KR0145236B1 - Regenerative pump - Google Patents

Abstract

It is an improvement of the friction regeneration pump in which a blade extending substantially radially in the peripheral portion of the disk-shaped impeller. The blade is formed in a plane perpendicular to the axis of rotation of the impeller, the surface of which is located forward in the direction of rotation of the impeller, and the point on this plane is the area of the blade with a large radius from the axis of rotation. In the direction of rotation of the impeller rather than the area of the blade with a small radius from the center of rotation is in the rear. This provides a frictional regeneration pump having a higher discharge pressure without reducing the discharge amount as compared with a pump having a blade extending in the radial direction of the impeller.

Description

Friction regeneration pump

1 is a cross-sectional view showing the main part of the friction regeneration pump according to the present invention,

2 is a cross-sectional view taken along line II-II of FIG. 1,

3 is a longitudinal sectional view of a fuel pump using one embodiment of a friction regeneration pump according to the present invention;

4 is an enlarged cross-sectional view of the pump in the embodiment shown in FIG.

5 is a plan view of the outer body in the pump,

6 is a bottom view of the partition plate in the pump,

7 is a plan view of a partition plate in the pump,

8 is a bottom view of the inner body in the pump,

9 is a plan view of the impeller in the pump,

10 is a partially enlarged plan view of the peripheral edge portion of the impeller in the pump;

11 is a longitudinal sectional view of a fuel pump using another embodiment of a friction regeneration pump according to the present invention;

12 is an enlarged cross-sectional view of the pump in the embodiment shown in FIG.

13 (a) to 13 (e) show cross-sectional shapes of the blades of the pump impeller of the present invention.

Drawing with contour along with the cross-sectional shape of the blade of the pump impeller,

14 shows the relationship between the discharge pressure and the flow rate of the pump of the present invention together with that of the pump of the comparative example.

Figure,

Figure 15 shows the relationship between the rotational speed and the flow rate of the impeller of the pump of the present invention

Plots compared to

16 is an enlarged cross-sectional view of an essential part of a conventional frictional regeneration pump;

17 is a cross-sectional view taken along line XVII-XVII of FIG. 16,

18 is an enlarged cross-sectional view of an essential part of a known improved friction regeneration pump, and

FIG. 19 is a cross-sectional view taken along line XIX-XIX in FIG. 18. FIG.

* Explanation of symbols for main parts of the drawings

1: housing 2: rapeseed passage

3: impeller 4: blade

5: home PO1, PO2, P1: pump

[Background of invention]

[Field of Invention]

The present invention relates to an improvement of a friction regeneration pump used in a fuel pump of an automobile, and more particularly, to improve the pump efficiency by increasing the discharge pressure without reducing the discharge amount as compared with the conventional friction regeneration pump.

[Description of the Prior Art]

The friction regeneration pump has an impeller including a plurality of grooves formed on both sides of the peripheral edge portion and a blade positioned radially in the substrate between the grooves at the edges of the flat disc-shaped substrate. In the pump chamber formed in the housing, the impeller is rotated in a plane perpendicular to the axis by an axis arranged at the center of the substrate, and the liquid flowing from the inlet formed in the housing is connected to the housing at high pressure. It is also known as a non-contact pump for discharging from the discharge port formed.

The frictional regeneration pump, which is known as a general formula, is denoted by reference numerals PO1 in FIGS. 16 and 17, and is stored in the pump chamber in the housing 1 and rotated as an impeller 3. In the peripheral edge portion of the substrate, a plurality of grooves 5 each having a larger length are formed at equal intervals on both sides of the substrate as they reach the outer peripheral edge of the substrate, and between these grooves 5 in the circumferential direction. The blades 4 having the same width are formed in the radial direction of the substrate.

The pump chamber for accommodating the impeller 3 includes a flat inner wall 6 facing the flat side surface portion of the substrate and a cylindrical inner circumferential wall 7 facing the circumferential edge of the blade 4 of the outer peripheral edge of the substrate; At the position corresponding to the lateral side of the blade 4, the inner wall 6 and the inner circumferential wall 7 are connected, and at the same time, the inlet and the discharge port (not shown) formed in the housing 1 are connected. A half moon-shaped groove wall surface 8 forming the fluid passage 2 is provided.

