CN201827234U - Axial throttling structure of liquid sliding antithrust bearing - Google Patents
Axial throttling structure of liquid sliding antithrust bearing Download PDFInfo
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- CN201827234U CN201827234U CN2010205385953U CN201020538595U CN201827234U CN 201827234 U CN201827234 U CN 201827234U CN 2010205385953 U CN2010205385953 U CN 2010205385953U CN 201020538595 U CN201020538595 U CN 201020538595U CN 201827234 U CN201827234 U CN 201827234U
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- axial
- bearing
- thrust bearing
- main shaft
- throttling
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Abstract
The utility model discloses an axial throttling structure of a liquid sliding antithrust bearing, belonging to the field of a liquid sliding bearing and comprising a bearing, an antithrust bearing and an antithrust bearing positioning piece, wherein an axial throttling edge A used for the axial thrust resistance of a spindle is arranged at the inner side of the bearing; the antithrust bearing is arranged between the axial throttling edge A of the bearing and the spindle; an axial throttling edge B opposite to the axial throttling edge A is arranged on the outer circumference of the antithrust bearing; a throttling clearance C is arranged between the axial throttling edge A and the axial throttling edge B; the bearing, the antithrust bearing and the spindle form a cavity E communicated with a throttler; the inner groove of the bearing and the outer circle of the spindle form a cavity Q; the inner side of the bearing between the cavity Q and the cavity E is provided with an axial throttling edge S; and a throttling clearance is arranged between the spindle and the corresponding part of the axial throttling edge S. In the utility model, the rigidity of the spindle is effectively improved and the axial throttling structure is specially applicable to a machine tool spindle system.
Description
Technical field
The utility model relates to the liquid sliding bearing field, particularly a kind of liquid sliding thrust bearing throttle structure that is applicable to machine-tool spindle system.
Background technique
Existing liquid sliding thrust bearing two ends all are the ring cavity structures that adopts radially throttling.The people such as Zhong Hong that the Electronic Industry Press publishes in September, 2007 write " hydrostatic pressure dynamic and hydrostatic bearing design service manual " P52 page or leaf and have introduced a kind of hydrostatic spindle unit of typical C 6140 lathes.As shown in Figure 1, its main shaft 1, fore bearing 2, rear bearing 3 and thrust bearing 4, locking nut 5 has constituted the axial thrust bearing structure of hydrostatic spindle unit jointly, and the ring cavity structure of radially throttling is all adopted in the end that fore bearing 2 and rear bearing 3 are used for thrust, and thrust bearing 4 is arranged in rear bearing 3 rear portions, utilize locking nut 5 fixing, adjust the i.e. gap on throttling limit radially of axial clearance by the size that changes thrust bearing gap spacer 6.Because the elongation △ L that the main shaft thermal expansion causes is usually in 1/100 millimeter magnitude, and thrust bearing axial clearance and it is at the same order of magnitude, when main shaft 1 high speed rotating heating expansion caused length dimension to become big, axial clearance can become greatly thereupon, caused axial stiffness to reduce.
Summary of the invention
The purpose of this utility model provides the axial throttle structure of a kind of liquid sliding thrust bearing, it will have two ends now all is that the thrust bearing of radially throttle structure changes the radially thrust bearing of the axial throttle structure of the throttling the other end of an end into, can improve the working condition and the rigidity of main shaft, especially high-speed main spindle effectively.
For achieving the above object, the technical solution adopted in the utility model is: the axial throttle structure of described liquid sliding thrust bearing comprises bearing, thrust bearing and thrust bearing locating piece, its structural feature is, described bearing inboard is useful on the axial throttling limit A of main shaft axial thrust, be provided with thrust bearing between this axial throttling limit A and the main shaft, the axial throttling limit B relative with this axial throttling limit A arranged on this thrust bearing excircle, between described axial throttling limit A and the described axial throttling limit B throttle clearance C is arranged, bearing, thrust bearing and main shaft form the chamber E that is communicated with flow controller, bearing inside groove and main shaft outer ring coelosis Q, there is axial throttling limit S the inboard of bearing between chamber Q and chamber E, between the main shaft part corresponding with throttling limit S throttle clearance arranged.
Described liquid sliding thrust bearing is provided with also radially that throttle structure is, at bearing one end face the annular chamber D that is communicated with flow controller is arranged, and between this bearing face end face corresponding with the main shaft major part radially throttle clearance F is arranged.
