WO2001090578A1

WO2001090578A1 - A flow pump having the rotary vanes and valves

Info

Publication number: WO2001090578A1
Application number: PCT/KR2000/000586
Authority: WO
Inventors: Pyeong-Gyu Lim
Original assignee: Lim Pyeong Gyu
Priority date: 2000-05-22
Filing date: 2000-06-09
Publication date: 2001-11-29
Also published as: AU5111900A; KR20000050177A; KR100375943B1

Abstract

The present invention relates to a flow pump using rotary vanes and valves, which provides a new mechanical system having the simplified structure of fluid transporting system comparing with the type of the piston operation, the vane application, the root or the gear system in the prior arts of the flow pump system or any kind of the fluid transporting system. A pump having the rotary vanes and valves comprises said rotor (3) which is axially installed and is rotatably supported in said housing (2), and forms vanes (4) at least two on the periphery of rotor (3), said two rotary valves (7) having said concave groove (6) at least one on the periphery of the rotary valve are axially installed along the longitudinal direction of said flow path (5) formed in the housing (2), said master gear (8) and said slave gear (9) axially fixed on said rotor (3) said rotary valve (7) respectively are combined each other for the tooth-coupled operation.

Description

A flow pump having the rotary vanes and valves

Technical Field

The present invention relates to a flow pump ,'ύsing the rotary vanes and valves, which provides a new mechanical system having a simplified structure of fluid transporting system comparing with the type of the piston operation, the vane application, the .root or the gear system in the prior arts of the flow pump or any kind of the fluid transporting system.

Background Art

Various kinds of flow pumps have been commonly used and have been sophisticatedly devised for the high efficiency, the distinct power and the versatile usage for transporting liquid or gas in the prior art.

But for the piston-type of a flow pump or an engine as shown in US 6,062,188, it shows relatively complicate structure and consists of many assembly parts resulting the negative results such as high cost for making a complete production or relatively low efficiency for pumping fluid or gas.

The vane-type flow pump, for examples, of US .5,947,71 , US

5,290,648 or US 4,447,196, can be found in the prior art. But this kind of type has also disadvantage in that the , vane of rotor compresses the cylinder's wall resulting a fast breakdown due to the high frictional resistance and abrasion.

Regarding to the typical gear-type of flow pump in the prior art, as shown in US 6,048,187 or US 6,062,836, it also reveals a shortage in the endurance because it is forced to rotate by the tooth-coupled gears and the structure has low efficiency limit for pumping the operational fluid.

Generally speaking, the mechanical structure of pumps or motors in the prior art is apt to generate high frictional force which produces abrasion, frictional loss and low efficiency for the pump or the motor system while in the stroke process. In addition, the flow pumps or the motors according to the prior arts also, lack in versatility for its usage due to the sole purpose for adapting its functional demand.

Furthermore, they also have a demerit for generating immediate torque for transporting fluid or forming the immediate ^, pressure in the early stage of pumping process.

Disclosure of the Invention

In order to improve a high pressure pump or a hydraulic motor in the prior art due to the above-mentioned reasons, a flow pump according to the present invention provides a new^' mechanism of pumping system having the high endurance, the low frictional loss, the versatile use and the high efficiency.

Under the embodiment of present invention in addition, the immediate achievement to the maximum pressure and torque can be accomplished concurrently when the system starts to rotate.

Furthermore, the present invention can be utilized as a combining use for a high pressure pump and hydraulic motor or by adding simple apparatus to the present invention, the present system also can be applicable to the additional use as a precise fluid gauge. Accordingly, another embodiment of present invention is also to provide a versatile pumping system for transporting fluid.

Brief Description of the Drawings

The present invention will be fully understood from the detailed description given hereinbelow and the accompanying- drawings which are given by way of illustration only, and 'thus are not limitative of the present invention, and wherein : '

Fig. 1 is a sectional view which shows the present invention of flow pump. 'I, .. Fig. 2 relates to a longitudinal cross sectional view of the present invention. , '

Fig. 3 is a sectional view illustrating the main- embodiment of the present invention.

Fig. 4 illustrates diagrammatically how the system works for transporting fluid gradually. Best Mode for Carrying Out the Invention

An explanation of the detailed constitution under the present invention will now be discussed, using the forementioned configuration of the device of the present invention. By means of the rotational power exerted on the rotating shaft in the housing or the pressure difference between the incoming and' outgoing fluid, the incoming fluid flows initially into the void part of the casing. And then, the pressurized fluid in the casing causes the rotating force to the central rotor in counter-clockwise^' direction. In cooperating .with the rotational motion of rotor, the rotary valve having the groove on the periphery revolves i'n the clockwise¹ direction together with the vane of rotor so that the outwardly turning vane can draws the fluid along the rotating direction. Under the embodiment of present invention, the present pumping system can ' neglect any frictional resistance which might be occurred by the recurrent process of maintaining the tightness between the vanes of" rotor and the rotary valves.

In addition to the above-mentioned mechanism, ^' the cylindrical shape of rotor and the rotary valve in this system provide an excellent endurance and a simple structure having ' low trouble rate which can eliminate disadvantages in the prior of pumping system or the flow motor system. ^{■ '}. ^:

The pumping system under the present invention provides an rotor (3) which is axially installed and rotatably supported by means of, the centrical motor (not shown on the figures) of the housing (2). And at least two vanes (4) formed on the outer periphery of the above-mentioned rotor (3) are configured maintaining the constant gap between them. The above-mentioned vanes (4) also can be- constructed in an assembly type for combining with the rotor (3) depending on its functional requirement. And along the longitudinal direction of the flow path (5) formed on the housing (2), two rotary valves (7) at least having the concave groove (6) are axially installed so that the rotary valves can rotate corresponding to the rotational motion of the rotor (3). For the driving of rotational motion, a master gear (8) and a slave gear(9) axially fixed on the rotor (3) and rotary^' valve (7) respectively are combined each other for the tooth-coupled operation.