In the conventional friction regeneration pump PO1, the flow LM based on the friction between the blade 4 and the fluid flows into the fluid passage 2 by the rotation of the fluid and the impeller 3 at the arrow F. It occurs in the rotational direction of the impeller 3 to be displayed, and in the radial direction of the impeller 3 along the surface 9 located forward with respect to the rotational direction F of the impeller 3 of the blade 4. The stream LB joins the stream LM in the fluid passage 2.

As a result, the velocity energy is converted into pressure energy by the reduction of the velocity of the flow LM of the fluid flowing from the inlet port and flowing through the fluid passage 2, and discharged at high pressure from the discharge port. Japanese Patent Application Laid-Open No. 2-45690 describes an improvement of the friction regeneration pump shown in FIGS. 18 and 19.

In this pump PO2, the radius decreases in the region where the radius from the center of rotation of the impeller 3 is small, as is apparent from the eighteenth degree of the width of each blade 4 of the impeller 3. Gradually increasing, and as a result, the end edge of the central axis of rotation of the impeller 3 of each concave groove 5 has a shape in which two half moon faces 4a and 4b are connected.

In the pump PO2, the center points of the widths in the circumferential direction of the respective blades 4 are the same as the pump PO1 in that they are located on one radial line passing through the center of rotation of the impeller 3, respectively. As compared with the pump PO1, the flow LB generated in the concave groove 5 flows smoothly due to the presence of the half moon faces 4a and 4b, thereby increasing the pump discharge pressure.

However, when the radial length of the blade 4 is the same as the length of the blade 4 of the pump PO1, the volume of the concave groove 5 is reduced to reduce the discharge amount, so that the pump efficiency is not improved. Do not.

[Overview of invention]

The original object of the present invention is to increase the discharge pressure without reducing the discharge amount. It is to provide a friction regeneration pump with improved pump efficiency.

Still other objects of the present invention will become apparent to those skilled in the art from the following disclosure and description of the preferred embodiments of the present invention.

The present invention is a flat disk-shaped substrate, which is rotatably supported by a shaft on a housing, and the two sides are rotated in a plane perpendicular to the axis of rotation of the shaft. An impeller having blades located approximately radially with respect to the substrate between a plurality of concave grooves and their concave grooves formed on both sides of the part, and a flat inner surface formed in the housing and opposing both flat side surfaces of the substrate of the impeller. A fluid passage connecting the inner wall and the inner circumferential wall at the position opposite to the wall surface, the cylindrical inner circumferential wall facing the tip edge of the blade, and the inner circumferential wall and connecting the inlet and outlet of the fluid formed in the housing; It is provided with the half-moon-shaped groove-shaped wall surface to form, and In the pump chamber for receiving the Im kkwelreo it relates to an improvement of the friction pump comprising a reproduction thereof.

According to the present invention, each blade of the impeller is located in front of the direction of rotation of the impeller, the center point of the width in the circumferential direction in the plane perpendicular to the rotation center axis radius from the rotation center axis In this large part, it extends so that it may be located at least on the same radius line or rearward with respect to the rotation direction of the impeller rather than the part whose radius from the said center of rotation is smaller.

Thereby, the length of the surface which exerts a centrifugal force on the fluid which flows along the surface located ahead with respect to the rotation direction of the said impeller of each blade according to the rotation of the said impeller can be ensured, and the discharge pressure of a pump can be increased. .

According to the present invention, the center point of the width in the circumferential direction in the plane perpendicular to the rotation center axis of each blade of the impeller passes through the rotation center axis in an area having a large radius from the rotation center axis of the impeller. Is positioned on the general meridian of the substrate.

As a result, the radial flow of the fluid flowing along the surface positioned with respect to the rotational direction of the impeller of the blade is substantially perpendicular to the flow of the fluid flowing through the pump and the chamber, thereby further increasing the discharge pressure of the pump. Can be.

Furthermore, according to the present invention, each blade of the impeller has a center point of the width in the circumferential direction in the vertical plane of the impeller in the rotation direction of the impeller as the radius from the center of rotation increases. It is extended so that it is located laterally with respect to it.

This makes it possible to select the magnitude of the centrifugal force acting on the fluid flowing along the plane located forward with respect to the rotational direction of the impeller of the blade and the angle at which the flow of fluid merges with the fluid flowing through the fluid passage. The discharge pressure can be obtained according to the use of the friction regeneration pump.

Various other objects, features, and additional advantages of the present invention will be better understood in light of the following detailed description when considered in conjunction with the accompanying drawings, wherein like reference numerals designate like elements throughout.

