JPS582495A - Voltex flow pump device - Google Patents

Abstract

PURPOSE:To reduce the loss torque due to the friction between an impeller and a case by forming spiral grooves on one side of the impeller so as to perform a pumping action and to reduce the thrust load applied to the impeller. CONSTITUTION:A multitude of grooves 34 are radially formed on the outer periphery of both sides of an impeller 33, on one side of which is formed spiral grooves 35. Therefore, the fluid sandwitched in the gap 30 formed by a lug 16' of a suction side case 13 of the impeller 33 is pushed into the spiral grooves 35 by revolutions of the impeller 33 to perform a pumping action, by which a force is applied to the impeller 33 in the direction of a discharge side case 23, thus the thrust load applied to the impeller in the direction of the suction side case 13 can be reduced. Thereby, the loss torque due to the friction between the impeller and the case can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vortex pump device that obtains a high-pressure fluid with a receiving flow rate, which is used, for example, in an automobile fuel pump, and the object thereof is to reduce the trust load acting on an impeller. be.

1 and 2 show one side of a conventional vortex pump device. In Figures 1 and 2, 1 is an impeller;
This impeller 1 is disk-shaped, and a plurality of grooves 7 are formed radially on the outer periphery of both sides thereof. The rotating shaft 3 is press-fitted into the impeller 1, and the impeller 1 is rotated via the rotating shaft 3 by the motor. The impeller 1 is the pump case 2,
2/ via bearings 4, 4' so as to be freely rotatable.

The pump cases 2, 2' are provided with a partition wall 8 that partitions a low-pressure part where the suction port 6 is located and a high-pressure part where the discharge port 6 is located.

Next, we will explain the operation of the above conventional example (Fig. 1,
In FIG. 2, the impeller 1 is rotated by a motor in the direction of the arrow. As the impeller 1 rotates, fluid sucked in from the suction port 5 flows through a fluid passage 9 partitioned by the impeller 1 and the pump cases 2, 2' as the impeller 70 rotates. Furthermore, the fluid that has entered the grooves 7 formed on the outer periphery of the fuη surfaces of the impeller 10 flows out into the fluid passage 9 due to the centrifugal force caused by the rotation of the impeller 1, and merges with the flow in the fluid passage 9. At this time, the flow within the fluid passage 9 is disturbed, which increases the pressure of the fluid.

Assuming that the circumferential speed of the impeller 1 is u and the cross-sectional area of the fluid passage 9 is A, the maximum pressure Pmax at the discharge port 6 of the vortex pump device is P maxcc u2 The maximum flow rate Qmax of the vortex pump device is Q maw =: Au The characteristics of the vortex pump device are shown in FIG. 3a. Further, the efficiency 1 of the vortex pump device is indicated by a' in FIG. Efficiency l is approximately 6 of the maximum flow rate Qmax
It is maximum when the flow rate is 0%. The characteristics and efficiency of the vortex pump device are determined by the outer diameter and rotational speed of the impeller 1, the shape of the groove 7, the shape of the fluid passage 9, and the blades.

It is determined by fluid leakage from the gap between the wheel 1 and the pump cases 2, 2'.

Vortex pump devices are better suited for low flow, high pressure applications than other turbine pumps. However, in the above conventional example, in order to obtain high pressure with an even smaller flow rate, there was a drawback that the pump efficiency decreased.Next, in order to eliminate the drawbacks of the above conventional example, the present inventor has already proposed a method. The vortex pump device will be explained with reference to FIGS. 4 and 5.

In FIGS. 4 and 6, reference numeral 10 denotes an impeller, and a plurality of grooves 11 are formed radially on the outer periphery of both side surfaces of the impeller 1o. In addition, at the center of the impeller 10 is a rotating shaft 1.
2 is fixed. Note that without fixing the impeller IQ to the rotating shaft 12, the driving force of the rotating shaft 1.2 is
may be engaged so that the transmission can be transmitted to the user. The impeller 1o has a suction side case 13, a partition case 18. It is installed in a space formed by the discharge side case 23 via bearings 29, 29' in a non-contact manner. Note that a sealing material such as a thin sheet that obstructs the flow to the gaps between the impeller 10 and each of the above-mentioned cases is placed in the gaps 30.
, 30', and 30''. Also, in order to cut off leakage from the gap between the rotating shaft 12 and the discharge side case 23, a sealing material such as packing may be added to the gap 31.

Further, in this embodiment, the impeller 1o and the rotating shaft 12 are supported by the suction side case 13 and the discharge side case 23 by bearings 29, 29', and the rotating shaft 12 is supported by a motor outside the pump case. The impeller 1o may be supported and have a cantilevered structure with respect to the rotating shaft 12. A structure may also be used in which one of the twisted rotating shafts 12 is supported by a motor or the like outside the pump case, and the other is supported by the pump case.

