JPS59221490A - Vane type air pump - Google Patents

Abstract

PURPOSE:To keep the rotary balance of the vane type air pump by a method wherein a plurality of cylindrical body, provided at the base ends of a vane with predetermined intervals, are provided with a balance weight projecting to the direction of opposite side of the vane so as to be bridged. CONSTITUTION:The base end side of the first vane 191 is fitted into the groove 22 of rod-like bifurcate part 21 of first holding member 201 and are secured thereto with a plurality of rivets 23. A pair of cylindrical bodies 241, 242, supported by a vane shaft 2 through needle bearings 25, are supported by the bifurcate part 21. The first balance weight W1, projecting to the direction opposite to the first vane 191, is bridged between both cylindrical bodies 241, 242 and is secured to the cylindrical bodies 241, 242 by small screws.

Description

[Detailed description of the invention] The present invention relates to a vane type air pump.

Conventionally, this type of air pump has a vane shaft whose axis line coincides with the center line of the cylindrical casing, and a cylindrical rotor which surrounds the vane shaft and whose rotational center line is eccentric with respect to the center line. A long hole is provided in the peripheral wall of the rotor parallel to the rotation center line, and the vane is passed through the long hole so that the tip of the vane slides on the inner peripheral surface of the casing as the rotor rotates. A plurality of cylindrical bodies provided at a predetermined interval at the base end of the vane are rotatably supported on the vane shaft via bearings, and seals are pressed against both sides of the vane, respectively, on the inner side of the ridge of the elongated hole. A device in which members are arranged is known.

In the above air pump, when the vanes rotate together with the rotor, a radial load is generated on the bearings of each cylindrical body relative to the vane shaft due to the centrifugal force of the vanes, and the durability of these bearings is impaired. In addition, when a needle bearing is used as a bearing, the radial load causes the needle roller to tilt, which not only impairs the durability of the needle bearing, but also causes a thrust load to be generated on the cylindrical body and therefore on the vane, causing the vane to become incline. One end face of the vane is pressed against the inner surface of the opposite end wall of the rotor, which causes a problem in that the end face of the vane is worn and the pump efficiency is reduced.

In view of the above, the present invention aims to improve the durability of each bearing by ensuring rotational balance of the vanes, and includes a plurality of cylindrical bodies bridged with balance weights protruding in the opposite direction to the vanes. be.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings. A vane shaft 2 whose axis line coincides with the center line of the cylindrical casing 1 is disposed inside the cylindrical casing 1, and one end of the shaft 2 is connected to one end of the vane shaft 2. The vane shaft 2 is fixed by screwing a bolt 6 that is fitted into a through hole 4 formed in the end wall 3 and passes through a contact plate 5 fixed to the outer surface of the end wall 3 to one end of the vane shaft 2.
is attached to the casing 1 so as to be non-rotatable and non-moveable in the axial direction.

Further, a cylindrical rotor 7 surrounding the vane shaft 2 is disposed within the casing 1, and one annular end wall 8 of the rotor 7
is rotatably supported by the boss portion 10 of the end wall 3 of the casing 1 via a bearing 9, and is rotatably supported by the boss portion 10 of the end wall 3 of the rotor 7.
A drive shaft portion 12 protruding from the casing 1 is rotatably supported by the other annular end wall 14 of the casing 1 via a bearing 13 . The drive shaft portion 12 is connected to the engine via a transmission mechanism (not shown).

The rotation center line of the rotor I is offset by ε from the center line of the casing 1 by +QI, so that a part of the outer circumferential surface of the rotor 7 is always in sliding contact with the inner circumferential surface of the casing 1. The other end 15 of the vane shaft 2 is formed into a crank shape, and the shaft end is connected to the bearing 1.
6 and is supported in a bearing hole 17 formed in the drive shaft portion 12 of the rotor 7 .

Three elongated holes 18 are formed at equal intervals in the circumferential wall of the rotor 70 in parallel with its rotation center line, and each elongated hole 18 has first to
Third vanes 191 to 193 penetrate therethrough. The base end side of the first vane 1910 is the first holding member 20. rod-shaped bifurcated portion 21 of
A pair of cylindrical bodies 24 are fitted into the grooves 22 and fixed by a plurality of rivets 23, and protrude from the bifurcated portion 21 at a predetermined interval. ．． 24. is rotatably supported on the vane shaft 2 via a needle bearing 25 as a bearing.