Detailed Description of the Preferred Embodiments

3 and 4 show a fuel pump for an automobile engine using one embodiment of the frictional regeneration pump of the present invention. The fuel pump is configured to accommodate the pump P1 and the motor 41 according to the present invention in the cover 42.

In this embodiment, the pump P1 is provided with two first impellers 31A and 315 arranged in this embodiment, and the first pump chamber 11A formed by the outer body 12 and the partition plate 18. The first impeller 31A disposed therein and the second impeller 31B arranged inside the second pump chamber 11B formed by the partition plate 18 and the inner body 25 and the motor 41 It is a two-stage pump driven to rotate simultaneously by the drive shaft 47.

The impellers 31A and 3LB have the same structure, and each has a flat disc-shaped substrate 10 and a plurality of concave grooves 34 formed on both sides of the substrate 10 at the peripheral edges of the substrate 10. Between these recessed grooves 34, the blade 33 located radially with respect to the said board | substrate 10 is provided. Both impellers 31A and 3LB are supported by the drive shaft 47 so that the flat side surface of the substrate 10 rotates in a plane perpendicular to the rotation center axis of the drive shaft 47 of the motor 41.

The outer body 12 of the pump P1 is integrally provided with an inlet pipe 13 on the outer side thereof, and the surface of the first impeller 31A on the side facing the first pump chamber 11A. A flat inner wall 14A opposite the flat surface of the substrate 10 and a cylindrical inner circumferential wall 18A opposite the leading edge of the blade 33 of the first impeller 31A are formed, and the blade ( The inlet 16 and the partition plate 19 which connect the inner wall 14A and the inner circumferential wall 18A at a position opposite to the side surface of the cover 33 and communicate with the inner passage of the inlet plate 13 are provided. As shown in FIG. 5, a concave groove wall surface 15 which connects a position opposed to the outlet-inlet 23, which will be formed through, is approximately 5 / of the circumferential length of the first pump chamber 11A. It is formed over the length of 6. The recessed part 15a is provided in the chisel part which communicates with the outflow_flow_port | entrance 23 of this groove-shaped wall surface 15, and a step is provided.

Reference numeral 37 denotes a recess for loosely accommodating the tip end of the drive shaft 47 formed at the center of the inner wall 14A of the outer body 12.

The partition plate 19 is a flat shape having a circular contour, and a through hole 20 for loosely inserting the drive shaft 47 of the motor 41 is formed at the center thereof and at the outer body 12. Outflow-inlet formed by penetrating the partition plate 19 at a position circumferentially extending over a length of approximately 5/6 of the circumferential length of the first pump 11A from the position corresponding to the formed inlet 16. 23 is formed.

On the surface of the partition plate 19 facing the first pump chamber 11A, a flat wall surface 17A is formed to face the flat surface of the substrate 10 of the first impeller 31A, and the sixth As shown in the figure, the wall surface 17A and the inner circumferential wall 18A of the outer body 12 are connected to each other, and at the same time between the outlet-inlet 23 and the position corresponding to the inlet 16. The concave groove wall surface 21 is formed in an arc shape over a length of approximately 5/6 of the circumferential length of the first pump chamber 11A.

As a result, the inlet 16 and the outlet-inlet are formed in the first pump chamber 11A by the groove-shaped wall surface 15 formed in the outer body 12 and the groove-shaped wall surface 21 formed in the partition plate 19. A first fluid passage 36A connecting 22 is formed in the circumferential direction over approximately 5/6 lengths of the circumferential length of the pump chamber 11A. In the fluid passage 36A, the blade 33 of the first impeller 31A is exposed.

In the inner body 25 of the pump P1 is formed a through-hole 26 penetrating loosely through the drive shaft 47 of the motor 41 at the center thereof, and at the same time, an outlet-inlet 23 formed in the partition plate 19. The second pump chamber 11B and the cover penetrate the inner body 25 at positions distant from the circumferential direction over approximately 5/6 lengths of the circumferential length of the second pump chamber 11B at a position opposite to A discharge port 29 communicating with the internal space of 42 is formed.

On the surface facing the pump chamber 11B of the inner body 25, a flat inner wall surface 14B facing the flat portion of the substrate 10 of the second impeller 31B and a blade 33 of the impeller 31B. A cylindrical inner circumferential wall 18B opposite to the leading edge is formed, and at the position opposite to the side surface of the blade 33, the inner wall 14B and the inner circumferential wall 18B are connected to each other; 29 and a concave groove-shaped wall surface 28 which connects the position opposite to the outlet-inlet 23 are formed as shown in FIG.

