JPS61223292A - Method of sealing vane bearing in vane pump - Google Patents

Abstract

PURPOSE:To enable a bearing seal to be easily mounted by caulking fixedly an elastic seal member between bores of vane holders at both ends of bearing row for journalling a vane and a fixed shaft. CONSTITUTION:An elastic seal member 43 provided between the bore of a bearing holder 29c and a boss 10 abuts against one end of an outer shell 33a of a roller bearing 33 for journalling a vane. And the seal member 43 is fixed by caulking the opening edge of the bore with a caulking blade. Also, the advance stroke (S) of the caulking blade is made larger than distance (p) between the opening surface of the bore and the end face of the seal member 43. Thus, the seal member can be fixed securely by a simple operation.

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a vane bearing sealing method in a vane pump for compressing fluid. □ ′〈Conventional technology〉 A cylindrical casing with a land portion sandwiched between the inner circumferential surface and an open suction boat & θ discharge boat, and Jfi1! A rotor in the form of an intersecting cylindrical cylinder is eccentrically and rotatably supported in the casing so that its outer circumferential surfaces face each other with a small gap in the ia wound part, and a fixed shaft coaxial with the casing is connected to the rotor via a bearing. a vane rotatably supported by the rotor and slidable on the inner circumferential surface of the casing through a slit cut in the peripheral wall of the rotor; A vane pump equipped with a sealing member is known, for example, from Japanese Utility Model Application Publication No. 52-35511.

In such a vane pump, the vane is
In order to rotatably support the vane support, the vane support is supported on a fixed shaft using a needle bearing or the like, but such a bearing needs to be lubricated with a lubricant such as grease. However, since the vane support rotates at high speed, it is recommended to provide a seal to prevent the am agent from scattering due to centrifugal force.
It is disclosed in the publication No.

However, in such a known seal structure, the elastic seal is built into the needle bearing, which complicates the manufacturing process and increases costs, and the grease deteriorates due to the heat generated by sliding contact between the seal and the needle holder. Inconveniences such as needle skew may occur.

<Problems to be solved by the invention> Therefore, it is possible to use a seal member separate from the bearing, but if the seal is simply press-fitted into the inner hole of the vane holder, the retaining force of the seal will decrease due to the elasticity of the seal. Since the pump cannot sufficiently increase the pressure, there is a risk that the seal may fall off while the pump is operating. However, when a fixing device such as a circlip is used to fix the seal member, there is a disadvantage that the number of parts increases and the manufacturing process becomes complicated.

In view of these drawbacks of the prior art, the main object of the present invention is to provide a suitable sealing method for a vane bearing of a vane pump.

According to the present invention, an annular elastic seal member is provided in a gap between the inner hole and the fixed shaft adjacent to both ends of the rolling bearing. The process of fitting, concentrically with the inner hole! A notch is formed on the outer periphery of the opening of the inner hole by a caulking blade arranged in a shape φ, and the inner periphery of the opening of the inner hole is deformed radially inward due to the cut, thereby causing the elastic sheath member to holding it in the inner hole, and the depth of the cut is larger than the distance between the entrance part of the inner hole and the outward end surface of the elastic seal member. This is accomplished by providing a method for sealing a vane bearing in a vane pump.

In particular, it is preferable that the angle between the side end surface of the notch and the inner circumferential surface of the inner hole is in the range of 60@ to 90 degrees.

<Function> By caulking and fixing the elastic seal member with appropriate cutting depth and cutting angle in this manner, a reliable bearing seal can be easily realized.

<Embodiments> Preferred embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

1 and 2, a vane pump according to the invention is shown in its entirety.

An end IE 22 and a discharge chamber casing 3 are collinearly secured to the right open end in FIG. 1 of the cylindrical casing 1 with one end open, using bolts 4. Inside the casing 1 is a hollow cylindrical rotor R.
The center of rotation is received eccentrically by ε with respect to the center of the casing 1. The rotor R consists of a cylindrical member 5, a disk 6 whose left end in FIG. It consists of a disk 8 which is secured to the right end of the shaft by a bolt 9 and has an annular bearing boss 8a projecting outward.

The protruding shaft 6a is rotatably supported via a ball bearing 11 on a boss 10 provided on the end wall of the casing 1 opposite to the open end, and a retainer 12 is attached to the end surface of the boss 10 with a bolt 13 By fixing the ball bearing 11 using a screw, the ball bearing 11 is prevented from being removed in the axial direction. Further, at the end of the protruding shaft 6a, there is a pulley 15 that is prevented from rotating by a half-moon key 14.
is fitted, and is prevented from being removed via a flat washer 16 screwed onto the shaft end of the protruding shaft 6a with a bolt 17.

A belt 48 wound around the pulley 15 allows the rotor R to be rotationally driven using power transmitted from, for example, an engine.

