JPS627988A - Vane pump - Google Patents

Abstract

PURPOSE:To safely and easily send the transported substance without generating pulsation by making the sectional area of an operating chamber constant in the course where a vane is slipped off from a fluid suction hole and set into a discharge hole. CONSTITUTION:A vane groove 13 which crosses at right angles at the axis center with a rotor 12 supported by a rotary main shaft 31 and an auxiliary rotary shaft 14 is formed inside a casing 11. A vane 14 which is slidable in the direction of the rotor diameter is inserted into the vane groove 13. A flow passage 20 in the casing 11 is formed so that the sectional area is made constant in the course where the vane 14 is slipped off from a fluid suction hole 15 and set into a fluid discharge hole 16, onto the outer periphery of the rotor 12. Therefore, the transported substance is not compressed in the flow passage 20, and the substance can be sent safely and easily. Therefore, the generation of pulsation due to compression can be prevented.

Description

[Detailed description of the invention] Industrial applications The present invention relates to improvements in vane pumps.

BACKGROUND ART A conventional vane pump rotates an eccentric rotor in a casing having a circular inner wall surface, and a vane having a length equal to the diameter of the inner wall surface of the casing is attached to the rotor. The vanes were set to slide in the radial direction of the rotor as the rotor rotates to apply pressure to the fluid in the flow path. Furthermore, in conventional pumps, the casing and liner are integrally formed.

Problems to be Solved by the Invention According to the above-mentioned conventional technology, the fluid flow path formed by the gap between the inner wall surface of the casing where the pressure is applied and the outer peripheral surface of the rotor flows from the vicinity of the suction hole to the discharge hole. Until then, the capacitance changes. Therefore, the pressure of the fluid changes with this change in volume, and the compression and expansion actions are repeated. For this reason, not only pulsation occurs in the fluid sent out from the discharge hole, but when the fluid to be sent is a tangible material, it is easily compressed and damaged.

In addition, in recent years, there has been a demand for larger pumps, and there is a strong desire for larger rotors.
The ninth rotor that was installed in combination had to be a cantilevered rotor, and there was a limit to how large a cantilevered rotor could be made. In order to make the rotor double-sided for reinforcement purposes, it was necessary to use a single vane that could be inserted from the side of the rotor. Furthermore, when manufacturing a conventional large pump in which the casing and liner are integrally formed, an extremely large processing machine must be used, which poses the problem of being cumbersome to operate and extremely high processing costs. There was also.

The present invention solves the above-mentioned problems, does not cause pulsation even if it is large, can be operated at high speed, does not damage the material to be sent, and
The purpose of the present invention is to provide a vane pump that can be easily and safely delivered at a low cost.

Rounding Means for Solving Problems The present invention is a vane pump having two vanes, in which an auxiliary shaft is connected to the opposite side of the main shaft of the rotor in order to eliminate pulsation and increase the size of the rotor to prevent vibration. The rotor is supported from both sides, and two vanes can be inserted and removed, successfully increasing the size and speed of the pump.

The configuration of the present invention is as follows.

In other words, in a vane pump having two orthogonal vanes, the rotor is rotatably disposed within a casing and has vane grooves that are perpendicular to each other at the axial center. The rotor is capable of being inserted and removed from the opposite side of the rotor, and is slidable along the rotor's radial direction, and an auxiliary rotation shaft is fixed to the opposite side of the rotor's main rotation axis,
The flow path in the casing is set to have the same cross-sectional area on the outer periphery of the rotor from the fluid suction hole to the fluid discharge hole.

As the rotor rotates, the fluid sucked in from the fluid suction hole is pressurized by the vanes sliding in the grooves and sent out from the fluid discharge hole through the gap passage between the inner wall surface of the liner and the outer peripheral surface of the rotor. It will be done.

Example The present invention will be explained below based on embodiments shown in the drawings.

