JPS59160085A - Vane pump - Google Patents

Abstract

PURPOSE:To secure the balance of pressures as well as the lubrication of both side surfaces of the vane by providing recesses, communicated with a pressure introducing port, on both side surfaces of the vane. CONSTITUTION:When the output shaft 37 of a motor is rotated, a shaft 15 and a rotary body 16 are rotated and the vane 19, inserted into a groove 17, is rotated under abutting against a cam surface 10. The side surfaces of the vane 19 are provided with the recesses 50 and the pressure introducing port 18 is communicated with the recesses 50 through paths 51. According to this method, pressure variation may be relieved by the recesses 50 and the pressures of a pair of recesses 50 become equal to the same of the pressure introducing port 18 by the paths 51, therefore, the balance of the pressure may be kept. Further, the function of static bearing may be expected by supplying the high pressure of the pressure introducing port 18 into the recesses 50.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is a vane pump having a flexible side plate and a mechanism for controlling rotor side clearance. The problem is that conventional vane pumps of this type have flexible side plates, and for example, the pump discharge pressure is introduced into the outer surface of the side plate, and the side plate is configured so that it twists toward the rotor in response to the pump pressure. was.

According to this configuration, the rotor side clear radius, which has an important relationship with f/p performance, is automatically adjusted according to the pump pressure, resulting in high pump efficiency. It was inevitable that the deflection would be uneven due to the pressure distribution inside the pump, the support conditions of the side plate, etc. As a result, the rotor side clearance varies from place to place during rotation of the rotor, resulting in non-uniform forces being generated in the side direction on the blades sliding in the grooves of the rotating body of the rotor.

Due to this unbalanced force in the side direction, the blades protrude from the grooves of the rotating body and rotate while coming into contact with the side plates, causing wear on the blades.

Technical Problem of the Invention The technical problem of the present invention is to eliminate the influence of force in the side direction on the blade (for example, pressure acting on the side surface of the blade), which occurs because the deflection of the side plate is uneven depending on the location. be.

Technical Means of the Invention In order to solve this problem, the present invention provides four parts on both sides of the blade to alleviate the effects of sudden pressure rises and drops, and also communicates the pair of recesses with the pressure introduction port. Measures were taken to ensure pressure balance and lubrication of the blade sides.

DESCRIPTION OF THE EMBODIMENTS An embodiment of the vane pump according to the present invention is shown in FIGS. 1-7.

In the figure, a pump case 1 has a pump part storage space 2 and a magnet storage space 3 for torque transmission inside.
The rain space communicates with the pump case 1. The pump case 1 is further provided with an inlet 4 and an outlet 6 so as to communicate with the pump storage space 2. The pump storage space 2 has a discharge port 6.
It has a V cut 6b in the axial direction at the position, which communicates with the magnet storage space 3.

The side plate 6 is made of a resin molded product in which a main bearing 7 and a member 8 having a terminal surface are integrally molded, and is flexible, so that it can be inserted into the pump housing space 2.

An eccentric ring 9 is inserted between the pair of side plates 6.

The eccentric ring 9 has an outer diameter and an eccentric inner diameter, and this inner diameter forms the cam surface 1o. Eccentricity/g9 is notched 11.
12, and these cutouts constitute flow passages communicating with the suction port 4 and the discharge port 6, respectively.

The cam surface 10 between the cutouts 11, 12 becomes the pump actuating cam surface 13.

The rotor 14 is held between a pair of side plates 6 so as to freely rotate on a main bearing 7. In this rotor 14, a shaft 16 and a rotating body 16 are fixed as one body, and blades 19 having pressure introduction ports 18 inside are inserted into grooves 17 of the rotating body 16 so as to be freely retractable.

Among the spaces surrounded by the pair of side plates 6, the eccentric ring 9, and the rotor 14, the space corresponding to the pump operating cam surface 13, which is the section where the pump action is performed, becomes the pump 1 operating chamber 20.

The outer diameters of the side plate 6 and the eccentric ring 9 are set in a dimension relationship such that they fit with the inner diameter of the pump housing space 2 with almost no clearance, and the axial width of the rotating body 16 is slightly smaller than the width of the eccentric ring 9. It is set so that it becomes smaller.

The pump housing space 2 of the pump case 1 is closed with a lid 21, and the outer surface of the side plate 6 forms a space A22.

The magnet storage space 3 is closed with a seal plate 23 made of non-magnetic material, and a driven magnet 24'f is inside.
have.