A bearing post 8a provided on the disk 8 on the other end side of the R is rotatably supported via a ball bearing 18 by a bearing boss 2a provided inwardly protruding from the center of the end wall 2. . Ball bearing 18
A Teflon ring 19 is interposed between the inner race and the outer peripheral surface of the bearing boss 2a, so that the ball bearing 18 can be displaced along the axial direction to a certain extent without causing runout.

Inside the rotor R, a fixed vane shaft 20 extends concentrically with the inner circumferential surface of the casing. The portion 20a is fitted into an axial through hole 2b provided inside the bearing post 2a at the end '12 and concentrically with the casing, and has a threaded portion 21 that protrudes toward the discharge chamber casing 3 side of the small diameter portion 20a. A nut 23 is fastened through a washer 22 to fix the vane shaft 20 integrally to the center of the end wall 2. A crankshaft 20b is provided at the left end of the fixed vane shaft 20 in FIG. It is rotatably fitted and supported.

Three slits 25 are cut in the cylindrical member 5 of the rotor R along the axial direction at equal intervals in the circumferential direction, and each slit 25 has flat vanes 26 to 28 made of synthetic resin.
is inserted. The base end of each vane is fixed to the vane holders 29 to 31 with rivets 32. Each of the vane holders 29 to 31 is rotatably supported on the fixed vane shaft 20 via a needle bearing 33, and the axial position of each vane holder is determined by a thrust washer 34 sandwiched between each of the vane holders 29 to 31 at an appropriate position. It is being

Each vane holder 29-31 has a vane mounting portion 29a-3.
1a1 bearing holding parts 29b to 31b129C to 31C and counterweight parts 29d to 31d129e to 31e, the counterweight parts are disposed at diametrically symmetrical positions with respect to the corresponding vanes 26 to 28, and each rotating vane 26 ~28 static balances are taken.

Further, the vane holder 29 and the vane holder 30 are of the same shape, and each one of the counterweights 29
d and 30d are large, and the other counterweight 29e130d is small, and the respective bearings are arranged so that the large counterweight is located at the center in the axial direction, and the small counterweights are located at both ends in the axial direction. The holding parts 29b, 29c, 30b, and 30c are pivotally supported by the fixed vane shaft 20. Furthermore, the third vane holder 31 has two medium-sized counterweights 31d, 3.
1e, and each other vane holder 29.3
The bearing holding parts 31b, 31 are inserted between the large counterweight and the small counterweight.
C is pivotally supported by a fixed vane shaft 20. In this way, the weight of the counterweight is distributed symmetrically along the axial direction, and the vanes 26 to 28 are dynamically balanced.

FIG. 3 is a detailed perspective view of one of the three vane units. The needle bearing 33 is fitted into the inner hole 45 of the bearing holding portion 290, and elastic seal members 43 are fitted into the front and rear ends of the needle bearing 33. Hold the other bearing 1! A similar needle shaft and elastic seal member are fitted into the inner hole of $29b, but are not shown.

As clearly shown in FIG. 4, the needle bearing 33 is
An outer shell 33b formed by inwardly bending the end of a cylindrical metal plate, a plurality of needles 33a, and a device for receiving each needle so that the needles are maintained at a constant distance from each other and in the same posture. The wind shell 33c is a cylindrical body having a long hole. The elastic seal member 43 is made of a soft polymer material such as rubber,
It has an annular shape so as to fit into the gap between the outer circumference of the fixed shaft 20 and the inner circumferential surface of the inner hole 45 of the bearing holding part 29c. The main body portion 43a of the elastic seal member 43 adjacent to the inner circumferential surface of the inner hole 45 has a ring-shaped core metal 44 embedded therein and is in close contact with the inner circumferential surface of the inner hole 45. Elastic seal member 4
The inner peripheral part adjacent to the outer peripheral surface of the fixed shaft 20 of No. 3 is the lip part 4.
3b, and is in sliding contact with the outer circumferential surface of the fixed shaft 20 or facing it with a minute gap maintained.

The needle bearing 33 is connected to the outer periphery of the fixed shaft 20 and the inner hole 6.
Although the elastic seal member 43 is precisely fitted onto the inner circumferential surface of the pump 45 and is unlikely to fall off, there is a risk that the elastic seal member 43 may fall off during operation of the pump if left as is. Therefore, according to the present invention, the bearing holding portion 29
The end face adjacent to the opening of the inner hole 45 of c is caulked radially inward to prevent the elastic seal member 43 from falling off.

FIG. 5 shows how to perform the above-mentioned crimping using the crimping jig 50. This caulking jig 50 includes a blade 5 provided annularly along the outer periphery of the opening of the bearing holding portion 29c.
1, and a first guide portion 52 that protrudes into the inner hole of the needle bearing 33 and guides the caulking jig 50 along the axial direction.
, a second guide part 53 that determines the fixed position of the elastic seal member 43 in the inner hole 45, and a third guide part that comes into contact with the end surface of the bearing holding part 29G to determine the plunge depth of the blade 51. 54.

