KR100251084B1 - Spiral pump - Google Patents

Abstract

PURPOSE: A spiral pump is provided to prevent leak and improve pumping efficiency by engaging teeth protruded in a driving spiral disk and a driven spiral disk to flow in and discharge fluid. CONSTITUTION: Each tooth(100) having radius of curvature is bent and protruded in a driving spiral disk(2) and a driven spiral disk(3), and the teeth are engaged with each other. The end and the rear end of each internal part are prevented from being contacted in engaging by forming the outer surface of the tooth into the even surface. The driven spiral disk is inclined, and a pivot(20) is installed to support a driving shaft(5) in an end of an inclined shaft(15) engaged with the driven spiral disk. A corrugated tube prevents fluid and foreign matters from flowing out of the pivot. The spiral pump sucks fluid from an intake port(23), and pressurizes and discharges the fluid with pumping, and prevents leak of the fluid with the curved teeth protruded in the disks.

Description

Spiral Pump

The present invention relates to a spiral pump, and more particularly, to a spiral pump which has a predetermined radius of curvature to each of the driving spiral disk and the driven spiral disk to protrude and engage the fluid to prevent the outflow of the fluid.

In general, a pump converts mechanical energy into fluid energy, and is classified into turbo type and volume type in view of its operation principle.

Representative turbo pumps include centrifugal pumps, and reciprocating pumps and screw pumps, including gear pumps, can be cited as volumetric pumps.

Centrifugal pumps are generally composed of an impeller and a casing. The centrifugal pump rotates the fluid to be pumped at a high speed by the impeller to generate centrifugal force. The centrifugal pump pumps the fluid from the center of the impeller to the outer circumferential side using the pressure change.

Gear pumps are pumps that mesh with each other in two casings and rotate to push fluid from the suction side to the discharge side, and are generally suitable for small-capacity and mainly used for delivering oil such as lubricating oil.

Turbo pumps and volumetric pumps have different characteristics, which are compared with each other as follows.

(1) Characteristics of turbo pump

㉮ It is generally used at high speed rotation, so the volume of the device is smaller than the discharge flow rate.

운전 Even if the valve is operated with the valve closed, the head of the pump does not rise extremely.

저 Generally for low head and large flow rate.

동력 There is less power loss due to internal friction because of the large gap between the moving part and the fixed part.

출 The flow rate, suction head and discharge head can be easily adjusted by adjusting the opening degree of the discharge side and suction side valves.

(2) Characteristics of volumetric pump

효율 Generally high efficiency.

No lake is needed.

고 Generally for high chickenpox and small dose.

㉱ The flow rate is almost constant at any head condition.

As can be seen from the comparison of characteristics, the turbo and volumetric expressions have many contradictions in their characteristics, and in particular, they contain completely contradictory contents.

In other words, the centrifugal pump, which is a turbo type pump, has a representative advantage in that it can deliver a large flow rate, while the head of the pump is small, and the gear pump, which is a volumetric pump, can arbitrarily enlarge the head of the pump to obtain high efficiency, while the structure of the pump There is a disadvantage in that the flow rate cannot be increased.

Therefore, the conventional pump conventionally used has a fatal disadvantage that does not satisfy at least one side in terms of discharge head or discharge flow rate.

In the meantime, the applicant of the present application has proposed the prior patent application No. 94-3493, which combines a centrifugal pump and a gear pump to inhale the centrifugal pump and discharge the gear pump to obtain a high head. It is a spiral pump that can deliver a relatively large flow rate.

The spiral pump is rotatably installed in the casing provided with an inlet and an outlet, an impeller for sucking fluid from the inlet side by the rotation thereof, and one side is interlocked with the impeller. In addition, the fluid discharged from the impeller is provided and a pair of scroll disks are provided to enable the discharge by pushing the fluid outward by providing a compressive force according to the rotation.

The spiral pump sucks fluid by driving an impeller, and flows the sucked fluid between one or two pairs of opposing scroll disk surfaces which are continuously engaged on one side according to rotation to be discharged according to a gear pump method. It is able to send large flow rate while getting high head.

However, this spiral pump has a vertical engagement surface of the scroll disks which are mutually opposed to each other, so that there is a gap between them due to tolerances during mechanical processing or contact friction during operation. There was this.

In other words, pressure is applied as the fluid passes through the inside of the scroll disk that presses the fluid, that is, between the driving scroll disk and the driven scroll disk during operation, and pressurizes the fluid, wherein the gap formed between the engagement surfaces The fluid is released from the pressure changes therein, thereby reducing the pumping efficiency and at the same time the fluid hits the disk has a problem that the noise is generated.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described conventional problems, and an object thereof is a radius of curvature that is formed and engaged in each of a driving spiral disk and a driven spiral disk for introducing a fluid and simultaneously supplying and discharging a fluid. It is to provide a spiral pump that protrudes with the concave-convex contact to prevent the flow of fluid between them, and improve the pumping efficiency.