Driven magnet 24 is magnet 26 and yoke plate 26
is integrally molded with the case 27. A cut-shaped hole 28 is provided in the center of the case 27, and the D of the shaft 15 is
It fits into the cut portion 15a and transmits the torque transmitted to the driven magnet 24 to the shaft 16.Furthermore, an end bearing 29 is inserted into the recessed portion 2a& of the case 27, allowing the driven magnet 24 to rotate freely on the seal plate 23. Hold. Since the inner diameter of the magnet storage space 3 is set to be larger than the outer diameter of the driven magnet 24, the driven magnet 24 can freely rotate within the magnet storage space 3.

Assemble the above parts as follows. First, one of the side plates 6 is inserted into the pump housing space 2, and then the eccentric ring 9 is inserted with its notches 11 and 12 aligned in the same direction as the suction port 4 and the discharge port 6, respectively. Furthermore, axis 1
5 into the main bearing 7 so that 15& is on the magnet storage space 3 side.

The blades 19 and the springs 19 & are inserted into the grooves 17 of the rotary body 16, respectively, and the other side plate 6 is inserted overlapping the eccentric ring 9. Place the spring 3o for fixing the side plate on the previous side plate 6, then insert the O-ring 31 into the groove 32, and then close the lid 2.
1 is fixed with screws 33 while pressing the spring field and Osu/Gug 31.

The driven magnet 24 is attached to the shaft 16 in the magnet storage space 3.
0 cut) 15a and insert it together with the end bearing 2.
9 into the recess 26 of the case 27, then insert the O ring groove 3.
Insert the O-ring 31' into 2' and fix the seal plate 23 with screws (not shown).The assembly of the pump is completed as described above.The motor 34 is fixed with the flange 36 and the screws 36. At the same time, a drive magnet 38 is fixed to the motor output shaft 37 via a yoke plate 39.

The operation will be explained below. When the motor output shaft 37 is rotated, the drive magnet 38 rotates, and this rotational torque is transmitted to the magnetically coupled driven magnet 24. When the driven magnet 24 rotates, the shaft 16 and the rotating body 16 rotate via the O-cutter 16a, and the blade 19 inserted into the groove 17 is caught by the biasing force and centrifugal force of the spring 19a.
It rotates while contacting the cam surface 1o.

The volume of the space constituted by the pump operating cam surface 13, the rotating body 16, and the vane 19 is continuously changed by t'c, and the pump action is performed by this volume change.

Furthermore, a V provided at the position of the discharge port 6 of the pump storage space 2
The operation of cut 5b will be described. This V cut 6b is
Introducing the discharge pressure of the pump into the space A22 and the magnet storage space 3 to apply forced lubrication to the main bearing 7,
It works to ensure the life of the bearing.

Furthermore, the pump discharge pressure is introduced to the side plate outer edge 6b by this V cut 6b, and a pressure difference is generated between the side plate outer edge 6b and the side plate inner edge 6C. Since the pressure on the side plate outer edge 6b side is higher, the side plate 6 is on the side plate inner edge 6C side, that is, the rotating body 16
It deflects to the side, and the a-ta side clearance becomes smaller.

Since the smaller the rotor side clearance, the higher the volumetric efficiency becomes, this mechanism can compensate for a decrease in volumetric efficiency due to an increase in pump pressure.

By the way, the pressure on the side plate outer edge 6b side is constant and equal to the pump discharge pressure, but the pressure on the side plate inner edge 6b side has a distribution, and therefore the amount of deflection changes depending on the location.
The clearance (hereinafter referred to as R8) between the rotating body 16 of the a-mount 14 and the inner edge 60 of the side plate changes locally. To state this more specifically, the pressure inside the pump is low on the side of the suction port 4, which is almost equal to the suction pressure, and is pressurized when it enters the area of the pump working chamber 20, so the pressure is increased. The pressure continues to increase and reaches the maximum pressure on the discharge port 6 side.

The change in 7 at this time changes depending on the boundary shape of the eccentric ring 9, but basically, as shown in FIG. On the pump discharge side, side plate outer edge 6b, side plate inner edge 6C
Since there is no pressure difference, the deformation of the side plate 6 is small and constant, so Rs is almost constant.

