KR0183366B1 - Spairal pump - Google Patents

Abstract

The present invention relates to a spiral pump combining the principle of a centrifugal pump and a gear pump, and an object of the present invention is to provide a high efficiency spiral pump capable of delivering a large flow rate while obtaining a high head. 23 and a casing 1 having a discharge port 24, and an impeller 7 for rotatably installed inside the casing 1, for sucking fluid from the suction port 23 side by the rotation thereof; A pair of scroll disks, one side interlocked with each other and interlocked with the impeller 7 to inject the fluid discharged from the impeller 7, and then provide a compressive force according to rotation to push the fluid outward to enable ejection. It is characterized by comprising a 2,3).

Description

Spike pump

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

Figure 2 is a cross-sectional view showing a drive scroll disk of the spiral pump according to the present invention.

FIG. 3 is a perspective view showing the spiral tooth shape of the driving and driven scroll disk shown in FIG.

4 is a longitudinal sectional view showing a dual scroll oblique compression element according to a second embodiment of a spiel pump of the present invention.

* Explanation of symbols for main parts of the drawings

1: casing 1 ': main casing

1 cover 2 drive scroll disk

3: driven scroll disk 4: shaft hole

5: drive shaft 6: key

7: impeller part 8: impeller wing

9: compressive action surface 10: first opening part

11: second opening 12: groove

13,14: this 15: inclined axis

16 hole 17 inwardly projecting flange

18,18 ': Bolt 19: outwardly facing flange

20: pivot 21: support surface

22: shaft hole 23: suction port

24: discharge port 24 ': fluid transfer path

25,25 ': Bolt 26: Fluid chamber

27: Bore 28: Bushing

29: angle adjustment member 30: compression chamber

102,102 ': Driven scroll disk 102: Driven scroll disk

104: opening 105: drive shaft

106: height 107,107 ': impeller portion

130,130 ': Compression chamber 131,131': Ejection point

α: crossing angle

The present invention relates to a spiral pump. The present invention particularly relates to a combination of a centrifugal pump and a gear pump. The suction pump is a centrifugal pump method and the discharge pump is a gear pump method, and relates to a spiral pump capable of relatively high flow rate while obtaining a high head.

Pumps are broadly classified as turbo and volumetric in terms of their principle of operation as converting mechanical energy into energy of a fluid.

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

A centrifugal pump is 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, and transfers the fluid from the center of the impeller to the outer circumference by using the pressure change caused by the centrifugal force. .

The gear pump is a pump in which two gears mesh with each other in a casing and rotate to push the fluid from the suction side to the discharge side. In general, it is suitable for small-capacity ones and is 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 water and large capacity.

㉱ Power loss due to internal friction is small due to 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 discharge and suction valves.

(2) Characteristics of displacement pumps

효율 Generally high efficiency.

No lake is needed.

고 Generally used for high head and small amount.

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

As can be seen from the above characteristics comparison, the turbo and volumetric expressions have many opposites in their characteristics, and in particular, they contain completely opposite contents. In other words, the centrifugal pump, which is a turbo 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 its structure is discharged. There is a point that the flow rate cannot be increased. According to the above, the conventional pumps that have been put to practical use have had a fatal disadvantage of not satisfying at least one side in terms of discharge head or discharge flow rate, and it has been a very difficult problem to solve this problem.

The spiral pump according to the present invention solves the above-mentioned difficulties and is equipped with the typical advantages of the two types of pumps.

It is therefore an object of the present invention to provide a high efficiency spir pump capable of delivering a large flow rate while obtaining a high head.

The object of the present invention is a casing having an inlet and an outlet, rotatably installed inside the casing, and an impeller for sucking fluid from the inlet side by rotation thereof, and one side meshing with the impeller. By providing a spiral pump that is interlocked, having a pair of scrolls to enable the discharge by injecting the fluid discharged from the impeller and then providing a compression force in accordance with the rotation to push the fluid outward Is achieved.