A hole 14 having a stepped portion for holding a bearing 29 is formed in the center of one side of the suction side case 13 . Reference numeral 15 denotes an annular groove formed on one side of the suction side case 13, and a starting end and a terminal end of this groove 15 are separated by a partition wall 16. 17 is a through suction port formed at the starting end of the groove 16, and the fluid passes through this suction port 17,
It is sucked into the starting end of the groove 16.

18 is a partition case, and an annular partition wall 19 is formed on the inner wall of this partition case 18.

A notch 2o is formed in a part of this partition wall 19. Further, annular step portions 21 and 21' are formed on both sides of the inner wall of the partition case 18, and the starting and ending ends of each step 21 and 21' are separated by partition walls 22 and 22', and at the same time The terminal end of the first step 21 is connected to the starting end of the second step 21' via a notch 2o provided in a part of the partition wall 19. Furthermore, in the conventional examples shown in FIGS. 4 and 6,
Although the notch 2o is used to connect the step portions 2M and 21', a connecting passage such as a pipe may also be used.

Reference numeral 23 denotes a discharge side case, and a through hole 24 having a stepped portion is formed in the center of the discharge side case 23 for holding the two bearing gears and protruding the rotating shaft 12. 26
is an annular groove formed on one side of the discharge side case 23, and the starting end and the terminal end of this groove 25 are separated by a partition wall similar to the partition wall 16 of the suction side case 13. 2
Reference numeral 7 denotes a through-hole discharge port formed at the end of the groove 25, and the fluid exits through the discharge port 27.

As shown in FIG. 4, by combining the impeller 1o, the suction side coos 13, the partition case 18, and the discharge side case 23, a first fluid passage 28 is formed by the groove 16, the stepped portion 21, and the impeller 10. , the groove 26, the stepped portion 21' and the impeller 10
A second fluid passage 28' is formed. The terminal end of the first fluid passage 28 and the starting end of the second fluid passage 28' are connected through a notch 2o provided in the partition case 18.

Next, regarding the operation of the conventional example shown in FIG. 4 and FIG.
This will be explained with reference to FIG. In FIG. 4, the impeller 1o is rotated by the motor in the direction of the arrow. Impeller 10
Due to the rotation of the suction port 1 provided in the suction side case 13
The fluid sucked in from the impeller 10 is pulled by the impeller 10 and flows through the first fluid passage 28 . The principle of increasing the pressure of the fluid at this time is the same as that of the conventional vortex pump device shown in FIGS. 1 and 2. The pressure of the fluid increases as it flows through the fluid passage 28, and a partition wall 16. ．． 22, the second
into the fluid passageway 28'. The principle of increasing the pressure of the fluid flowing through the second fluid passage 28' is the same as that of the conventional vortex pump shown in FIGS. 1 and 2, but the fluid flowing into the second fluid passage 28' is already under pressure. It's getting expensive. As the fluid advances through the second fluid passage 28', its pressure is further increased, and it hits the partition wall 22' that partitions the low pressure section and the high pressure section, which are composed of the discharge side case 23 and the partition case 18, and flows into the discharge side case 23. It exits from the provided discharge port 27.

FIG. 6 is a diagram showing the characteristics and efficiency of the conventional example shown in FIGS. 4 and 6 in comparison with the characteristics and efficiency of the conventional example shown in FIGS. 1 and 2. According to the conventional example shown in Figure 6,
It is possible to reduce the flow rate and increase the pressure without reducing efficiency. In addition, in FIG. 6, a,
a' are the characteristics and efficiency of the conventional vortex pump device shown in FIGS. 1 and 2, respectively, and b and b' are the characteristics and efficiency of the
Figure 6 shows the characteristics and efficiency of the conventional vortex pump device shown in Figure 6.

According to the conventional vortex pump device shown in FIGS. 4 and 6, fluid passages are formed on both sides of one impeller without changing the dimensions of the impeller and the grooves on the impeller. By connecting the passages in series, the fluid passage cross-sectional area is
Since it is half of the conventional example shown in Figures 1 and 2, and the distance of the fluid passage for applying pressure to the fluid is longer, it is better than the conventional example shown in Figures 1 and 2 without reducing efficiency. It has the advantage of being able to obtain high-pressure fluid with the amount of flow it receives.

