KR20020043765A - High pressure valume type pump - Google Patents

Abstract

PURPOSE: A high pressure volume type pump is provided to expand change of volume while preventing blocking by solids and sludge. CONSTITUTION: A driving shaft(10a) of a motor(10) and one end of a rotary axis(20) is coupled and fixed to a coupling(1). A first rotary body(30) with an inner gear part(30a) formed on an inner circumference thereof, is formed integrally with the other end of the rotary axis. The first rotary body is placed on a placing part of a multi-stepped placing part of a gear frame(40) joined with the motor by a saddle(2). A pump casing has a bypass pipe, passing fixed fluid, formed to smooth flow of fluid taken in and discharged through an inlet(50a) and an outlet(50b) and optimum periphery composed of two of doubled circles and is closely joined to the gear frame with a coupling device. A second rotary body(60) has a diameter smaller than the first rotary body and a circumscribed gear part(60a) on a periphery thereof to eccentrically rotate by the inner gear part of the first rotary body as the first rotary body rotates and is joined to the first rotary body. A triangular rotor(80) is joined to the other side of the second rotary body to eccentrically rotate by an inner circumferential surface of the pump casing to take in and discharge fluid through the inlet and outlet by rotary force of angular surfaces of the triangle. A pump cover(90) seals the pump casing together with the gear frame.

Description

High pressure valume type pump

The present invention relates to a volumetric pump applied to wastewater treatment of wastewater and sewage containing a high viscosity solids or sludge or for the spraying of pesticides and boilers in the industrial field, and in particular, the volume change through the improvement of the structure of the pump The present invention relates to a high-pressure volumetric pump that enables pumping of high power while eliminating pulsation as well as clogging caused by foreign matter, solids, and sludge.

In general, volumetric pumps are used for industrial applications for the transfer of solids with high viscosity, for drainage in rural areas, for treatment of wastewater and sewage containing various sludges, for spraying orchard pesticides, and for rapid drainage of boilers. As used above, most of the volumetric pumps used for industrial or general purpose have a structure that enables the pumping from the operation of gears, vanes, screws and the like.

However, in the case of the pump pumped from the volumetric pump as described above, wear of the rotor formed therein occurs when the pump is used for a long time or the pumping pressure is increased because the discharge pressure is limited. At the same time, the pumping efficiency of the pump is greatly reduced.

In addition, the pump as described above is clogged discharge or suction port from the sludge or foreign substances contained in the water according to the period of use, which is difficult to manage the inconvenience, especially the industry that transfers high viscosity solids When applied to the field has a disadvantage that the pumping force is greatly reduced while the outlet or inlet of the pump is blocked by the solid material.

In addition, since the conventional pump has a considerable weight and a complicated structure, the pulsation rate is not only increased from the pumping operation of the pump, but also has a considerable difficulty in repair as well as movement.

Thus, although the conventional pump does not provide a pump capable of high pressure pumping, the above-mentioned piston type pump also has a disadvantage of causing severe noise while showing a high pulsation rate from the pumping operation of the pump in which the piston reciprocates linearly. There is this.

Accordingly, the present invention has been made to solve the conventional problems as described above, the object of the present invention, by configuring a pump of a simple structure including a casing and a rotor optimally designed through an epicycloid curve, Prevents clogging caused by foreign substances, solids and sludges while increasing the volume change, and also makes the pump compact and easy to manufacture, while simplifying the structure and enabling powerful suction / discharge without pulsation through high power pumping operation. On the other hand, it is to provide a high pressure displacement pump to facilitate the repair.

In other words, the present invention is a pump using the principle of the Wankel engine applied to the vehicle in reverse, by designing the casing and the rotor of the pump under the optimum epicycle load curve under optimum conditions, the pump of high pressure and high power Is to provide.

In addition, the present invention is designed in the direction of the inlet and outlet of the pump in a single direction formed side by side in the same area or in both directions in which the inlet and outlet are formed side by side respectively, so that the suction and discharge from the pumping operation of the pump It is intended to make the pumping of the fluid containing sludge and foreign substances as well as the solids made more efficient.

1 is an exploded perspective view showing a structure of a high pressure displacement pump in one embodiment of the present invention.

Figure 2 is a cross-sectional view showing a structure of a high pressure displacement pump in one embodiment of the present invention.

Figure 3a is a rotor initial state in the pump casing in one embodiment of the present invention.

Figure 3b is a positional view of the first rotary body internal gear portion and the second rotary body external gear portion according to the initial state of the rotor in an embodiment of the present invention.