Second. Similarly, the third vanes 192 and 193 are the same as the second vanes. They are attached to the third holding members 20□ and 203, respectively,
Two sets of cylindrical bodies 24. ．． 24. and 24. .

246 are the second . Third holding member 20. ．． 2G.

belongs to

As shown in FIG. 4, the first holding member 20. One cylindrical body 2 of
4□ is arranged at one end of the silk 1 vane 191, and the other cylindrical body 24. is the first vane 19. It is arranged in the middle part of both cylindrical bodies 24. . ．． is biased by α to one edge of .

A first vane 19. A first balance weight W1 protruding in the opposite direction to the cylindrical body 24. ．． 2
42.

The attachment relationship between the third vane 193 and the third holding member 203 is as shown in FIG.
0. The mounting relationship is the same with that of the cylinders 24S and 2.
46, there is a third base protruding in the opposite direction to the third base 7193.
A balance weight W3 is fixed to 246.

As shown in FIG. 5, both cylindrical bodies 24 of the second holding member 202.
,2. ．． 4. The bisector line V-V, which is perpendicular to the axis of the vane shaft 2, coincides with the bisector Z-Z of the second vane 192, which is perpendicular to the axis of the vane shaft 2, and the two cylindrical bodies 24 ．． ，
A second balance weight W2 protruding in the opposite direction to the second vane 192 is bridged between 244 and fixed by a machine screw (not shown).

The first to third balance ways) Fi to W,
- The durability of each bearing 25 can be improved by ensuring the rotational balance of the third vane 191.19s. Also number 1. Third vane19. ．． At 193, one end is a cylindrical body 24. .

246 protrudes in the axial direction of the vane shaft 2, and is cantilevered from the cylindrical bodies 241, 24. Ryo1. Third vane19. .

When the vanes 19.193 rotate, centrifugal force causes the vanes 19. .

193 may tend to tilt and wear unevenly, but such a problem can be prevented by the third balance way) Fl p'3.

The tips of each vane 191 to 193 are recessed into the rotor 7 at the position where the rotor 7 makes sliding contact with the inner peripheral surface of the casing 1;
As the rotor 7 rotates, it protrudes from its outer peripheral surface and can slide on the inner peripheral surface of the casing 1.

A long groove 26 with openings facing each other is formed in the inner surface of each long hole 18 in the longitudinal direction of the long hole 18, and each long groove 26 has a groove 26 that is in pressure contact with the first to third vanes 191 to 193. 1. Second seal member 271 .

27□ is fitted. The bottom of each i-groove 26 and the first groove opposite thereto. Second seal member 27. ．． 272 There is a third
As shown in the figure, the corrugated first plate. Second spring 2B, 282
are respectively accommodated, and both springs 28. ．． Due to the elastic force of 282, both seal members 27. , 272 for each vane 19
．． ~193, thereby each vane 19
Each seal member 27 for 1 to 193. , 27□ is maintained.

An outlet 31 of the suction chamber 29 and an outlet 32 of the discharge chamber 300A are opened on the inner circumferential surface of the casing 1, with a land portion in sliding contact with the outer circumferential surface of the rotor 7 interposed therebetween. 33.
34 indicates the inlet of the suction chamber 29 and the outlet of the discharge chamber 30, which communicate with the suction boat and the discharge port, respectively.

The rotor 1 is driven by the engine and rotates in the direction of arrow α in FIG.
193 also rotates in the same direction, and the inner wall surfaces 35.
36 is formed on a plane including tangent lines X-X and )'-y passing through the entrance edge of each vane on the inner circumferential surface of the casing 1, respectively.

Further, the vane exit edge of the inlet 32 in the discharge chamber 30 has a protrusion 38 that continuously protrudes from the land side.
The protrusion 38 is provided with an arcuate surface 37 that bulges inward of the discharge chamber 30 .