It is another object of the present invention to provide a spiral pump capable of delivering a large flow rate while obtaining high head.

1 is a longitudinal sectional view of a spiral pump according to the present invention;

Fig. 2 is a longitudinal sectional view showing a drive spherical disk of the spiel pump.

Fig. 3 is a plan sectional view showing the drive spherical disk.

Fig. 4 is a longitudinal sectional view of a driven spherical disk of the spiral pump.

5 is an enlarged cross-sectional view of the main portion of the present invention.

Figure 6 is a cross-sectional view showing the assembled state of the two spiral disks according to the present invention.

Fig. 7 is an enlarged sectional view showing the main parts of another embodiment of a spiral disc of the present invention;

Fig. 8 is an enlarged sectional view showing the principal parts of still another embodiment of a spiral disc of the present invention;

Fig. 9 is an assembled sectional view of a installed spiral pump of a plurality of spiral discs.

Fig. 10 is a sectional view of a state in which both spiral discs are connected by universal joints.

Fig. 11 is a sectional view of a state in which both spiral disks are connected by a constant velocity joint.

* Explanation of symbols for main parts of the drawings

1: Casing 2: Driven Spiral Disk

3: passive spiral disk 4: shaft hole

5: drive shaft 6: key

12: groove 15: inclined shaft

20: pivot 23: inlet

24 discharge port 30 fluid compression chamber

40: universal joint 50: constant velocity joint

51: steel ball 52,53: connection groove

100: tooth 102: support housing

The object of the present invention is a casing having a suction port and a discharge port, and a driving and driven spherical disk mounted in the casing to provide fluid and at the same time provide a compressive force so that a tooth is formed on the opposite side so as to be discharged. And a drive shaft for rotating the drive spherical disk by transmitting power of a power generating means, and the inclined joint of the driven spherical disk with the drive spherical disk such that the opposite side is gradually separated from one side with a predetermined inclination. In the axial pump provided with a shaft, teeth formed on each of the driven and driven spiral disks are projected to have a predetermined radius of curvature so as to be engaged in an uneven form. The fluid flows outward from the compression chamber formed between the disks. To prevent the phenomenon that output will have a feature that can improve the pumping efficiency.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings. Figure 1 shows a longitudinal cross-sectional view of a spherical pump in accordance with the present invention, the present invention is provided with a casing (1) having a suction port 23 and the discharge port 24, and is mounted in the casing (1) to flow fluid It is composed of a spiral disc (2) (3) which is discharged by applying pressure at the same time.

The spiral discs 2 and 3 are connected to a means for generating power such as a motor or an engine, and are driven on a drive shaft 5 arranged on a drive shaft 5 for transmitting rotational force. It consists of a passive spiral disk (3) interlocking with 2).

The driving spiral disk 2 has a shaft hole 4 formed in the center thereof as shown in FIG. 2 so that the driving shaft 5 is connected by a connecting means such as a key 6, and the outer periphery of the shaft hole 4. There is a fastening part 7.

The fastening portion 7 serves to draw the fluid toward the compression action surface 9 when the drive spherical disk 2 is assembled and rotated in the casing 1 and to exert the fluid in a radial direction by applying centrifugal force to the fluid. .

One side surface of the drive spherical disk 2 is formed with a spiral tooth surface extending from the outer side to the outer circumference of the opening portion for introducing fluid into the center portion, that is, the compression action surface 9 side. .

The spiral tooth surface is formed at least 360 ° from the central portion so as to apply a strong centrifugal force to the fluid as shown in FIG.

In addition, the spiral tooth type is composed of a tooth (100) protruding on one side of the disk (2) (3) and the groove 12 formed thereby, the contact surface when the driven spiral disk (3) to be described later is engaged It protrudes curvedly with a predetermined radius of curvature so that a clearance is removed in between.

On the other hand, the contact surface is the same as the compression action surface 9 which exerts a centrifugal force on the fluid.

4 and 5 show the structure of the driven spherical disk 3 which is engaged with the drive spherical disk 2 and rotates, which corresponds to the teeth formed on the drive spherical disk 2. Teeth 100 to be engaged with each other, and a hole 16 is formed in the center thereof.

The through hole 16 is provided with an inwardly projecting flange 17 connected to the inclined shaft 15 having a predetermined inclination angle α and is coupled to the outer surface of the inclined shaft 15.