Figure 4a is a state in which the rotor rotates 90 ° in the pump casing in one embodiment of the present invention.

Figure 4b is a positional view of the first rotary internal gear and the second rotary external gear according to the embodiment of the present invention according to the rotation of the 90 °.

Figure 5a is a 180 ° rotational state diagram of the rotor in the pump casing in one embodiment of the present invention.

Figure 5b is a positional view of the first rotary body internal gear portion and the second rotary body external gear portion in accordance with an embodiment of the present invention by 180 ° rotation of the rotor.

Figure 6a is a 270 ° rotational state of the rotor in the pump casing in one embodiment of the present invention.

Figure 6b is a positional view of the first rotary body internal gear portion and the second rotary body external gear portion according to the rotation of the rotor 270 ° in one embodiment of the present invention.

7 is a cross-sectional view of another embodiment of the present invention to which a reduction gear is applied to a high pressure displacement pump.

Figure 8 is another embodiment of the present invention in which the inlet and outlet of the pump casing is set in both directions.

Figure 9 is another embodiment of the present invention in which the inlet and outlet of the pump casing is set to double.

* Explanation of symbols on the main parts of the drawings *

One ; Coupling 1a; Insert groove

2 ; Saddle 3; bearing

4 ; Sealing part 10; motor

10a; Drive shaft 20; Axis of rotation

30; First rotating body 30a; Internal gear

30b; Rotary pin 40; Gear frame

50; Pump casings 50a, 50a '; Inlet

50b, 50b '; Discharge port 50c; Bypass tube

Q; Circumferential surface 60; Second rotating body

60a; External gear portion 70; Rotary pin

80; Rotor 80a; Tension hole

90; Pump cover 100a; 1st reduction gear

100b; Second reduction gear d1, d2, d3; Triangle

200; Internal wall surface 200a; Suction hole

200b; Discharge holes L and M; Communication

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

1 is an exploded perspective view showing a high pressure displacement pump structure as an embodiment of the present invention, Figure 2 is a cross-sectional view showing a high pressure displacement pump structure as an embodiment of the present invention.

3A is a diagram illustrating an initial state of a rotor in a pump casing according to an embodiment of the present invention, and FIG. 3B is a diagram illustrating a first rotating body internal gear unit and a second rotating body external gear according to an initial state of a rotor according to an embodiment of the present invention. It is also the location of the fisherman.

4A is a view illustrating a state in which a rotor is rotated by 90 ° in a pump casing according to one embodiment of the present invention, and FIG. 4B is a diagram of a second internal rotation gear unit and a second rotating body that rotates by 90 ° in an embodiment of the present invention. The position of the entire external gear is also shown.

Figure 5a is a 180 ° rotation state diagram of the rotor in the pump casing in one embodiment of the present invention, Figure 5b is a first rotational internal gear portion and the second rotation of the rotor according to the 180 ° rotation of the rotor in one embodiment of the present invention The position of the entire external gear is also shown.

Figure 6a is a 270 ° rotational state diagram of the rotor in the pump casing in one embodiment of the present invention, Figure 6b is a first rotary body internal gear portion and the second rotation according to the 270 ° rotation of the rotor in one embodiment of the present invention The position of the entire external gear is also shown.

As shown in Figs. 1 to 6, in the pump where the pumping is performed from the rotation of the motor 10 having the drive shaft 10a,

In addition to the drive shaft (10a) of the motor 10 to one side end of the rotary shaft 20 to the coupling (1),

On the other end of the rotating shaft 20 has an internal gear portion (30a) to the inner circumferential surface and the first rotating body 30 of a predetermined diameter to protrude the rotating fixing pin (30b) integrally formed at the center thereof,

The first rotating body 30 is seated on one of the seating portion (not shown in the figure) of the multi-stage mounting portion of the gear frame 40 coupled to the motor 10 through the saddle (saddle) 2,

The gear frame 30 is connected to the pump casing 50 having an optimum circumferential surface Q from a double overlapping circle while forming an inlet 50a and an outlet 50b. Tightly bond)

The first rotational body 30 has an external gear portion 60a on its outer surface such that an eccentric rotation is made along the internal gear portion 30a of the inner side while the first rotational body 30 is designed to have a small diameter. To combine the second rotating body 60,

In the center of one side of the second rotating body 60, the rotation fixing pin so that the external gear portion 60a of the second rotating body 60 is not separated from the internal gear portion 30a of the first rotating body 30. Fastening the rotary shaft pin 70 through its bearing 3 along its outer circumferential surface 30b,

On the other side of the second rotating body 60 while the eccentric rotation along the inner circumferential surface (Q) of the pump casing 50 through the rotational force of each triangular top (d1) (d2) (d3) inlet (50a) And a triangular rotor 80 for sucking or discharging the fluid through the discharge port 50b,

The inside of the pump casing 60 to which the rotor 80 is coupled is characterized by being sealed with a pump cover 90 together with the gear frame 40.

