JPS6184415A - Oil bearing structure with shaft seal - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] [Industrial Application Field 1] The present invention is directed to an elastic foil bearing structure having a shaft seal, and in particular, processes the front and cover of a single foil material to connect the bearing and the shaft seal. This relates to an integrated bearing structure that simplifies the bearing structure.

[Prior Art] Conventionally, a hydrodynamic fluid bearing with the ability to support a rotating shaft and a hydrodynamic shaft seal with folds that seal the rotating shaft in a non-contact manner differ in terms of their opening and design. It is a separate structure, and there is no unified structure yet. This is especially true when it comes to the foil @ receiver (1η structure), which was previously invented by the present invention.

[Problems to be solved by the invention] Conventionally, the bearing and the shaft seal were separate bodies, which increased the length of the rotating shaft in the axial direction, hindering weight reduction and reducing the rigidity of the rotating shaft. However, it was not possible to achieve sufficient speed and performance by 1q.

"Flower Mei's 1.1 target" The present invention integrates the bearing and the 1111 seal (IL L and small)
In addition to reducing weight, the rigidity of the rotating shaft has been increased to achieve even higher speeds and higher performance (Monkey Shaft Seal F").
This is to improve the bearing surface appearance.

[Summary of the Invention] The configuration of the present invention in accordance with the above-mentioned object is such that the receiving part and the shaft seal part are adjacent to each other in the width direction of a single piece of elastic foil material.
In order to install C, the longitudinal direction - Fl of the bearing part and seal part
A bearing foil or seal foil section, a dump foil section, and a sprinkler 71 (ru section) are provided in order in parallel and continuously to form an elastic foil body with a shaft seal, and this elastic foil body with a shaft seal is connected to the rotating shaft and the case. The bearing is wound in the above order between the bearing surface and laminated in three layers.Thereby, the bearing generates fluid film pressure to support the shaft load, while also sealing the shaft. The part can be elastically displaced to seal the shaft and
It is designed to have a low fA>, a stable shaft at high speed (high performance, and excellent shaft sealing performance).

[Example] An example of the present invention will be described below based on FIGS. 1 to 4.

As shown in FIGS. 2(A) and 2(D), the width direction of a piece of flexible elastic foil material is divided into a bearing part a and a shaft seal part A. The length direction is (
B) As shown in the same figure (B), which is a sectional view taken from the arrow, from the right, the bearing foil part [3a, dump foil part Qa,
When the spring foil portion Sa is also a shaft seal portion, as shown in FIG. -b, the dump foil portion Db1 and the spring foil portion sb are continuously formed. That is, by processing the front and back surfaces of a single sheet of foil material, an elastic foil body 1 is obtained in which the bearing part a and the shaft seal part A are integrally molded in parallel. The length of each part of this elastic film body 1 corresponds to the circumference of a cylinder that goes around the case supporting surface, which will be described later, and the width is set to be the length necessary for shaft support and shaft sealing.

Also, can you tell me the name of the appropriate interval in the length direction in the middle part in the width direction divided into the bearing part a and the shaft seal part? ! 2 ventilation holes 2
．． 2... is drilled, and the pressure at both ends of 1IiIll receiving part a (
Avoid equalizing the pressure in the width direction.

Bearing part A of bearing part a of 5'S divided in the width direction (
As shown in Figure 2 (D), the flat inner surface of the wall part Ba is a brane type with a flat inner surface as well as the outer surface shown in Figure 2 (A). It has been subjected to wear treatment. The form of the pairing twine part 3a is not limited to the illustrated example, but may be of any type, such as a spiral group, herringbone, step type, or pocket type. Also,
As shown in the drawing, the bearing ring 71 has a number of pressure release passages 3 at appropriate intervals in the length direction at the center in the width direction for stabilizing the bearing at high speed. This pressure release path 3 consists of a large-diameter pocket 4 bored on the outer surface 1111 and a small-diameter orifice 5 bored on the inner surface.
The pressure on the inner surface is transferred from orifice 5 to pocket 1.
~4 and release it with great force toward the outer surface.