In addition, the driven spherical disk 3 coupled to the inclined shaft 15 has a predetermined inclination angle, so that when one side is engaged with the drive spherical disk 2 as shown in FIG. 6, the teeth 100 are recessed 12. It is completely inserted into and coupled, the opposite side is gradually expanded by the inclination angle is formed between the compression chamber 30 therebetween.

And a pivot 20 for supporting the drive shaft 5 is installed at the tip of the inclined shaft 15, the pivot 20 is formed in a ball shape to enable a smooth rotation with each other and at the same time the inclined shaft 15 and the drive shaft 5 are positioned.

On the other hand, the support housing 102 for supporting the drive shaft 5 has a support surface 21 for rotatably supporting the drive spiral disk 2 and a bearing 22 for supporting the drive shaft 5, the casing (1) is made by coupling the cover part 1 "to the main casing 1 'including the suction port 23 and the discharge port 24 so as to support and conceal one end of the inclined shaft 15.

The suction port 23 guides the fluid to be transferred from the outside to the fastening portion 17 of the drive spherical disk 2.

The lid portion 1 ″ is provided such that the inclined shaft 15 of the driven spiral disk 3 is kept inclined at a predetermined angle α with respect to the drive shaft 5 of the driven spiral disk 2. Configuration.

In addition, the outer side of the pivot 20 of the inclined shaft 15, which is provided in the support housing 102 to support the end of the drive shaft 5, the corrugated pipe 150 to prevent the inflow of dust and foreign matter, including the fluid is It is installed.

The cover part 1 "has a bore 27 for receiving one end of the inclined shaft 15 of the driven spiral disk 3, and the inner diameter of the bore 27 covers the shaft 15 in sliding contact. The bearing is configured to accommodate the sliding bearings 28 at regular intervals.

Reference numeral 26 in the drawing denotes a fluid chamber.

Referring to the assembling process of the present invention having such a configuration, first, the drive spherical disk 2 is disposed on the support surface 21 of the main casing 1 ′, and the drive shaft 5 is connected to the bearing 22. Insert the shaft shaft 4 and the assembly of the inclined shaft 15 and the driven spherical disk (3) is placed on the drive spherical disk (2) so that the tooth 100 is fitted into the groove (12).

The distance between a pair of spiral disks (2) (3), that is, the driving spiral disk (2) and the driven spiral disk (3), is determined by the fluid chamber (when the disk 3 is coupled to the disk 2 in an inclined state. 26, and the groove 12 is determined so as not to disengage, this distance is maintained by the axes 20 and 15 of the discs 2 and 3.

The cover part 1 "has a bore 27 for receiving one end of the inclined shaft 15 of the driven spherical disk 3, and the inner diameter of the bore 27 covers the shaft 15 in sliding contact. The support is enough to accommodate the sliding bearings 28 at regular intervals.

The upper side of the sliding bearing 28 is embedded with a sealing material and the inclined shaft 15 in the sliding bearing 28 is embedded in the main casing 1 ′ while forming the crossing angle α with the driving shaft 5.

During operation of the spiral pump, the inclined shaft 15 receives a force to return to a position parallel to the drive shaft 5 by centrifugal force by the rotation of the driven spherical disk 3, so that the inclined shaft 15 is a sliding bearing 28. It is supported by and firmly coupled to maintain the inclined posture without shaking.

The inclined coupling between the spiral disks (2) and (3) is one of the couplings between the grooves of the two disks (2) and (3), for example, located at the left side as shown in FIG. A variable volume fluid compression chamber 30 is formed between the (12).

In this way, the volume of the fluid compression chamber 30 is the maximum when the coupling degree is the smallest.

While the disks 2 and 3 rotate together to move the groove 12 engagement portion on the left side to the right in the drawing, their engagement becomes deeper and circumferentially 180 from the point where the volume of the fluid compression chamber 30 is maximum. At the point of movement, the size of the fluid compression chamber 30 eventually becomes 0 and discharges the fluid.

That is, the coupling degree of the groove 12 of the inclined side of the driven spiral disk 3 is the deepest and the size of the fluid compression chamber 30 is small.

In this way all teeth 100 and recesses 12 of the discs 2 and 3 can compress the fluid to one side with varying degrees of engagement.

The discharge port 24 is located at the point where the coupling degree is greatest.

Determining the maximum volume of the fluid compression chamber 30 is the inclination of the disk 3, that is, the inclination of the inclination shaft 15.

As described above, the spiral pump of the present invention which rotates the disks 2 and 3 at high speed by the rotational force transmitted from the drive shaft 5 and introduces the fluid, and discharges the fluid by applying a centrifugal force to each disk 2 ( The teeth 100 formed in 3) are engaged with each other in a protruding state with a predetermined radius of curvature, thereby preventing a fluid from flowing out between them.