According to another aspect, the pump casing (50) is a "U" bypass tube for passing a predetermined fluid so that the flow of the fluid intake and discharge from the eccentric rotation of the rotor 80 can be easily made without resistance Form 50c,

The suction port 50a and the discharge port 50b of the pump casing 50 are formed side by side in the same area so that the suction and discharge of the fluid from the eccentric rotation of the rotor 80 can be maintained at a high pressure.

According to another aspect, the rotor 80 is abrasion-resistant and the flow of the fluid is easily made without resistance while preventing the compression of the fluid by minimizing the friction force generated when the inner surface of the pump casing 50 and the contact It is preferable to mold with a special rubber material having excellent heat resistance,

In each triangular top (d1) (d2) (d3) of the rotor 80, the triangular tops (d1) (d2) (d3) are inside the pump casing (50) during the eccentric rotation of the rotor (80). Each of the holes 80a exerting tension were machined to keep the rotor 80 in close contact with the circumferential surface Q, thereby preventing breakage.

When each of the triangular tops d1, d2, and d3 rotates, the inlet 50a is vacuumed in the pump casing 50 while maintaining intimate contact with the inner circumferential surface Q of the pump casing 50. The fluid is sucked through the pump casing 50, and the fluid sucked into the pump casing 50 is discharged to the discharge port 50b by the rotational force of the respective triangular tops d1, d2, and d3 of the rotor 80. It has a structure made of this.

Here, the gear frame 40 is formed of a plurality of seating parts not shown in the drawing bar,

Each seating portion has a bearing (3) to facilitate rotational rotation of the rotating shaft (20), and fluid in the pump casing (50) sealed from the pump cover (90) and the gear frame (40). It is preferable to fasten the sealing portion 4 so as not to flow into).

Referring to Figures 1 to 6 attached to the operation of an embodiment of the present invention configured as described above are as follows.

First, the drive shaft 10a of the motor 10 is fastened to one side of the coupling 1, and then the gear frame 40 having multiple seats at the center of the motor 10 is coupled to the saddle 2. .

Subsequently, the sealing unit 4 and the bearing 3 are seated on each seating portion formed from the inside of the gear frame 40, and then integrated with the first rotating body 30 through the gear frame 40. The fixed shaft 20 is inserted into the coupling 1 to be fixed.

Then, the first rotating body 30 is mounted on another seating portion formed in the gear frame 40, so that the rotating shaft 20 and the first rotating body 30 is the motor 10 When the drive of the drive shaft 10a and the coupling (1) and the rotary drive.

Then, the pump casing 50 having an optimal circumferential surface Q from a double overlapping circle on one side of the gear frame 40 is fastened by fastening means (for example, bolts or hexagon bolts).

Thereafter, the second rotating body 60 is fastened and fixed to one side of the rotor 80 by the first rotating body 30 seated on the seating portion of the gear frame 40.

Then, the rotary shaft pin 70 is fastened to one side of the second rotating body 60 through the bearing 3 to the outer circumferential surface of the rotating fixing pin 30b protruding on the center of the first rotating body 30. It is in close contact, the internal gear portion 30a formed on the inner circumferential surface of the first rotating body 30 in accordance with the close contact between the rotating shaft pin 70 and the rotating fixing pin (30b) to the outer surface of the second rotating body (60) The formed external gear portion 60a engages at predetermined intervals to perform eccentric rotation thereof.

Thereafter, when one side of the pump casing 50 into which the rotor 80 is inserted is sealed as the pump cover 90, both sides of the pump casing 50 are from the pump cover 90 and the gear frame 40. It has a structure that is tightly sealed, it is possible to intake and discharge the fluid.

Therefore, the motor 10 of the high-pressure rotary pump assembled as described above is applied to industrial or rural drainage or wastewater and sewage wastewater treatment facilities containing various sludges, orchards for spraying pesticides or for rapid drainage of boilers. In this case, the driving shaft 10a and the rotating shaft 20 connected from the coupling 1 may be interlocked from the driving of the motor 10.