On the surface facing the second pump chamber 11B of the partition plate 19, a flat wall surface 17B is formed opposite to the flat surface of the substrate 10 of the second impeller 31B. As shown in the figure, the wall surface 17B and the inner circumferential wall 18B of the inner body 25 are connected, and at the same time between the outlet-inlet 23 and the position opposite to the outlet 28. A concave groove wall surface 22 is formed in an arc shape over approximately 5/6 lengths of the circumferential length of the pump chamber 11B.

As a result, the outlet-inlet 23 and the discharge port are formed in the second pump chamber 11B by the groove-shaped wall surface 28 formed in the inner body 25 and the groove-shaped wall surface 22 formed in the partition plate 19. A second fluid passage 36B connecting 29 is formed in the circumferential direction over the length of approximately 5/6 of the circumferential length of the second pump chamber 11B. In this fluid passage 36B, the blade 33 of the second impeller 31A is exposed.

9 is a plan view of the impeller according to the present invention. Since the first impeller 31A and the second impeller 31B have the same structure, they are indicated by reference numeral 31 in the drawings.

The impeller 31 is made of a flat disk-shaped substrate 10, and the concave groove 34 that increases in length as the peripheral edges reach both sides of the substrate 10 at the peripheral edges of the substrate 10. A plurality of at equal intervals in the circumferential direction, and a blade 33 having a constant width in the circumferential direction is formed between the recessed grooves 34.

A ridge hole 38 is formed at the center of one surface of the substrate 10, and a sectional D-shaped shaft hole is formed by combining a cylindrical inner wall and a planar inner wall with the center of rotation as the center of rotation of the substrate 10. (32) is penetrated, and the impeller (31) is attached to the drive shaft (47) of the motor (41) through the shaft hole (32). The inner side surface portion of the substrate 10 in the radial direction from the concave groove 34 is a flat surface.

The present invention is characterized in that the direction of rotation of the impeller 31 of the blade 33 (indicated by arrow F) is shown in FIG. 10 in which a part of the peripheral edge of the impeller 31 is enlarged. Direction) is formed in the concave surface 30 in the plane perpendicular to the rotational center axis of the impeller 31, and in the plane perpendicular to the rotational center axis of the blade 33. The center point 40 of the width in the circumferential direction of the blade 33 is rotated by the impeller 31 in a region where the radius from the center of rotation of the blade 33 is larger than the area of a radius from the center of rotation of the blade 33. It is located in the rear with respect to the direction (F).

In the present invention, preferably in the plane perpendicular to the axis of rotation of the impeller 31 of the blade 33, the radius from the axis of rotation of the center point 40 in the circumferential direction of the blade 33 If the center point of this minimum position is 40A, the center point of the maximum position is 40C, and the center point at approximately the center position of the center points 40A, 40C is 40B, the center point 40 is in the plane perpendicular to the rotation center axis. As shown in FIG. 10, the line connecting the center line is located on a half-moon-shaped line with the front concave with respect to the direction of the arrow F between the center point 40A and the center point 40B. Between 40B) and the center point 40C, it is located on the general meridion line 60 of the board | substrate 10 which passes through the center point 40B.

In FIG. 10, the blade 33 shown by the broken line shows the blade formed in the back surface of the said board | substrate 10, and is formed by shifting the position in the circumferential direction with the blade 33 of the surface shown by the solid line.

In addition, in the fuel pump shown in FIG. 3, the motor 44 for driving the pump P1 is arranged in the cover 42, and the rotor 46 of the motor 41 has the drive shaft ( At one end of the end portion 47, the end member is supported by the bearing body 49 on the inner body 25, and closes the end portion of the cover 42 at the other end portion of the drive shaft 47. It is supported by the bearing 50 at 43.

The commutator, brush, choke coil, etc. of the motor 41 are not shown. When the motor 41 is driven, the first impeller 31A and the second impeller 31B of the pump P1 rotate at the same time as the drive shaft 47, and the fuel sucked from the inflow cup 3 is discharged. The inside of the cover 42 from the discharge port 29 of the inner body 25 via the fluid passage 36A of the first pump chamber 11A and the fluid passage 36B of the second pump chamber 11B. Discharge into space.