However, in the vortex pump apparatus shown in FIGS. 4 and 6, the pressure of the fluid flowing through the second fluid passage 28' is
Since the pressure is higher than that of the fluid flowing through the fluid passage 28, a thrust load is generated on the impeller 1o. Due to the generation of the thrust load, the impeller 1o is pressed against the suction side case 13, and the friction between the impeller 10 and the suction side case 13 increases the torque required to rotate the impeller 1°. That is,
This torque becomes loss torque and reduces pump efficiency. In the conventional example shown in FIGS. 4 and 6, a ball bearing 29 is used to receive the thrust load and keep the impeller 1o and the suction side case 13 out of contact. If it is possible to reduce the thrust load, use a sliding bearing, which is cheaper than a ball bearing, to support the thrust load instead of the ball bearing 2.9 used to support the thrust load. be able to.

An object of the present invention is to reduce the thrust load acting on the impeller by forming a spiral groove on one side of the impeller.

Next, an embodiment of the present invention will be described with reference to FIG. In Fig. 7, 33 is an impeller, and Figs.
Similar to the impeller 10 shown in the figure, a plurality of grooves 34 are formed radially on the outer periphery of both side surfaces of the impeller 33. Further, a rotating shaft 36 is fixed to the center of the impeller 33. Note that the impeller 33 may not be fixed to the rotating shaft 36, but may be engaged with the rotating shaft 36 so that the driving force can be transmitted to the impeller 33. Furthermore, a piece of the impeller 33 facing an annular protrusion 16' formed in the suction side case 13 for blocking the flow of fluid from the first fluid passage 28 toward the center of the suction side case 13; A spiral groove 35 is formed on the side surface.

Due to the rotation of the impeller 33, the impeller 33 and the suction side case 1
The fluid sandwiched in the gap 3o formed by the protrusion 16' of No. 3 is forced into the spiral groove 36 and performs a pumping action. Due to this pumping action, a force acts on the impeller 33 in the direction of the discharge side case 23, and the thrust load acting on the impeller 33 in the direction of the suction side case 13 can be reduced.

It should be noted that the impeller is not limited to the one in the above embodiment;
As shown in the figure, an impeller 37 may be used in which a plurality of grooves 38 are spirally formed on the outer periphery of both sides of the disk, and as shown in FIG. In,
An impeller 39 may be used in which a plurality of grooves 40 are formed along a line inclined with respect to the radial line of the disk.

The present invention has the above configuration, and according to the present invention, the thrust load acting on the impeller can be easily reduced by a simple structure in which a spiral groove is formed in the center of one side of the impeller. This has the advantage of being able to reduce the Therefore, according to the present invention, 1. It has the advantage of reducing torque loss due to friction between the impeller and the case, preventing a drop in pump efficiency, and using an inexpensive plain bearing.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view of a conventional vortex pump device, and Figure 2 is a cross-sectional view of a conventional vortex pump device.
3 is a characteristic diagram of a conventional vortex pump device, FIG. 4 is a sectional view of a vortex pump device already proposed by the present inventor, and FIG. 5 is an exploded perspective view of the same device. Fig. 6 is a diagram comparing the characteristics and efficiency of the device with those of a conventional example, Fig. 7 is a perspective view of an impeller of a vortex pump device according to an embodiment of the present invention, and Fig. 8 is a diagram comparing the characteristics and efficiency of the same device with those of a conventional example. FIG. 9 is a perspective view of the impeller of the second embodiment, and FIG. 9 is a perspective view of the impeller of the third embodiment of the present invention. 1o ・Advanced impeller 1.11...Groove, 12...
...Rotating shaft, 13...Suction side case, 14.
...hole, 15 ... annular groove, 16 ...
...Partition wall, 17... ...Suction port, 18...Partition case, 19...
...Annular partition wall, 16'...Protrusion, 20...
...notch, 21.21'... annular step, 2
2,22. '... Partition wall, 23... Discharge side case, 24... Hole, 26... Annular groove, 27... Discharge port, 28°28'...
...Fluid passage, 29.29'...Bearing, 3qs
o；3o″・・・Gap, 31・・・Gap,
33... Impeller, 34... Groove, 35...
...Spiral groove, 36 ... Rotating shaft, 37 ...
...impeller, 38...groove, 39...impeller, 4o...groove. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 2

Claims (1)

[Claims] A plurality of spiral grooves are formed on the inner circumferential side of the plurality of first grooves on one side of the disk, and are formed radially, spirally, or obliquely with the first grooves of number Ka on the outer circumference of both sides of the disk. An impeller having a second groove formed therein, a rotation shaft for rotating the impeller, a pump case housing the impeller, an inner wall of the pump case and the impeller, Annular first. a second fluid passage; a second fluid passageway; A part of the second fluid passage is connected to a partition wall, a suction port connected to a starting end of the first fluid passage, and a terminal end of the four first fluid passages to a starting end of the second fluid passage. A vortex pump device comprising a connecting passage and a discharge port connected to the terminal end of the second fluid passage.