By simultaneously pressing the crimping jig 50 against one bearing holding part 29c from the left and right directions with a force of about 1.5 tons, the bearing holding part 29G is pressed against the bearing holding part 29c as shown in FIGS. 6 and 7. Depth of cut 4 around the entire circumference of the opening end surface
6 is provided so that a part of the member of the bearing holding portion 29C, that is, the deformed portion 47 is pressed against the elastic seal member 43. Since an annular core bar 44 is embedded in the elastic seal member 43 along its circumferential direction, the elastic seal member 43
is firmly fixed.

In order to realize the above, for example, the bearing holding part 29
If the inner diameter of the inner hole 45 of c is 21 mg+, the inner hole 45
The thickness tl between the inner peripheral surface of the metal core 44 and the opposing surface of the core metal 44 is 0.5.
It is best to keep it below 100 yen. Further, the thickness t2 of the elastic seal member 43 on the surface facing the opening side of the core bar 44 is preferably about 0.2 wm. Further, the immersion depth p from the open end of the inner hole 45 of the elastic sealing member 43 is 0.351111, and the distance from the axis of the fixed shaft 20 of the blade 51 of the caulking jig 50, that is, the blade 5
If the difference q between the radius of the first tip position and the radius of the inner hole 45 of the bearing holding part 29C is F12.0m+, then it is good≦, and the blade 51
．． One person's stroke speed is approximately 0. ．． 3m - 0.4 rin! That's good. Generally, if S is too large, the pressing force required for caulking will be large, and even the portion of the inner hole 45 that receives the needle bearing 33 will be deformed.If S is too small, the elastic seal member 43 will be damaged. Holding force becomes insufficient.

At this time, if the cutting edge angle θ of the blade 51 is 80°, the deformed portion 4
The radially inner end of 7 is approximately 0.2 as from the radius of the inner hole 45.
Displaced inward, the resistance force against the pulling direction of the elastic seal member 43 is 20Kg to 30Ky when the opening is chamfered by approximately 0.5mm+C, and approximately 20Kg when the opening is chamfered only. 40Kg was obtained. For example, when the cutting edge angle θ is 60°, the bearing holding part 29
In some cases, inconveniences such as cracks appearing in c and deformation of the outer shells 33 and b of the needle bearing 33 may occur, and such inconveniences should not occur if θ is set to 80°. Depending on other conditions, θ is generally 60°
It is preferable that θ≦90′.

What is important here is that the protruding position of the tip of the blade 51 be deeper than the outward end surface of the elastic seal member 43. By doing so, the cut and raised portion 47 is reliably pressed against the elastic seal member 43, and the required seal holding force is ensured. In the above embodiment as well, the intrusion stroke S of the blade 51 is approximately 0.3 to 0.4.
m, whereas the distance p from the opening of the inner hole 45 to the outward end surface of the elastic sealing member 43 is 0.3. Since he is Maro, we can see that these conditions are met.

The blades 51 of the caulking jig 50 may be formed in an annular shape along the entire circumference as in the above embodiment, or at equal intervals as shown in FIG. For example, it may be divided into six parts tJ≧.

Now, as clearly shown in FIG. 2, the portion of the cylindrical member 5 facing each slit 25 is a thick walled portion 5d, and the opposing surface that defines the slit 25 has a thick wall portion 5d extending over the entire length of the slit. Axial grooves 35a, 35b are recessed, and carbon shoes 36, 37 are fitted into each groove so as to partially protrude from the grooves 35a, 35b. A leaf spring 38 is provided between the bottom of the groove 34 on the front side in the rotational direction of the rotor R and the bottom of the carbon shoe 36.
are sandwiched between the vanes 26 to 28 elastically by the two force-bonshoes 36 and 37 to seal between the inside and outside of the rotor R.

The inner circumferential surface of the casing is generally circular with the same radius, and the land portion 41 located between the suction boat 39 and the discharge boat 40 that open toward the inner circumferential surface has an O-ta R.
As shown in FIG. Also, an imagination I showing the outline of the inner circumferential surface of the casing 1! 42
It is offset radially outward. Therefore, as the rotor R rotates, the tips of the vanes 26 to 28 rotate while slidingly contacting the inner peripheral surface of the casing 1.
1, the tip of each vane 26 to 28 should be recessed inward from the outer circumferential surface of the cylindrical member 5 of the 0-taR and come into sliding contact with the land portion 41.

Next, the operation of the vane pump of this embodiment will be explained.