In other words, if the above-mentioned rotor (3) rotates counter, clockwise direction, the mechanical structure of present invention is devised so as to rotate in the clockwise direction Tor ^"the rotary valve (7) respectively.

The rotating periphery of rotor . (3) and rotary valve (7) according to the above-mentioned mechanism provides¹ tight sealing for the fluid flow. Whenever the vane (4) of the .rotor^": (3) meets the ^■ rotary valve (7) while in the tooth-coupled operation, the concave groove (6) as a coupling element formed on the rotary valve (7) is corresponded such that the continuous rotation of rotor and rotary valves can be achieved.

Only a concave groove (6) along the periphery of rotary valve (7) is formed for combining with two vanes on the rotor while two concave grooves for the three configuration of vanes respectively. The rotor (3) and rotary valve (7) are axially fixed by the bearing (10) installed on the both edges of housing (2). And depend on its application, this system can be widely applied to a- flow meter by measuring the pulses by means of the pulse sensor (12) located on the housing (2). For the application as a flow meter based on the . present embodiment, the flow measuring system consists of a pulse ■ sensor and a pulse target (1 1 ) which is axially installed on the rear part of rotor (3). According to the above-mentioned structure, the flow pumping device (1 ) under the present embodiment can transport the. pressurized fluid by rotating the rotor (3) using the driving source like a motor. To the contrary, the rotor can be rotated by the pressurized fluid depending on its flow rate so as to measure the numbers of revolution which is a proportional quantity of the flow rate of fluid in the system.

For the more tangible understanding to the present invention the flow pumping system having the rotor driven by a motor will be described hereinbelow. If the rotor (3) rotates counterclockwise by the driving source like a motor as shown on the fig. 4, the rotary valve (7) revolves clockwise to the contrary by combining with the master gear (8) of rotor (3). The entered fluid through the incoming gate of fluid path (5) by the rotational driving force of rotor (3) and rotary valve (7) is transported through the fluid path (5) formed by the vane (4) and housing (2). At that time, the opposite rotary valve (7) to the vane (4) of rotor (3) is tightly cooperated with the rotating periphery of rotor (3) for the unidirectional fluid flow inside the chamber. The sealing mechanism between the rotor and the rotary valve by means of the rotational motion provides the unidirectional flow pumping in cooperation with the configuration of vanes on the rotor so that the flow speed is proportional to the revolution of those revolving parts. By the continuous rotation of rotor (3), the fluid moves gradually to the out gate of the fluid path (5) after passing the area of vane (4). At the moment of the out going stage of fluid, the fluid can not be overflowed in the counter-direction by means of an in-phase mechanism of present invention. The in-phase mechanism of present invention comes from a mutual cooperation in the rotational motion between the rotor (5) and the rotary valve (7) resulting the closure of; the outgoing gate and opening of the incoming gate of fluid path (5)..

Since the location of concave groove (6) is calibrated on the- periphery of the rotary valve (7) in accordance with the matching timing so that the vane (4) meets rotary valve (7) in phase by the tooth-coupled operation, the refined mechanism as mentioned above. is greatly utilized for the actual operation of pumping system.

For the detail application, the pulse sensor (1 1 )M installed on the ^; pulse target (12) as shown on Fig. 1 without the driving power source of rotor (3) can measure the numbers of revolution of rotor(3) which is a proportional quantity of the fluid speed inside the chamber such,, that the present invention can be used as a bi-mechanical system.

Those skilled in the art will readily recognizeMthat these and other modifications and changes may be made to the present invention without strictly following the exemplary application illustrated and described herein and without departing from the true spirit and scope of the present invention. Industrial Applicability

As shown on the above-mentioned description . in detail, the present invention under the embodiment of the rotating valves provides many advantages for controlling the fluid flow in the system. The present invention has excellent advantages such as the high mechanical endurance of hardware, the. high efficient compressing or the pumping speed and the enhanced flowing, efficiency since the mechanical structure is nearly perfect against the metallic friction which eventually occurs while in the stroking process. Futhermore the maximum pressure pan be reached immediately at the moment of starting stage of, rotational motion of the rotor. For the case of a motor application under the present embodiment, the_:. ultra speed control system is necessary because the maximum torque is accomplished with the fluid pressure simultaneously.'^' . ' For the another merit of this system in the ' actual industry , application although it may depends on the conventional pressure, the present invention is not necessary for the special heat treatment, procedure below the pressure of 200 Kg/cm. In other words, the general materials including non-metallic component can be applied for machining this kind of system for the conventional use.

The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of: the invention,;^" and all such modifications as would be obvious to one skilled in the art are intended to be included within the scope of the following claims.

Claims

Claims:

1 . A pump having the rotary vanes and valves comprising ; said rotor (3) which is axially installed and is rotatably ' supported in said housing (2), and forms at least two said vanes (4) on the periphery of rotor (3), said two rotary valves (7) having at least one said concave groove (6) on the periphery of rotary valve (7) are axially installed along the longitudinal direction of said flow path (5) formed in the housing (2), said master gear (8) and said slave gear (9). axially fixed on . said rotor (3) and said rotary valve (7) respectively are combined eac other for the tooth-coupled operation.