The fuel discharged into the inner space of the cover 42 flows around the rotor 46 of the motor 41 and passes through the check valve 45 arranged in the end member 43, and the discharge pipe 44 Ejected from.

11 and 12 show a fuel pump for an automobile engine using another embodiment of the frictional regeneration pump of the present invention. The fuel pump shown in FIG. 11 differs only in that the pump P2, which is another embodiment of the present invention, is used in place of the pump P1 in the fuel pump shown in FIG. The same reference numerals are given to the same parts as the illustrated fuel pump, and the description thereof is omitted.

The pump P2 of the present embodiment is one blade 33 arranged in one pump chamber 11 formed between the inner body 25 and the outer body 12, the impeller 31 is It is the same as the 1st and 2nd impellers 31A and 3LB. The outer body 12 has the same structure as shown in FIGS. 4 and 5.

That is, the outer body 12 has an inlet 13 on its outer surface, and the surface facing the pump chamber 11 is flat against the flat wall surface 10A of the substrate 10 of the blade 33. A half moon-shaped groove shape which connects the inner wall 14 and the inner circumferential wall 18 facing the tip edge of the blade 33 and the inner wall 14 and the inner circumferential wall 18 to the inlet 16 at the same time. The wall surface 15 is formed. The surface facing the pump chamber 11 of the inner body 25 is flush with the flat side wall 10B of the substrate 10 in the same manner as the partition plate 18 shown in FIGS. 4 and 6. A wall surface 17 and a groove-shaped concave wall 21 connecting the wall surface 17 and the inner circumferential wall 18 are formed to penetrate the inner body 25 at the position of the outlet-inlet 23. The discharge port 29 is formed.

As a result, the inlet port 16 and the outlet port 28 are formed in the pump chamber 11 by the groove wall surface 15 formed in the outer spring body 12 and the groove wall surface 21 formed in the inner body 25. A fluid passage 36 connecting the c) is formed in the circumferential direction over the length of approximately 5/6 of the circumferential length of the pump chamber 11.

The blade 33 of the impeller 31 is exposed in the fluid passage 36.

The operation of the present invention will be described based on the embodiment of the frictional regeneration pump of the present invention schematically shown in FIGS. These drawings use the same reference numerals as the one-stage pump P2 shown in FIG. 11 and FIG.

When the impeller 33 rotates in the direction shown by the arrow F, the fluid passage 36 is formed in the fluid passage 36 formed in the pump chamber 11 by the two groove-shaped wall surfaces 15 and 21. By the movement of the blade 33 exposed inside, the flow LM of fluid arises in the same direction as the arrow F. As shown in FIG.

Flat both side surfaces 10A and 10B (FIG. 2) of the substrate 10 constituting the impeller 31 and the flat inner surface 17 of the outer body 12 and the flat inner surface 14 of the inner body 25. In the gap between and the rotation about the central axis of rotation of the impeller 31, the substrate 10 does not contact the outer body 12 and the inner body 25, the impeller 31 in the gap It has a minimum dimension in the radial direction of no fluid flow.

By the way, as the impeller 31 rotates, the surface of the blade 33 positioned forward with respect to the rotational direction of the impeller 31 indicated by the arrow F at the peripheral edge portion of the impeller 31 ( The fluid in contact with 30 is given a centrifugal force due to the rotation of the impeller 31, and the radial flow LB indicated by the arrow F is generated in the concave groove 34.

In the surface perpendicular to the rotational center axis of the impeller 31 (FIG. 1), the center point 40 of the width in the circumferential direction of the impeller 33 is from the rotational center axis of the blade 33. In an area with a large radius (area between center point 40B and center point 40C), relative to the direction of rotation P of the impeller 31 than an area with a smaller radius from the rotation center axis (area between center point 40A and center point 40B). Located in the rear.

Accordingly, the length of the face 30 corresponding to the length from the base (position of the center point 40A) of the blade 33 to the tip end (position of the center point 40C) is equal to the conventional impeller 3 shown in FIG. When the rotation speed of the impellers 31 and 3 is the same, the centrifugal force generated in the radial flow LB generated by the impeller 31 of the present invention is longer than the length of the surface 9 in the conventional impeller. It is larger than the centrifugal force generated in the radial flow LB generated by (3).

And in this invention, the width | variety of the circumferential direction of the said blade 33 in surface perpendicular | vertical to the rotation center axis | shaft of the said impeller 31 is set as the front-end | tip part from the base (position of center point 40A) of this blade 33 With the same dimensions up to the position of the center QN 40C, the volume of the concave groove 34 formed between the blades 33 is equal to that of the conventional impeller 3 with the blades 4 having the same width. It is the same as the volume of the recessed groove 5 in this.