The dump foil portion Oa and the spring foil portion 3a, which are continuous with the pairing twine delta coil portion 3a, are arranged on their outer surfaces across the entire length in the width direction and at an appropriate interval in the length direction (with a pitch even shorter than the pressure release path 3). A plurality of linear support protrusions 6, 6, . Dump foil part Da and spring foil part 3
The boundary with a is 1.5 times the pitch b of the support protrusions 6. The outer surface end of the spring foil portion 3a has a key 7 for locking and fixing. Thus, the spring foil portion 3a and the dump foil portion [)a have exactly the same shape except for the key 7.

On the other hand, the seal foil part Lb of the shaft seal part divided in the width direction is exemplified as a plain type with a flat inner surface like the bearing foil part Ba, and the substantial seal part is formed in the shaft seal part. In order to make it narrower than the overall length in the width direction, both ends are shaved to create a convex cross-section. The convex surface of this convex seal is subjected to an appropriate wear-resistant treatment.

Dump foil portion Db continuous to seal foil portion 1b
The spring foil portion sb has a ladder-like protrusion on its outer surface. That is, the shape is concave at a predetermined depth. ! 11, 8... at appropriate intervals in the direction? ! 2. The width of the self-portrait 92 to ensure the sealing property by forming the remaining part'), 'IO and y
A ladder-like protrusion is formed by the linear support protrusion 11 remaining between the 5-shaped four parts 8 and 8. The pitch of the linear support protrusions 11 at the top of this ladder-like protrusion becomes a spring T11 like the support protrusion O of the bearing part a, but it is set larger than the pitch of the support protrusions 6 of the bearing part a, so that it has a spring property. is set relatively low. In the illustrated example, it is set to twice that of the bearing part a. Note that, unlike the case of the bearing part a, the outer surface end of the spring foil sb of the shaft seal part 1) does not have a key that inhibits this in order to maintain sealing performance. The above-mentioned processing of the file surface can be carried out in one step using a known technique such as photo etching.

As shown in FIGS. 3 and 4, the elastic foil 1 formed from the single foil material described above is used in the bearing foil part Ba, the sealing foil part 1b1, and the sealing foil part [].
a-[)b, and spring foil portions 3a-3b are wound in this order and stacked between the rotating shaft 12 and the case support surface 13. That is, the elastic foil body 1 is formed into a triple-wound cylinder, and in the bearing part a, as shown in FIG. 3, the bearing foil part Ba1, the tongue foil part Da, the spring foil part Sa in order, bring the bearing foil part 3a into close contact with the dump foil part Qa, and make sure that the pressure release path 3 is between the support protrusions 6 and 6 of the dump foil part Qa. Adjust the mutual positions of the respective parts so that 6 and 6 are located between the support protrusions 6 and 6 of the spring foil section 3a. Through this adjustment, the shaft seal section b is automatically moved to the dump foil section Db as shown in FIG. The support protrusions 11 of the spring foil portion Sb are stacked so that they are located between the support protrusions 11 and 11 of the spring foil portion Sb.

Then, as shown in FIG. 1, a key groove 15 is provided in the axial direction of the case support surface 13 by the width of the bearing part a, and the locking and fixing key 7 at the end of the bearing part is inserted into this key groove 15. , by holding the elastic foil body 1 with the mounting plate 16 and restricting the movement of the elastic foil body 1 in the axial direction and around the axis.
/@Configure the receiving structure.

In this way, the foil bearing structure with shaft seal of this example is as follows:
The bearing part a and the shaft seal part A have a foil structure consisting of three layers, and a spring element, a damping element, a bearing element, and a sealing element are arranged in the circumferential direction of the case support surface 13 between each layer.

Now, 1. The operation of this embodiment with the configuration as shown in F will be explained.

The operating principle of the bearing and shaft seal of this embodiment is that the bearing part a is caused to form a bearing gap by a function based on a single flow lubrication in which the viscosity of the working fluid (one liquid) is dominant. This is a non-contact type bearing/shaft seal that supports the rotation 'Fll 112 while avoiding contact with the rotating shaft 12 by creating a gap between the shaft seal parts and the shaft seal.

That is, the bearing part a of the elastic foil body 1 that supports the rotating shaft 12 rotates around the center of the shaft in response to the magnitude of the shaft load, and the bearing part a between the rotating shaft 12 and the bearing foil part 3a. A wedge film is generated in the bearing gap G,1 to form a fluid film pressure, and this fluid film pressure supports the shaft load. by the way,,
When the rotating shaft 12 rotates at high speed, the fluid film pressure in Ga between the bearings increases.