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

1 is a longitudinal cross-sectional view of a spiral pump according to the present invention, which is a casing 1, a pair of drive scroll disks 2 and driven scroll disks 3 installed inside the casing 1; Consists of

A shaft hole 4 penetrates through the center of the drive scroll disk 2, and a drive shaft 5 connected to a prime mover such as a motor or an engine is coupled by a key 6 or the like. At the outer periphery of the shaft hole 4 there is an impeller portion 7. The impeller portion 7 is formed by forming a plurality of passages (8 in this embodiment) extending axially through the drive scroll disk 2 and extending in the circumferential and radial oblique spirals of the disk. Provided by In each passage between the adjacent impeller blades 8, the first open portion 10 opened on the compression action surface 9 of the drive scroll disk 2 is radially outward from the second open portion 11 on the opposite side. Is located. Thus, when the drive scroll disk 2 is assembled and rotated in the casing 1, the impeller portion 7 draws the fluid toward the compression action surface 9 and exerts a centrifugal force on the fluid and radially outwards. In the area from the slightly outer portion of the first opening portion 10 where the fluid enters the compression action surface 9 to the outer circumferential end of the driving scroll disk 2, the spiral teeth (tooth) are formed in the direction in which the impeller wings 8 extend. The surface is formed.

FIG. 2 is a cross-sectional view showing the driven scroll disk 3 and its upper portion removed from the spir pump of FIG. 1, showing the shape of the impeller wing 8 and the spiral tooth surface. The connection point 7a between the lower edge of each wing 8 and the body of the impeller portion 7 precedes the connecting point 7b between the upper edge of the wing and the body of the impeller portion 7 in the direction of rotation of the impeller portion. The fluid is transported from the second open portion 11 to the first open portion 10. In the illustrated embodiment, three teeth 13 are formed at even intervals along the circumference of the disk 2 to form three similar spiral grooves 12. The bottom surface of the groove 12 has a height parallel to the connection point (7a).

The number of the recesses 12 may be three or more.

As better shown in FIG. 3, the driven scroll disk 3 has a toothed surface that can engage the toothed surface of the drive scroll disk 2, which has a recess 12 in the drive scroll disk 2; There is a tooth 14 that can be fitted. In the center of the driven scroll disk 3, there is a hole 16 into which the inclined shaft 15 is fitted. The driven scroll disk 3 has an inwardly projecting flange 17 and is fastened to the outwardly projecting flange 19 formed on the inclined shaft 15 by fastening means such as a plurality of bolts 18 and 18 '. 15). In addition, the tip of the drive shaft 5 supports the bottom of the inclined shaft 15 by the pivot 20.

The casing 1 includes a main casing including a support surface 21 rotatably supporting the drive scroll disk 2, a shaft hole 22 supporting the drive shaft 5, a suction port 23, and a discharge port 24. The cover 1 " is attached to 1 'by means of fastening means such as bolts 25 and 25'.

The suction port 23 guides the fluid to be conveyed to the impeller portion 7 of the drive scroll disk 2. The cover part 1 is comprised so that the inclination axis | shaft of the driven scroll disk 3 may maintain the state inclined at the predetermined angle (alpha) with respect to the drive shaft of a drive scroll disk.

In addition, the main casing 1 'is provided with a fluid transfer path 24' for transporting the fluid pushed out by the operation of the pair of scroll disks 2, 3 to the discharge port 24.

The fluid transfer path 24 'extends to the discharge port 24 along the outer edges of the scroll disks 2,3.

In addition, the fluid transfer path 24 'is gradually expanded from the upstream side to the discharge port 24 downstream as shown in FIG. 2, and the length of the groove 12 of the scroll disc 2 is increased. It is set longer than the length where the outer circumference meets.

When assembling the spiral pump of the present invention, first, the drive scroll disk 2 is disposed on the support surface 21 of the main casing 1 'and the drive shaft 5 is fitted into the shaft hole 22 and the shaft hole 4. Next, the assembly of the inclined shaft 15 and the driven scroll disk 3 is placed on the drive scroll disk 2 so that the teeth 13 are fitted into the grooves 12.