In other words, when the curved teeth 100 are engaged, this becomes a concave-convex type, and the gap between them is naturally removed, so that the fluid flows outward from the compression chamber 30 that is engaged in the inclined posture and formed therein. The phenomenon can be prevented and the pressure inside can be maintained.

Fig. 7 shows another embodiment of such a spherical disc of the present invention, wherein the spherical disc 2 and 3 are formed on the driving spherical disc 2 and the driven spherical disc 3 (100). ) Is configured to have a predetermined inclination angle and formed into a substantially "[" shape so that it can also prevent the outflow of fluid that is present in the compression chamber 30 during operation.

8 shows another embodiment of the spiral disk of the present invention, in which teeth 110 formed on each of the spiral disks 2 and 3 are contacted at both ends thereof to reduce friction noise.

As shown in the figure, the outer surface of the tooth 100 protruding from the center portion to the outer circumference is cut by a smooth surface, and when these mutual teeth are joined, the respective inner surfaces of the teeth 100 correspond to the outer surface of the corresponding tooth 100. By contacting only the front end and the rear end, the inner side is engaged in the hollow (110a) can reduce the friction generated during operation.

9 shows a plurality of pairs of the spherical discs 2 and 3 of the present invention installed to improve pumping efficiency. First, the first drive spherical disc 2a mounted in the casing 1 and the first The second driven spiral disk 3b and the second drive, which are symmetrically located on the first driven spiral disk 3a and the first driven spiral disk 3a, which are engaged with and interlocked with the driving spiral disk 2a. It consists of a spiral disc 2b.

Here, the first drive spiral disk 2a is connected to the drive shaft 5a for transmitting power from the power generating means, and the first driven spiral disk 3a is assembled to the inclined shaft 15a to have a predetermined inclination angle. It is engaged with the first drive spherical disk 2a with a drawing.

In addition, the second driven spiral disk 3b has its teeth positioned symmetrically with the teeth of the first driven spiral disk 3a, and its tilted shaft 15a is fitted to the outer circumference of the tilted shaft 15a. It is the structure connected by the guide plate 15b which protruded to the outer side surface of ().

On the other hand, the second driven spiral disk 2b is meshed with the second driven spiral disk 3b.

10 and 11 show an example of connecting the two passive spiral disks 3a and 3b, and FIG. 10 shows a first driven spiral disk 3a and a second driven spiral disk 3b + type. It is connected to the universal joint 40 of Figure 11 is connected to both driven spiral disks (3a) (3b) with a constant velocity joint (50) consisting of a steel ball 51 and the connecting groove (52) (53). .

In the spiral pump having such a configuration, as the driving shaft 5a is rotated, both driving spiral disks 2a and 2b are rotated, so that both driven spiral disks 3a and 3b are rotated, thereby pumping efficiency. Can be increased.

As described above, the spiral pump of the present invention is capable of sending a large flow rate while obtaining a high head by injecting a pressure from the suction port, applying a pressure, and then discharging it by a gear pump method, and teeth protruding on each disk in a curved shape. If the mesh is made of irregularities to prevent the outflow of the fluid being pumped inside, it is possible to increase the pumping efficiency.

Claims (4)

A casing provided with a suction port and a discharge port, and a driven and driven spherical disc which is mounted in the casing to allow fluid to flow in and at the same time to provide a compressive force so that a discharge is formed on the opposite side so as to be discharged. A spigot pump is provided with a drive shaft for transmitting and rotating the power of the power generating means to the disk, and an inclined shaft for engaging the drive spherical disk so that the opposite side is gradually spaced from one side with the driven spiral disk at a predetermined inclination. The spherical pump according to claim 1, wherein teeth formed on each of the driving spherical disk and the driven spherical disk are bent to protrude with a predetermined radius of curvature so as to be engaged with each other in an uneven form. The method according to claim 1, characterized in that the outer surface of the protruding teeth having a radius of curvature formed in each of the drive and the driven spiral disk as a smooth surface so that only the front and rear ends of each inner surface are in line contact when engaged. Spiral pump. The corrugated pipe according to claim 1, which is provided at a tip of an inclined shaft which maintains the driven spiral disk at a predetermined inclination angle and is engaged with the driving spiral disk, and is provided in a corrugated pipe to prevent the inflow of fluid and various foreign substances outside the pivot supporting the driving shaft. Spiral pump, characterized in that. The spherical drive according to claim 1, wherein the first driven spherical disk and the first driven spherical disk which are symmetrically located in the casing are interlocked with the first driven spherical disk. An ear disk and a second drive spherical disk are installed, but the spherical pump is characterized in that the joint pressure on the spherical disk is reduced by connecting both driven spherical disks with universal joints or constant velocity joints.

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