Therefore, the frictional regeneration pumps Pl and P2 of the present invention can increase the discharge pressure without reducing the discharge amount as compared with the conventional frictional regeneration pump PO1.

The pump efficiency [η (%)] is given by equation (1) here.

η (%) = K, Q, N, T

Κ is the correction coefficient, P is the discharge pressure (KPa), Q is the discharge amount (ℓ / h), N is the rotational speed (rpm),

T is the load torque (Nm). In the pump P1 of the example of this invention shown in FIG. 3 and FIG. 4, it was k = 0.265 and T = 0.034 Nm.

When the rotational speed N and the load torque T are set to constant values by Equation 1, it can be seen that the pump efficiency η is proportional to the value P · Q multiplied by the discharge pressure and the discharge amount Q. Therefore, the pump efficiency is improved if the discharge pressure can be increased without reducing the discharge amount.

In the following, the pump P1 according to the embodiment of the present invention is compared with the conventional pump PO1 shown in FIGS. 16 and 17 and the conventional improved pump PO2 shown in FIGS. 18 and 19. Test data are shown in Table 1.

The comparative pumps PO1 and PO2 used for the test and the pump P1 of the embodiment of the present invention are provided with two stages of impellers 30 or 31, respectively, as shown in FIGS. 3 and 4.

Moreover, these pumps PO1, PO2, and P1 make the dimensions of the impellers 3 and 31 and the shape of the pump chamber the same, and are made of the shapes of the blades 4 and 33 formed in the impellers 3 and 31. The shapes shown in FIG. 16, FIG. 18, and FIG. 1 are respectively different shapes.

The comparison test was performed by comparing the discharge pressure P of each of the pumps PO1, PO2 and P1 to a constant value, but the discharge amount Q was 63.3 (l / h) for the pump P1 of the present invention. The discharge amount Q is larger than that of the comparative pumps PO1 and PO2, where the discharge amounts Q ((l / h)) are 61.1 and 59.5, respectively.

Therefore, the pump efficiency n proportional to the product of the discharge amount and the discharge pressure is larger than that of the comparison pumps PO1 and PO2.

Next, the discharge pressure P-discharge amount Q characteristic and the rotational speed N-discharge amount Q characteristics of the pump of the embodiment of the present invention are compared with those of the comparative pump.

12 (a) to 13 (e) show cross-sectional shapes of the blades formed in the impeller of the pump used for the above contrast, and the angular plane shows each blade in the plane perpendicular to the rotational center axis of the impeller. The cross section is schematically shown as an outline.

Each blade used in this comparative test has the same width t in the circumferential direction of the blade in the plane perpendicular to the rotational center axis, and rotates the tip of the blade (the position of the center point 40C) in the plane. The radius from the central axis and the radius difference between the tip and the base (the position of the center point 40A) are the same.

The blade 61 shown in FIG. 13 (a) corresponds to the blade 33 in the pump P1 of the present invention, and is centered from the tip end (the position of the center point 40C) of the blade 61. In a region having a large radius from the center of rotation to the position of center 40B, a line 40C-4OB connecting the center point 40 of the width in the circumferential direction of the blade 61 is connected to the center of rotation. And the blade in an area with a small radius from the center of rotation from the center of the blade 61 to the base (the position of the center point 40A) to match the radius line 60 connecting the center point 40C with the center point 40C. The line 40B-40A which connects the center point 40 of the width | variety of the circumferential direction of 61 is made into the circular arc which contact | connects the said radius 60.

As a result, in FIG. 13 (a), the surface 30 located forward with respect to the rotation direction F of the impeller has a radius R (R = 3t) from the base of the blade 61 to the center. An arc appears, and a straight line appears from the center portion to the tip portion of the blade 61.

FIG. 13 (b) shows a blade 62 of a modification of the blade 61 shown in FIG. 13 (a). The blade 62 has a line 40C-40B connecting the center points 40C and 40B from the center portion (position of the center point 40B) to the tip portion (position of the center point 40C) in the direction of rotation of the impeller. With respect to F), it is set as the straight line corresponded with the straight line 66 which cross | intersects with respect to the said radial line 60 at the angle (theta) (theta) 5 degree | times.