A part of this increased fluid film pressure is guided from the pressure release path 3 to the inner surface of the dump foil portion D11 that is in close contact with the pressure release path 3, and is released therefrom. Since this pressure release is performed from the small-diameter orifice 5 to the large-diameter pocket 4, a large force acts radially outward on the inner surface of the dance foil portion Qa, causing local deformation of the inner surface. A fluid reservoir is formed in the area.

Therefore, a squeeze film damper (') is applied to the damping foil portion Qa to damp the shaft vibration. On the other hand, the pressurized fluid film pressure that has not been released is transferred to the entire circumference of the damping foil portion Oa via the bearing foil portion [3a]. The two supporting protrusions provided on the outer surface of the spring foil portion S
The inner surface between the support projections 6.6 of the LI is pushed radially outward. Therefore, the spring foil portion 3a is deformed into a wave shape in the circumferential direction and exerts a spring function. Therefore, the dump foil part [a] is elastically supported on the case support surface 13, allowing core deformation and thermal deformation of the shaft. Spring required; in addition to 5)) 4r fl'l? i! Since the bearing part a of M construction has a kumping function and the spring is effective, it can stably support the rotating shaft 12 even at high speeds and high temperatures (low temperatures) of 113C.

In addition, the shaft seal portion of the elastic foil body 1 that seals the rotating shaft 12 is arranged so that the inside of the seal portion 11 corresponds to the center of the day of the rotating shaft 12.
While forming a wedge 1, each member is elastically displaced to seal the rotating shaft 12 while avoiding contact with the shaft seal portion 1).

Although the length is long, the four parts between the support protrusions 6 and 6 are open in the width direction, and the rectangular recess 8 of the shaft seal part is formed by the remaining parts 9 and 10 at both ends. Since the width direction is closed, each of the four rectangular parts 8 of the dash 1f 4(r; BL) b and the sedge link foil part 3a,
Originally there were 11 fluid reservoirs. I, Q, rotation 4*12 respectively
G between the seal gap and the seal foil part 1-1)
The pressurized fluid film pressure is R'J at b, and the seal foil part 1 b
When pressed outward in the radial direction, the Sgelinck foil part S'
The wave-like deformation of the rectangular recess 8.b occurs and exerts a spring function. The fluid in s is squeezed and a squeeze membrane pumping action occurs. However, since the pitch of the support protrusions 11, which are the spring elements of the shaft seal part 1), is larger than that of the bearing part a, and the springiness is set relatively low, vibration and expansion may occur. It is possible to stably maintain an extremely small seal gap without contacting the rotation +1iII+12. The shaft seal part in the illustrated example! ■This is a clearance seal for a seal on a cylindrical surface.In this case, the leakage, which is equivalent to the sealing performance, is proportional to the differential pressure and inversely proportional to the seal clearance, so an extremely small seal clearance is maintained. This means that the sealing performance is significantly improved. In this way, the damping function and spring function of the shaft seal part of the foil stacking structure are exerted in addition to the function of fluid film pressure, so high speed and
? Stable sealing performance without contact or clinging can be obtained even at 3 temperatures (low temperature).

As described above, according to this embodiment, the above-mentioned bearing part 1 and shaft seal part are formed from 9 to 9 pieces of foil material, and the surface of the material is processed by a known technique such as photo-etching. It can be mass-produced because it can
It can be manufactured at very low cost. If the spring foil body 1 is inserted between the rotary shaft 12 and the case support surface 13 in a rough position, the spring foil portions Sa, S expand due to the spring properties of the elastic foil body 1 itself.
b is brought into close contact with the '7-spring support 13, and rl
- Since the circumferential position of the Ar frame of the pond is automatically adjusted, the position of the laminated falls can be adjusted individually.
1. There is no need to do this, and assembly work becomes extremely easy.