Next, the operation of this embodiment will be explained. When the engine is operated and the air pump is driven, the rotor I moves to arrow a in Figure 2.
Accordingly, each vane 191 to 193 rotates in the direction of
1800 from the sliding contact part between the rotor I and the inner peripheral surface of the casing 1
While rotating, the length of the protrusion from the outer circumferential surface of the rotor 7 is gradually increased while slidingly contacting the inner circumferential surface of the casing 1, and then during 1800 rotations, the length of protrusion from the outer circumferential surface of the rotor 7 is gradually decreased while sliding into the inner circumferential surface of the casing 1. Slides on the circumferential surface. As a result, each of the vanes 191 to 193 sucks air from the outlet 31 of the suction chamber 29, conveys it, and then discharges it to the inlet 32 of the discharge chamber 30, thereby performing a pumping action.

Also, due to engine torque fluctuations, etc., each vane is 19° to 1
The inertial force of 93 is applied to the first spring 28. When the first seal member 271 bends and moves toward the first spring 28 , the elastic force of the second spring 2820 causes the second seal member 2 to bend.
7□ moves toward the first seal member 27°, thereby preventing a gap from being generated between each of the vanes 191 to 19° and the second seal member 272, thereby avoiding a decrease in pump efficiency.

Furthermore, the suction chamber 2
The air flows smoothly in the chambers 29 and 30, thereby suppressing the generation of turbulence and shock waves in both chambers 29 and 30, thereby reducing noise.

Furthermore, the arcuate surface 37 of the protrusion 38 at the outlet 32 of the discharge chamber 300A increases the flow rate of the air flowing along the surface 37 and lowers the pressure around the surface 31.
This makes it possible to efficiently draw air into the discharge chamber 3° without reducing the amount of air drawn into the rotor 1 and the land portion. Therefore, when the opening of each long hole 18 of the rotor 1 passes through the protrusion 38, the amount of air drawn into the inside thereof is reduced, so even if the opening of each long hole 18 passes through the land, the air inside the opening is reduced. The amount of high-pressure air is small, and the noise generated when it is discharged to the outlet 31 of the suction chamber 29 can be reduced.

As described above, according to the present invention, in the cylindrical casing,
A vane shaft whose axis line coincides with the center line of the vane shaft, and 7'JC
a cylindrical rotor that surrounds the vane axis and has a rotation center line eccentric with respect to the center line, and a long hole parallel to the rotation center line is provided in the peripheral wall of the rotor, and the long hole A plurality of cylindrical bodies provided at predetermined intervals at the base end of the vane are mounted on the vane shaft so that the vane passes through the vane and the vane tip slides on the inner circumferential surface of the casing as the rotor rotates. In a vane type air pump that is rotatably supported through a long hole and has seal members that press against both sides of the vane on both sides of a long hole, balance weights that protrude in the opposite direction from the vanes are attached to multiple cylindrical bodies. Since the bearings are cross-linked, it is possible to ensure the rotational balance of the vanes and improve the durability of each bearing.

Furthermore, by bridging the balance weight to the cylindrical bodies, the small space between the cylindrical bodies in the rotor can be used to provide a balance weight with appropriate heavy equipment, and the rigidity of each cylindrical body can be improved. .

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; Fig. 1 is a vertical sectional side view, Fig. 2 is a sectional view taken along the line ■-■ of Fig. 1, and Fig. 3 is a cross-sectional view of the
Figure III-[11 line sectional view, 4th. FIG. 5 is a perspective view of the vane. If', ~IV3...first to third balance weights,
DESCRIPTION OF SYMBOLS 1... Casing, 2... Vane shaft, 7... Rotor, 18... Long hole, 191-193... 1st - 3rd vane, 241-246... Cylindrical body , 25...bearing, 27. ．． 27□・・・1st. Second seal member patent applicant Honda Motor Co., Ltd. agent Patent attorney Ochiai

Claims (1)

[Claims] A vane shaft whose axis line coincides with the center line of the cylindrical casing, and a cylindrical rotor which surrounds the vane shaft and whose rotational center line is eccentric with respect to the center line are arranged in a cylindrical casing, A long hole parallel to the rotation center line is provided in the peripheral wall of the rotor, and a vane is passed through the long hole so that the tip of the vane slides on the inner peripheral surface of the casing as the rotor rotates. A plurality of cylindrical vane shafts provided at predetermined intervals at the base end of the vane are rotatably supported via bearings so that the vane shafts are rotatably supported on both inner sides of the elongated hole, respectively. What is claimed is: 1. A vane type air pump provided with a seal part that presses against a surface, characterized in that a plurality of the cylindrical bodies are bridged with balance weights that protrude in a direction opposite to the vanes.