13 (c) and 13 (d) show the blades 63 and 64 of the comparison pump, respectively.

In these blades 63 and 64, the center point 40A of the width direction at the base of each blade 63 and 64, and the center point 40C of the width direction in a front-end | tip part are center points 40B of the width direction of a center part. It is of the shape located forward with respect to the said rotation direction F by ().

The blade 63 shown in FIG. 13 (c) has a radius R in the area whose radius is smaller than the center of rotation axis in the outline of the surface 30 located forward with respect to the rotation direction F. FIG. A circular arc of (R = 3t)) is represented by a circular arc of radius R (R = 6t) in a region having a radius larger than the center of rotation. In addition, the blade 64 shown in FIG. 13 (d) has an outline of the surface 30 which is located forward with respect to the rotation direction F. The blade 64 has a radius R (R = 3t) in the entire area. It is indicated by an arc.

Fig. 13E shows the blade 65 of another comparison pump. The blade 65 has a center point 40 in the width direction of the blade 65 from the center portion (the position of the center point 40B) to the middle portion (the position indicated by the center point 40D) between the tip portion (the position of the center point 40C). The connecting line is located on the diameter line 60 connecting the center point 40A of the base and the rotation center axis, and the line connecting the center point 40D and the center point 40C of the distal end portion has an arc shape.

As a result, the contour of the front face 30 with respect to the rotation direction F of the blade 65 is a straight line parallel to the radial line 66 from the base to the middle part (the position of the center point 40D), From the intermediate portion to the tip portion is indicated by an arc of radius R; (R = 3t).

Figures 14 and 15 show the results of the comparative tests. FIG. 14 is a chart of P-Q characteristics showing the relationship between the discharge pressure P and the discharge amount Q of each pump provided for the test when the set voltages of the motors driving the pumps are 6 V, 8 V, and 12 V, respectively.

FIG. 15 is a chart of N-Q characteristics showing the relationship between the rotational speed N of the impeller and the discharge amount Q under the condition that the discharge pressure P is a constant value (284 kPa). In these diagrams, reference numerals 610, 620, 630, 640 and 650 are impellers with blades 61, 62, 63, 64 and 65 shown in Figs. 13 (a) and 13 (e), respectively. It is a characteristic line of the pump provided with.

As can be seen in these figures, the characteristic lines 610 and 620 of the embodiment pump of the present invention are approximately the same.

As is apparent from FIG. 14, in the embodiment pump of the present invention having an impeller with blades shown in FIG. 13 (a) and 13 (b), even when the set voltage is as low as 6V or 8V. The discharge pressure P which is stable and higher than the comparative example in the same discharge amount Q is obtained.

As is apparent from FIG. 15, in the embodiment pump of the present invention, the impeller has a stable rotation even in a region where the rotation speed is low, and the discharge amount Q at the same rotation speed N is higher than that of the comparative pump. low.

Claims (3)

A flat disc-shaped substrate which is rotatably supported by the shaft by the shaft and whose sides are rotated in a plane perpendicular to the axis, and a plurality of concave grooves formed on both sides of the peripheral edge portion at the peripheral edge portion thereof An impeller having blades positioned approximately radially with respect to the substrate between the concave grooves, and a flat inner wall formed in the housing and opposing flat both sides of the impeller substrate and a cylindrical shape opposite the tip edge of the blade. A friction regeneration pump comprising a pump chamber for accommodating an impeller therein and having a half moon-shaped groove wall surface for connecting an inner circumferential wall, the inner wall and an inner circumferential wall, and connecting an inlet and an outlet formed in the housing. Each blade formed in the impeller A surface located forward with respect to the rotational direction of the impeller is formed in a concave surface in the surface perpendicular to the rotational center axis, and the center point of the circumferential width of the blade in the surface perpendicular to the rotational center axis is And a region having a large radius from the central axis of rotation, said friction regenerative pump extending at least in a rearward direction with respect to the direction of rotation of said impeller than a region of small radius from said central axis of rotation. The center point of the width in the circumferential direction of each blade in the plane perpendicular to the rotation center axis of the impeller is radially passing through the rotation center axis in an area having a large radius from the rotation center axis. Friction regeneration pump, characterized in that located in the. 2. The blade of claim 1, wherein the center point of the width in the circumferential direction in the plane perpendicular to the center of rotation is gradually rearward with respect to the direction of rotation of the impeller as the radius from the center of rotation increases. Friction regeneration pump, characterized in that to extend.