Here, the outside of the second rotating body 60 fastened to one side of the rotor 80 having a triangular shape to the internal gear portion 30a of the first rotating body 30 formed at the other end of the rotating shaft 20 The folding fish (60a) is always engaged by a predetermined distance without a gap from the close contact between the rotation fixing pin (30b) and the rotating shaft pin (60a),

When the first rotary body 30 rotates as the rotary shaft 20 rotates, the external gear unit 60a meshes with the internal gear unit 30a of the first rotary body 30 by a predetermined distance. 2 rotor 60 and the rotor 80 is coupled to the second rotor 60 is the eccentric rotation in the pump casing 50 in the order of Fig. 3 → Fig. 4 → Fig. 5 → Fig. do.

At this time, when the rotor 80 makes the eccentric rotation, each triangular top (d1) (d2) (d2) maintains a close contact state along the inner circumferential surface (Q) of the pump casing 50,

From the rotation of each of the triangular top (d1) (d2) (d3) through the internal vacuum state (Fig. 3 and 4) of the pump casing 50 to suck the fluid at the inlet port (50a), the pump casing Fluid sucked into the interior of the 50 is guided to the discharge port (50b) from each of the triangular top (d1) (d2) (d3) of the rotor 80 is a continuous rotation (Figs. 5 and 6) again The discharge is made.

That is, when each triangular top (d1) (d2) (d3) of the rotor 80 rotates while maintaining in close contact with the inner circumferential surface (Q) of the pump casing 50, the rotation initial state In FIG. 3 and FIG. 4, the inside of the pump casing 50 is maintained in a vacuum state, thereby allowing the suction of fluid through the inlet port 50a.

The fluid sucked into the pump casing 50 through the suction port 50a is again in accordance with the rotational force of the respective triangular tops d1, d2, and d3 as shown in FIGS. 3 to 6. The discharge is made through the discharge port 50b which is formed in the same area as 50a).

Here, the pump casing 50 is formed with a bypass tube (50c) having a "U" shape,

The bypass pipe 60a separately passes a predetermined amount of fluid guided from the triangular tops d1, d2, and d3 of the rotor 80 to the discharge port 50b, thereby allowing the rotor 80 to be passed through. The flow of the fluid was more easily achieved without resistance while preventing the compression of the fluid due to the rotational force of the respective triangular tops d1, d2, and d3.

In addition, the rotor 80 is molded of a special rubber material having excellent wear resistance and heat resistance to minimize frictional forces generated in contact with the inner circumferential surface of the pump casing 60, the triangular top (d1) (d2) (d3) ), The tension hole 80a was processed.

The eccentric rotation of the rotor 80 due to the tension holes 80a causes the triangular tops d1, d2, and d3 to keep in close contact with the inner circumferential surface Q of the pump casing 50, respectively. It will be made easier while preventing damage.

On the other hand, Figure 7 is another embodiment of the present invention in which the reduction gear is applied to the high pressure rotary pump, which shows a diagram to prevent the overload of the high pressure displacement pump by installing the reduction gear in the high pressure displacement pump.

That is, by connecting the first and second reduction gears (100a, 100b) of a 2: 1 ratio to the end of the rotation shaft 20 and the drive shaft (10a) of the motor 10, respectively,

When the drive shaft 10a of the motor 10 rotates, the rotation shaft 20 is in accordance with the reduction speed (for example, 1/2) transmitted from the first and second reduction gears 100a and 100b. While rotating, the second rotary body 60 and the rotor 80, in which the external gear portion 60a is engaged with the internal gear portion 30a of the first rotating body 30 by a predetermined distance, are eccentrically rotated at a predetermined deceleration speed. The suction and discharge of the fluid were possible.

Here, one side end of the rotating shaft 20 is fastened to the insertion groove (1a) formed in the inner side of the coupling 1 after the bearing 3 is fastened to the first reduction gear (100a) on the shaft To form.

Meanwhile, FIG. 8 illustrates another embodiment of the present invention in which the inlet and the outlet are set in both directions in a state where the bypass pipe 50c of the pump casing 50 is removed.

That is, when the rotor 80 rotates eccentrically, the fluid sucked through the suction port 50a formed on one side of the pump casing 50 is further discharge port 50b 'formed on the other side of the pump casing 50. Through the discharge)

The fluid sucked through another suction port 50a 'formed on the other side of the pump casing 50 is discharged through the discharge port 50b formed on one side of the pump casing 50.