Here, attention will be paid to the clearance in the side direction (hereinafter referred to as Vs) between the blade 19 and the side plate 6. Vs is set in a dimensional relationship such that VB ) Rs so that the blade 19 can freely move in the groove 17 even when Rs becomes extremely small. Therefore, it is thought that the side plate 6 and the blade 19 do not rotate while being in pressure contact with each other, but wear marks are generally observed on the side surfaces of the blades in vane pumps having such a configuration.

It is thought that the mechanism of the occurrence of this wear mark has a large relationship with the change in R8 mentioned above. That is, in FIG. 6, the blades 19 are from positions B and C,
As we move from E to F, Rs increases, but since the gap constituting Rs is kept almost airtight, a negative pressure is generated, and the blade 19 protrudes from the groove 17. Become. Since the air gap constituting this Rs exists on both sides of the groove 17, if the rotor 14 always rotates at the center of the pair of side plates 6, the negative pressure generated on both sides of the blade 190 will be distributed evenly.
Although it is possible that the pressure balance is disrupted, a mechanism occurs in which the blade 19 protrudes from the groove 17 as the blade 19 moves from positions a and C to positions E and F. it is conceivable that.

Therefore, in this embodiment, a recess 6o is provided in the side surface of the blade 19, and the pressure inlet 18 and these four parts are connected to the passage 6o.
1 for communication.

According to the above configuration, pressure changes are alleviated by the cavity formed by the four parts 60, and the passage 51
1, the pressure in the pair of recesses 6Q becomes equal to the pressure in the pressure inlet 18, and the pressure balance is maintained.In addition, by supplying the high pressure in the pressure inlet 18 to the fourth part 6o, a hydrostatic bearing function is achieved. You can expect it.

Next, another embodiment of the present invention will be described with reference to FIG. In this embodiment, a recess 63 is provided on the side surface of the blade 19A, and this recess 63 is communicated with the pressure introduction port 18 through the bottom surface 53 of the blade 19A.

In this embodiment, the same effects as those of the previous embodiment can be obtained with a simpler configuration. Next, a third embodiment of the present invention will be described using FIG. 9.

In this embodiment, a recess 64 is provided on the side surface of the blade 19B, and this recess 54 is communicated with the pressure introduction port 18 through the upper surface 66 of the blade 19B.

In this embodiment, in addition to improving the pressure balance on both sides of the blade 19B as in the previous embodiment, the blade 19B
The fluid resistance caused by the piston action that occurs when moving along the recess 64 can be reduced by forming the recess 64 as a flow path.

Effects of the Invention The vane pump according to the present invention solves problems such as sideward movement of the vanes, reduced mobility, and wear caused by local differences in the side clearance between the flexible side plate and the rotating body. By providing recessed portions on the side surfaces and communicating these four portions with the pressure introduction ports provided in the blades, improvements are made in terms of pressure balance and lubricity.

[Brief explanation of drawings]

Fig. 1 is an exploded sectional view showing one embodiment of the vane pump according to the present invention, Fig. 2 is a top view of the vane pump with the lid and side plate removed, Fig. 3 is a top view of the vane pump, and Fig. 4 is a side sectional view of the same vane pump, and Figure 5 is C in Figure 2.
6 is an explanatory diagram of the deflection characteristics of the side plate of the same vane pump, 7 is a projection view showing the blade of the same vane pump and a sectional view of the same blade B-8, and 8 is a wooden Projection diagram of the blade according to Animonchi's example and 6 of the same blade
-8 sectional view and FIG. 9 are projection views of the vane according to the third embodiment of the Bay 7 pump according to the present invention. 6...Side plate, 9...Eccentric ring, 5b...
... Means for introducing discharge pressure (V cut), 16. Old... Rotating body, 17... Groove, 18... Pressure introduction port, 19° 19A, 19B.--- -・Feather, 50
, 53.54...-4 parts. Name of agent: Patent attorney Toshio Nakao and 1 other person 2nd
Figure 4 Figure 6 (8-) Figure 7, 3. t9 ///1 1'/ /σ lσI'/Figure 8 (oL) (b) Figure 9

Claims (1)

[Claims] a pair of flexible side plates, an eccentric ring held between the pair of O side plates, a means for introducing discharge pressure to the outer edge of the side plates, and a rotary member rotatably held between the pair of side plates. and a blade having a pressure introduction port slidably provided in a plurality of grooves of the rotating body, and a recess is provided in a part of the side surface of the blade facing the side plate, and A bed/pump 0 in which the recess and the pressure introduction port are communicated with each other.