The distance between the two scroll disks 2, 3 forms a fluid chamber 26 when the disk 3 is coupled to the disk 2 in an inclined state and the teeth 13 and the recess 12 do not disengage. This distance is maintained in the pivot 20 of the axes of the disks 2, 3.

The cover part 1 has a bore 27 for receiving the upper part of the inclined shaft 15 of the driven scroll disk 3, the inner diameter of the bore 27 being bushed to be in sliding contact with the shaft 15 ( 28) It is enough to accommodate at regular intervals. In addition, a threaded through hole is formed in the side wall of the lid 1. The angle adjusting member 29 is screwed through the through hole, and the tip of the member 29 pushes the upper side of the bushing 28 so that the bushing 28 and the inclined shaft 15 in the bushing 28 are driven by the driving shaft 5. ) And the angle of intersection (α).

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 scroll disk 3, so that the inclined shaft 15 has the angle adjusting member 29. It is tightly coupled with the tip of the to maintain the inclined posture without shaking.

The inclined coupling between the scroll disks 2 and 3 is best shown in FIG. 1, and the one between the two recesses of the recesses on the left side in the drawing has the smallest joining force, so that there is a variable volume of fluid between the recesses. The compression chamber 30 is formed. The volume of the compression chamber 30 is maximum when the coupling degree is the smallest. While the discs 2 and 3 are rotated together and these recessed joints on the left side are moved to the right in the drawing, their engagement becomes deeper, and 180 ° circumferentially moved from the point where the compression chamber 30 volume is maximum. In the end, the size of the compression chamber 30 becomes zero and discharges the fluid.

That is, this groove coupling degree on the side where the driven scroll disk 3 is inclined is the deepest and the size of the compression chamber 30 is the smallest.

In this way all of the teeth 2 and 3 of the discs 2 and 3 can strongly 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 compression chamber 30 is the inclination of the disc 3, that is, the inclination of the axis 15. Therefore, the angle adjusting member 29 is a means for adjusting the discharge flow rate of the spiral pump. The larger the crossing angle α between the shafts 5 and 15 by the angle adjusting member 29, the greater the maximum volume is, the larger the flow rate is. On the contrary, the smaller the crossing angle α, the lower the flow rate. Of course, the output flow rate can also be adjusted by the rotational speed of the drive shaft (5).

Operation of the spiral pump according to the present invention configured as described above is made as follows.

When the driving scroll disk 2 is rotated by the rotation of the drive shaft 1, the driven scroll disk 3 is interlocked with one side thereof, so that the impeller portion 7 integral with the driving scroll disk 2 is connected. Rotate As the impeller portion 7 rotates, the fluid is sucked into the fluid chamber 26 through the impeller wing 8 at the suction port 23 side and then is pushed outward by centrifugal force. The pushed out fluid is oriented at the radially inner side of both scroll discs 2 and 3. It penetrates into the gap between the two and the largest amount of fluid flows in the smallest portion of the scroll disk (2, 3), that is, the left side of FIG. The introduced fluid is then discharged to the fluid path 24 'along the spiral curved surface by rotation of the scroll disks 2, 3 (clockwise in FIG. 2). At this time, the flowed fluid moves along with the rotation of a pair of scroll disks (2, 3). As the gap between them narrows gradually, complete perfection is continuously made at the right point of FIG. Is discharged to the fluid transfer path 24 '. The pressure at this time can be increased as much as the opening degree of the discharge port is controlled. This is because the closing action occurs at the fully engaged portions of the scroll disks 2 and 3.

The fluid discharged to the fluid transfer path 24 'by the above process is pushed toward the discharge port 24 by the centrifugal force and the discharge pressure to perform the pumping action.

Figure 4 shows a double scroll gradient compression element which is a second embodiment of a spiral pump according to the invention. This embodiment includes a pair of opposing drive scroll disks 102, 102 'and a driven scroll disk 103 positioned between them. And a pair of drive scroll disks 102 and 102 'and a driven scroll disk 103 positioned therebetween. The pair of drive scroll disks 102 and 102 'may be coupled to the drive shaft 105 through the key 106 to co-rotate.