As shown in FIG. 1, the vane pump of the present invention includes a pump body 10 containing a rotor 12, a drive section 80 for imparting rotation to the rotor 12, and a reinforcing section 40 for increasing the rotation resistance of the rotor 12. .

In FIGS. 1 to 8, the pump body 10 is the base 1.
An upwardly facing fluid intake hole 15 and a sideways fluid outlet 16
A casing 11 is integrally formed, and the casing 1
A flow path 20 for the fluid to be conveyed is provided in the inside of the tank 1 via a liner 17 .

A rotor 12 with a horizontal axis is provided in the flow path.
A portion (174 circumferential areas) is provided adjacent to the liner 17. In this 1 part 4 circumferential area,
The rotor 12 and the inner circumferential surface 21 of the liner 17 are coaxial and set in circular arcs with different radii.

The liner 17 is separate from the casing 11, is cut using a machining center, is fitted into the casing 11, and is fixed by a liner fixing key 18.

The rotor 12 has a vane groove 18.18 perpendicular to its axis.
are provided, and two Fi sheets (7) vane 1 are provided in these vane grooves.
4.14 are orthogonal to each other and are assembled in a muntin-like manner. As shown in FIG. 8, both vanes are configured to be slidable relative to each other along the rotor radial direction.

Thus, on the outer periphery of the rotor 12, both 1111 portions 4 sandwich the coaxial section between the rotor and the liner inner circumferential surface 21.
The circumferential areas each have fluid suction holes 1 towards these areas.
5 and a fluid discharge hole 16 are opened. Then, the remaining 1 part 4 circumferential sections, that is, symmetrical side sections sandwiching the rotor axis with respect to the # period coaxial section, and the rotation direction R of the rotor 12
- Remove the fluid suction hole 15 along the -fluid discharge hole 16
The area up to is also considered a coaxial area.

In the latter coaxial area, the radius of the liner inner circumferential surface 21 is set larger than that of the former coaxial area, and the inner circumferential surface 21 and the rotor 1
2 and the same cross section Im (A=B=C in Fig. 2)
) is the flow path 20.

The curve of the inner circumferential surface 21 of the liner in the area where the fluid suction hole 15 and the fluid discharge hole 16 are opened, excluding the hole portions, is determined as follows.

That is, in FIG. 4, when the axial center of the rotor 12 is P, and points A, B, C, and D are the ends of the coaxial area passing through the axial center P, first, the distance between P and P is (PA+PB). ) No. 1
Find a point equal to /2 on the bisector of angle APB and define it as point E. Next is AE.

If we connect BB and draw perpendicular lines pointing toward the center of the liner from the respective center points F and G, and let the point where both perpendicular lines intersect be O, then O becomes the center point of the liner.

Therefore, draw an arc passing through E with 0 as the axis, and then O
By drawing the same arc on the symmetric side of , the curve AEBCD can be obtained. Therefore, a surface including the curve and extending in the width direction of the rotor 120 becomes the inner peripheral surface 21 of the liner 17.

The drive unit 30 includes a rotating main shaft 31 assembled by fitting a female connecting portion 31a into a female connecting portion 12a protruding from one end of the rotor 12 (right side in FIG. 1), and the casing 1.
1 and a drive/1 housing 82 that is assembled and fixed to the housing bolt 86 via a housing bolt 86. The rotating main shaft aiIfi drive housing 82 is supported by the bearing 3B and sealed by the ground backing 34. Rotating main shaft 31
and rotor 12 are prevented from rotating by a main shaft key 35. The rotating main shaft 31 is driven by a motor (not shown) via a reduction gear or the like. In FIG. 1, 37 is a backing press gland and 38 is a bear link cover.