In other words, in another embodiment of FIG. 8, as in the embodiment of the present invention, when the rotor 80 makes an eccentric rotation by 360 °, the suction and discharge of the fluid are not performed in the same region.

When the rotor 80 rotates by 180 °, it is shown that the discharge and suction of the fluid are simultaneously performed in both regions.

9 shows another embodiment of the present invention in which the inside of the pump casing 50 is removed while the bypass pipe 50c is removed.

That is, the inner casing wall surface 200 having an optimal circumferential surface Q is formed from a circle overlapping the pump casing 50 twice, and the rotor 80 can be eccentrically rotated inside the inner wall 200. It is formed so as to make a passage (L) (M) in communication with the inlet (50a) and the discharge port (50b) on the outside of the inner wall 200,

The inlet wall surface 200 is formed at predetermined intervals and the fluid flows into the inlet wall surface 200 through the passage L communicating with the inlet 50a and then passes through the outlet port 50b (M). A plurality of suction holes 200a and one (or a plurality of) discharge holes 200b are formed to enable log discharge.

That is, when the rotor 80 makes the eccentric rotation, the fluid sucked into the communication passage L through the suction port 50a formed on one side of the pump casing 50 is the inner wall 200 of the pump casing 50. Inflow into the inner wall 200 through the suction hole (200a) formed in the),

The fluid introduced into the inner wall 200 is connected to the communication passage M which is connected to the discharge port 50b through the discharge hole 200b formed in the inner wall 200 according to the eccentric rotation of the rotor 80 again. Through the discharge port 50b is shown an embodiment in which the discharge is made.

As described above, the present invention configures a pump having a simple structure including a casing and a rotor optimally designed through an epicycle rod curve, thereby preventing clogging due to foreign substances, solids, and sludge, while increasing the volume. In addition, while simplifying the structure, the high pressure and high output pumping operation enables powerful suction / discharge, while also making the design of a small pump easier and providing the effect of easy repair.

The present invention is not limited to the above-described specific preferred embodiments, and various modifications can be made by any person having ordinary skill in the art without departing from the gist of the present invention claimed in the claims. Of course, such changes will fall within the scope of the claims.

Claims (4)

In a pump in which pumping is performed from rotation of a motor having a drive shaft, One side end of the rotary shaft is fastened to the coupling together with the drive shaft of the motor, On the other end of the rotary shaft is formed integrally with the first rotating body having a predetermined diameter having an internal gear on the inner peripheral surface, The first rotating body seats one seating portion of the multistage seating portion of the gearframe coupled with the motor via a saddle, The pump casing having an optimum circumferential surface from a double overlapping circle and forming a bypass tube for passing a predetermined fluid so that the flow of the suction and discharge fluid through the suction port and the discharge port is easily achieved without resistance. To the gear frame in close contact with the fastening means, The first rotating body is designed to have a small diameter, and combines a second rotating body having an external gear part with an external surface such that an eccentric rotation is performed along the internal gear part of the inside when the first rotating body is rotated. The other side of the second rotating body is coupled to the triangular rotor for sucking or discharging fluid to the inlet and outlet through the rotational force of each triangular top while eccentric rotation along the inner circumferential surface of the pump casing, The inside of the pump casing coupled to the rotor is a high-pressure displacement pump, characterized in that sealed with a pump cover with a gear frame. The center of the first rotating body is projected in the center of the first rotating body so that the external gear portion of the second rotating body is not separated from the internal gear of the first rotating body, the center of the second rotating body The high-pressure volumetric pump, characterized in that the surface is configured to fasten the rotating shaft pin through the bearing itself is made along the outer circumferential surface of the fixing pin. According to claim 1, Each triangular top of the rotor, High-pressure volume characterized by forming tension holes for tension acting to prevent damage to the rotor while maintaining intimate contact between the triangular top and the circumferential inner surface of the pump casing when foreign substances are introduced from the eccentric rotation of the rotor. Type pump. The method of claim 1, wherein the pump casing, Forming an inner wall having an optimal circumferential surface from a double overlapping circle, passing through a plurality of suction holes and discharge holes in the inner wall, and forming a rotor in an inner side of the inner wall so as to allow eccentric rotation; And a suction passage and a discharge passage communicating with the suction and suction holes, the discharge and discharge holes, respectively to the outside of the internal wall to guide the flow of the fluid into or out of the internal wall.