of the compression vane is convex and the right side surface of the corresponding compression zone is concave.

29. The method of claim 28,
Wherein the right wing surface of the compressed region has the characteristics of an involute curve.

An outer rotor having a cylindrical interior and having an inner space into which fluid is introduced and having at least three compression regions formed in the inner space at regular intervals of the same shape;
An inner rotor disposed in the inner space of the outer rotor and having at least one compression vane sequentially inserted into the compression regions each time one rotation is made about the central axis;
A suction port for sucking the fluid into the inside of the outer rotor,
A discharge port for discharging the fluid in the compression region to the outside,
A first plate for sealing one side of the outer rotor,
A second plate for sealing the other side surface of the outer rotor,
And a fluid passage.

35. The method of claim 34,
Wherein the compression vane of the inner rotor is embodied as an asymmetric curved surface on both sides.

35. The method of claim 34,
Further comprising a power transmitting portion for rotating the central axis of the inner rotor.

35. The method of claim 34,
Further comprising a power transmission part for interlocking and rotating the inner rotor and the outer rotor.

37. The method according to any one of claims 35 to 37,
Wherein the power transmitting portion is constituted by using at least one of a gear, a timing belt, and a chain.

35. The method of claim 34,
And the suction port and the discharge port are formed on the second plate.

35. The method of claim 34,
Wherein the discharge port is formed to be equal to the number of the compression regions, and a check valve corresponding thereto is attached to the discharge port.

35. The method of claim 34,
Wherein the compressed region is formed in a 'C' shape by a left side, a compressed side, a right side and a right side.

35. The method of claim 34,
Wherein the first sealing reference surface of the compression vane is in contact with the left side surface of the compression region and the second sealing reference surface of the compression vane is in contact with the right side or right side surface of the compression region to form a closed space.

35. The method of claim 34,
Wherein the number of the compression blades is one or more smaller than the number of the compression regions and is formed so as to maintain equal intervals in the case of a plurality of compression blades.

35. The method of claim 34,
Wherein the ratio of the number of the compression zones to the number of the compression blades is equal to the ratio of the circumferential length of the outer circumferential surface of the outer rotor to the circumferential length of the outer circumferential surface of the inner rotor.