The reinforcing portion 40 is provided on the other side (left side in FIG. 1) of the pump stopper 10. The reinforcing part 40Fi is attached to the other side of the rotor 12 via the assembly port 2, and includes a rotation auxiliary shaft 41 fixed to the other side of the rotor 12 and an auxiliary housing 42 assembled to the casing 11 with housing bolts 46, and the driving part 8
0, it includes a bearing 4B, a gland backing 44, a backing presser gland 47, and a bearing cover 48. The rotor 12 and the rotation auxiliary shaft 41 are assembled in advance by attaching two vanes to the rotor 12, and then abutting the side surface on which the rotation auxiliary shaft 410 is attached to the other side of the rotor 12, as shown in Figure 8. The bolt 2 is screwed into the provided bolt hole 19.45 and tightened and fixed. After this assembly is completed, the auxiliary housing 42 is attached.

L, (When the upper vane pump is started and the rotor 12 rotates, the two vanes 14.14 are inserted into their respective vane grooves 1B.
, 1B while rotating in the rotor radial direction with both end surfaces in contact with the inner circumferential surface 21 of the liner in the casing, and the flow path 20
Pressure is applied to the fluid within the fluid discharge hole 16, and the fluid is delivered through the fluid discharge hole 16. During this operation, since the flow path from the fluid suction hole 15 to just before the fluid discharge hole 16 is formed to have the same cross-sectional area, a constant compressive force is continuously applied to the fluid. As a result, fluid pulsation may occur,
Cannot be damaged. Further, since the rotor is of a double-sided type with the other side also supported by the rotation auxiliary shaft, vibrations are suppressed even in the case of high-speed rotation or a large pump.

According to the present invention, the liner 17 is manufactured separately from the casing and assembled, so it can be easily manufactured using a small processing machine. Therefore, not only the cost of the pump as a whole is reduced, but also the liner 17 can be replaced when worn, making maintenance such as overhaul easy.

Effects of the Invention As described above, the present invention provides a vane bonnet 1 having two orthogonal vanes, in which the rotor is provided with vane grooves that are perpendicular to each other at the axis of the rotor, and each vane has a groove on the other side along the rotor axis. The vanes are slidable along the radial direction of the rotor, a rotation auxiliary shaft is fixed to the other side of the rotor, and the flow path inside the casing is inserted into and removed from the fluid suction hole at the outer periphery of the rotor. Since the area up to the fluid discharge hole is formed into a membrane chamber with the same cross-sectional area, there is no variation in the pressurizing force within the flow path. Therefore, pulsation does not occur in the fluid to be fed, and there is no damage even when feeding a tangible material.

In addition, even pumps using two vanes could be made faster and larger, making stable and smooth feeding possible.

[Brief explanation of drawings]

Fig. 1 is a longitudinal sectional view showing one embodiment of the present invention, Fig. 2 is a longitudinal sectional side view of the pump body, Fig. 8 is an exploded perspective view of the main part, and Fig. 4 is a longitudinal sectional view showing an embodiment of the present invention.
The figure is an explanatory diagram of how to obtain the inner circumferential surface of the liner. 10... Pump body, ll... Casing, 12...
... Rotor, 14... Vane, 15... Fluid suction hole, 16... Fluid discharge hole, 17... Liner, 20...
Channel, 80... Drive unit, 31... Rotating main shaft, 82...
... Drive housing, 40... Reinforcement part, 41... Rotation auxiliary shaft, 42... Auxiliary housing

Claims (2)

[Claims] (1) In a pump with two orthogonal vanes,
The rotor 12 is rotatably arranged within the casing 11,
It is provided with vane grooves 13, 13 that are perpendicular to each other at the axis, and the respective vanes 14, 14 can be inserted into and removed from the opposite side of the rotating main shaft 31 along the rotor axis, and
The rotor is slidable along the radial direction, and an auxiliary rotation shaft 41 is fixed to the side opposite to the main rotation axis of the rotor. A vane pump characterized in that the area up to the fluid discharge hole 16 is set to have the same cross-sectional area. (2) The vane pump according to claim 1, wherein the casing 11 has a separate liner 17 fitted and fixed therein.