The driven scroll disk 103 has an opening 104 at its center and is kept inclined in a constant direction between the drive scroll disks 102 and 102 'by a casing (not shown). Each of the three scroll disks has a spiral tooth shape, and the first driving scroll disk 102 has a counterclockwise spiral tooth shape on the top thereof as the teeth of the driving scroll disk 2 of the first embodiment, and a second driving scroll disk. 102 'has a clockwise helix on its underside.

The driven scroll disk 103 has a clockwise helix tooth on a surface facing the first driving scroll disk 102 and a counterclockwise helix tooth on a surface opposite the second driving scroll disk 102 'on the opposite side. Therefore, when the two disks 102 and 102 'rotate, the driven scroll disk 103 is rotated in an inclined position by them.

Impeller portions 107 and 107 'are integrally formed in each of the driving scroll disks 102 and 102' so that fluid is introduced from both sides of the spiral pump in both directions to transfer between the two driving scroll disks. When the three disks 102, 102 ', 103 are assembled, the maximum volume of compression chambers 130, 130' are formed on the upper and lower surfaces of the driven scroll disk 103 at a position 180 ° away from the circumference of the disk. Pressurized fluid is discharged at circumferential 180 ° shifted points 131, 131 ′ where fluid is introduced and exerts maximum compression force by co-rotation of the disks therefrom. Since the direction of fluid discharge at the discharge point (131, 131 ') is the same due to the engagement between the disks, the fluid is discharged from one discharge port by joining with the other discharge point by the fluid transfer path toward one discharge point. Can be configured to

Thus, the dual scroll inclined compression spigot pump configuration of the second embodiment can provide about twice as much fluid delivery as the spir pump of the first embodiment, as well as on both sides of the inclined driven scroll disk 103. By simultaneously performing balanced pumping at the same time, quiet pump operation can be achieved in which the pump elements cannot swing.

As described above, the spiral pump according to the present invention sucks the fluid by driving the impeller and flows the sucked fluid between one or two opposing scroll disk surfaces which are continuously engaged on one side as the gear pump is rotated. Since it is to be discharged in accordance with the high head to provide a breakthrough and excellent effect to send a large flow rate.

Claims (7)

A casing (1) having an inlet (23) and an outlet (24), and an impeller (7) rotatably installed in the casing (1) for sucking fluid from the inlet (23) side by the rotation thereof. ) And a pair of scrolls that engage with each other to interlock with the impeller 7 and inject the fluid discharged from the impeller 7, and then provide a compressive force according to rotation to push the fluid outward to enable ejection. A spiral pump comprising a disk (2, 3). 2. A spiral pump according to claim 1, wherein the pair of scroll disks (2, 3) are meshed with a plurality of spiral teeth at each one side end thereof opposite. The method of claim 1 or 2, wherein the pair of scroll disks (2, 3) are divided into a drive scroll disk (2) and a driven scroll disk (3), each of which is supported by the casing (1). A spiral pump having a drive shaft (5) and an inclined shaft (15). 4. The drive shaft (5) according to claim 3, characterized in that the inclined shaft (15) is inclined with respect to the drive shaft (5) such that the pair of scroll disks (2, 3) are rotated in a state where the pair of scroll disks (2,3) is engaged with the maximum at one side and the minimum at the other side. Spir pump. 4. A spiral pump according to claim 1 or 3, wherein the impeller (7) is formed integrally with the drive scroll disk (2). The casing (1) of the casing (1) is in communication with the impeller (7), the outlet (24) is in communication with the outer periphery of the pair of scroll disks (2, 3), the casing A spiral pump, characterized in that (1) comprises a main casing portion (1 ') and a lid portion (1). 7. The discharge port (24) according to claim 1 or 6, wherein the casing (1) has a discharge port (24) therein for guiding fluid discharged outwardly of the pair of scroll disks (2,3) to the discharge port (24). Spiral pump, characterized in that it comprises a fluid transfer path (24 ') is formed to gradually expand toward the side.