Rotational force from an engine or the like is transmitted via the belt 46, and the rotor R is rotated in the direction indicated by the arrow in FIG. At this time, since there is an eccentric amount ε between the vane shaft 20 and the rotating shaft of the rotor R, the eccentricity ε is defined by the outer circumferential surface of the rotor R, the inner circumferential surface of the casing 1, and the vanes 26 to 28. The empty space near the suction boat 39 is small as shown by A, but gradually increases as shown by B as the rotor R rotates. In this way, fluid is sucked in from the suction boat 39, and as the 0-ta R rotates, the volume of the empty chamber is gradually reduced as shown by C, and the fluid is compressed and transferred from the discharge boat 40 to the discharge chamber E. This discharge chamber E functions as a surge tank that absorbs the pulsation of the discharge pressure of the pump.1 As described above, according to the present invention, the bearing of the vane can be fixed without increasing the number of parts. This makes it possible to easily and effectively fix the elastic sealing member for use.Therefore, the manufacturing and assembly process does not become complicated.
Moreover, it can be manufactured without increasing the manufacturing cost. □ FIG. 1 is a longitudinal sectional view showing an embodiment of the base 0-n bomb according to the present invention.

FIG. 2 is a sectional view taken along line If-I in FIG. 1.

FIG. 3 is an exploded perspective view showing one of the vane units in the embodiment shown in FIGS. 1 and 2. FIG.

FIG. 4 is a detailed sectional view of the needle bearing shown in FIGS. 1 to 3.

FIG. 5 is an explanatory view showing the process of fixing the sealing member of the needle bearing by caulking i.

FIG. 6 is a sectional view showing in detail the nose crimping fixing bridge structure for the elastic seal member.

FIGS. 7 and 8 are partial end views of the bearing holding portion of the vane holder showing the caulking position.

1...K? 2... End wall 2a... Bearing boss 2b... Hole 3... Discharge chamber casing 4.
...Bolt 5...Cylindrical member 5a...Thin wall portions 5b, 5c...Inward flange 5d...Thick wall FiS 5e, 5f...Annular protrusion 6...Disc 6a...Protrusion Axis 6b...
・Hole 7...Bolt 8...Disc
8a... Bearing boss 8b... Annular protrusion 8C
,8d...Annular groove 9...Bolt 10...
・Boss 11... Ball bearing 12... Retainer 1
3...Bolt 14...Half-moon key 15...
Pulley 16 shaft/washer 17... bolt
18... Ball bearing 19... Teflon ring 20.
...Vane shaft 20a...Small diameter part 20b-...
Crankshaft 21...Threaded part 22...Washer 23...Nut 24...Needle bearing 25...Slit 26-28-...Vane 29
~31...Vane holder 29a~31a...Vane mounting portion 29b~31b129c~31c...Bearing holding portion 29
d ~ 31d, 29e ~ 31e... Counterweight 32... Rivet 33... Needle bearing 33
a-7 Utashi XjLt33b-Knee, -Dollar 33c・
... Wind shell 34 ... Thrust washers 35a, 35b ... Grooves 36, 37 ... Carbon shoe 38 ... Leaf spring 39 ... Suction boat 40.
...Discharge boat 41...Land portion 42...Outline 1i 43...Elastic seal member 44...Core metal 45...Inner hole 46...Notch
47...Deformed part 48...Belt 50...
・Caulking jig 51...Blades 52-54...
・Guide Department Patent applicant Honda Motor Co., Ltd. Representative Patent attorney Dai
Shima Yo - Figure 2 Figure 7 Figure 8

Claims (2)

[Claims] (1) A hollow space having a cylindrical casing with a suction port and a discharge port opened on its inner circumferential surface, and an outer circumferential surface facing the inner circumferential surface of the casing, and eccentrically and rotatably supported within the casing. a cylindrical rotor; a vane support having an inner hole rotatably supported via a rolling bearing on a fixed shaft coaxial with the casing; A vane pump comprising: a vane attached to the vane support so as to be slidable on the inner circumferential surface of the casing; and a seal member provided on the inner facing surface of the slit so as to come into contact with the vane. A vane bearing sealing method comprising the steps of: fitting an annular elastic seal member into a gap between the inner hole adjacent to both ends of the rolling bearing and the fixed shaft; and fitting an annular elastic seal member concentrically with the inner hole. A notch is formed in the outer periphery of the opening of the inner hole by an annularly disposed caulking blade, and the inner periphery of the opening of the inner hole is deformed radially inward due to the notch, thereby causing the elastic seal member to holding the elastic seal member in an inner hole, and the depth of the cut is greater than the distance between the opening of the inner hole and the outward end surface of the elastic seal member. Vane bearing sealing method. (2) The vane bearing sealing method according to claim 1, wherein the angle of the cut-side end face with respect to the inner peripheral surface of the inner hole is in a range of 60° to 90°.