In addition, the bearing structure used is made of F4R material, so it is small 'X! (In addition to being 111 speeds and high temperature (low temperature), the 11h seal has a stable bearing (instinct, 11h seal has a performance of 1'9x). L-su flow (turbo pressure ↑ 1111 戊,
Before turbo expansion, tai-, f+-sito, Taho cold 7! I
! ! , applied to Hikasa's high-speed rotation Juru/7-Bots 1-
(l You can reduce your own soj or 7 by -17.

Note that the foil structure also has the 1iPJ effect of being resistant to the intrusion of foreign matter.

Figures 5 and 6 show a modification of the embodiment shown in Figure 1, in which the shaft seal part is a simple brane type with a cylindrical surface, and the sealing surface is machined in groups of several circumferences. . That is, in the case of the one shown in FIG. 5, multiple spiral groups 18 are arranged at equal intervals in the length direction on the seal convex surface of the seal foil portion Lb. The one shown in FIG. 6 has a spiral group 18 engraved on the rotary shaft 12 of the seal portion instead of the seal foil portion L 11, and the sealing effect is enhanced by the pumping action of the spiral group 18. It has become. It is desirable to design the direction of the spiral group 18 by determining the high pressure side, the low pressure side, and the direction of rotation, and the illustrated example shows the case where P+ > P2 and the rotation 1 recess 12 rotates as shown by the arrow.

According to this, as the rotary shaft 12 continues to rotate, the seal part is sandwiched and the fluid tries to flow to Pr-'P2 due to the differential pressure, but the pumping 1' of the Spadel group 18 "Depending on the purpose, the fluid flows to the P2 side which has a low pressure. The ability to send the fluid to the high-pressure [)■ side is optically transported, and the sealing performance can be actively improved. The seal effect is young.

, L, ρ2'・F''1 (r1) (Although not shown in Figure 5, the spiral group 18 is set in the opposite direction to that in Figures 5 and 6. Opposite side 9: ■
Just install it in the section - J.

[Invented by Song Dynasty] In summary, the present invention provides the following excellent effects.

III Since the IMI receiving part and the shaft seal part are integrally formed with the elastic foil, the small W° on the fixed side
! Light Cloak Sevenri [For good reason, monkey and cane, rotation 1111
The axial stiffness of It is possible to significantly increase the

2) By using a foil structure for the bearing and the sealing part, it can sufficiently handle centrifugal expansion and mature expansion of the rotating shaft, and even with the small gap C1, the contact and clinging problems that were common in the past are avoided. It can function stably and safely at high temperatures (low temperatures) and high speeds without causing damage.

[Brief explanation of the drawing]

Fig. 1 is a side view including a partially expanded state showing a preferred actual IM example of the shaft seal-equipped file bearing structure according to the present invention, and Fig. 2 is the main part of Fig. 1. A developed view of the elastic foil body in the circumferential direction, FIG. 3 is a sectional view taken along the arrow ■ in FIG. 1, and a normal sectional view of the bearing part, and FIG.
5 and 6 are side views including a partially expanded state 11n showing a modification of the present invention. In the figure, 1 is an elastic foil body, 3 is a pressure release path 12 is a rotating shaft, 13 is a case support surface, a is a bearing part, b is a shaft seal part, [3a is a bearing foil part, D3 is a gunb7A file part, 3a is the subring file part, l b L:, L
Seal-) 4 ile part, Db is kumbufoil part, 31)
It is LL spring foil 81X. IIJ shi'I! 1i Konjin G Yojima Harima Sen 1 [Sai Co., Ltd. Agent Patent Attorney Kinutani (H Male Figure 1 b・'1 City Sea 1 and Sb Nubu'): /7
7-cho Ishiteiku Q Ln scolding ()' ヱ [F] Δ

Claims (1)

[Claims] a bearing foil section having a pressure release path that forms a fluid film pressure and releases the fluid film pressure; a dump foil section that receives the fluid film pressure released from the pressure release path and damps vibrations;
An elastic foil bearing section in which a spring foil section that elastically supports a dump foil section is successively formed, a seal foil section that forms fluid film pressure, a dump foil section that dampens vibrations of the seal foil section, and a spring that elastically supports the dump foil section. An elastic foil body formed by integrally molding an elastic foil shaft seal portion in which foil portions are successively formed in parallel in parallel is wound and laminated between the rotating shaft and the case support surface in the above-described continuous formation order. Foil bearing structure with shaft seal.