Be provided with the chamber M that is communicated with the flowing medium container by passage between described bearing and the thrust bearing cylindrical.
Below the utility model made further specify.
The axial throttle structure of a kind of liquid sliding thrust bearing, comprise bearing 9, thrust bearing 8 and snap ring 11, described bearing 9 inboards are useful on the axial throttling limit A of main shaft 1 axial thrust, be provided with thrust bearing 8 between this axial throttling limit A and the main shaft 1, the axial throttling limit B relative with this axial throttling limit A arranged on these thrust bearing 8 excircles, between described axial throttling limit A and the described axial throttling limit B throttle clearance C is arranged, bearing 9, thrust bearing 8 and main shaft 1 form the chamber E that is communicated with flow controller, bearing 9 inside grooves and main shaft 1 outer ring coelosis Q, chamber Q is communicated with the flowing medium container by passage, there is axial throttling limit S the inboard of bearing 9 between chamber Q and chamber E, between main shaft 1 part corresponding with throttling limit S throttle clearance arranged.
Further, shown in Fig. 2 and 6, axial throttling limit B described in the utility model stretches into the axial throttling hem width degree L1 of the width L2 of bearing 9 axial throttling limit A less than bearing 9 axial thrusts, in such cases, effectively axially throttling hem width degree L0 equals the width L2 that axial throttling limit B stretches into bearing 9 axial throttling limit A, because the elongation △ L that main shaft 1 thermal expansion causes is usually in 1/100 millimeter magnitude, and effectively axial throttling hem width degree L0 is usually in the millimeter magnitude, so the elongation △ L that main shaft 1 thermal expansion causes is very little to the influence of effectively axial throttling hem width degree L0, thereby makes pressure P 2 kept stables.
Described bearing 9 end faces are radially throttle clearance F with gap between the corresponding end face of main shaft 1 major part, when described radially throttle clearance F when stablizing gap F0, the pressure P 1 of end face ring die cavity D diminishes, the front end bearing capacity is less than the rear portion bearing capacity, the rear portion bearing capacity promotes main shaft 1 to reducing the radially direction motion of throttle clearance F, the pressure P 1 of end face ring die cavity D becomes greatly thereupon, stablizes gap F0 until reaching.Otherwise when throttle clearance F radially when stablizing gap F0, the pressure P 1 of end face ring die cavity D becomes big, the front end bearing capacity is greater than the rear portion bearing capacity, the front end bearing capacity promotes main shaft 1 to enlarging the radially direction motion of throttle clearance F, the pressure P 1 of end face ring die cavity D diminishes thereupon, stablizes gap F0 up to reaching.
System pressure is that the flowing medium of P0 is leaded up to the annular chamber D that flows into bearing 9 end faces after the flow controller throttling in the work, under the effect on the annular radial throttling limit that main shaft 1 major part ear end face and bearing 9 front-end faces form, form pressure P 1, by known hydraulic pressure formula as can be known when radially throttle clearance F diminishes, ring-like chamber D internal pressure P1 increases, when radially throttle clearance F becomes big, revealing increases, ring-like chamber D internal pressure P1 reduces, another road pressure fluid medium is by flowing into after the flow controller throttling by bearing 9, the chamber E that thrust bearing 8 and main shaft 1 form, formation pressure P 2 under effectively axially throttling limit L0 that the throttling inner hole surface of thrust bearing 8 cylindricals and bearing 9 rear portion shoulder holes forms and the axial throttling limit S effect of bearing 9 in the inboard between chamber Q and the chamber E, the pressure P 1 of end face ring die cavity D multiply by end face ring die cavity D useful area and draws the front end bearing capacity, the pressure P 2 of chamber E multiply by the effective face area of thrust bearing and draws the rear portion bearing capacity, reach balance when the bearing capacity at two ends, front and back equates, radially throttle clearance F reaches stable.
Further, shown in Fig. 3 and 7, the width L2 that axial throttling limit B described in the utility model stretches into bearing 9 axial throttling limits also can be not less than the axial throttling hem width degree L1 of bearing 9 axial thrusts and elongation △ L sum L1+ △ L that main shaft 1 thermal expansion causes, in such cases, described effectively axially throttling hem width degree L0 equals axial throttling hem width degree L1, the elongation △ L that main shaft 1 thermal expansion causes can not have influence on the effectively axially width L0 on throttling limit, thereby can not have influence on the working condition and the rigidity of main shaft 1, this point is used on the high-speed main spindle especially meaningful.
Further, axial throttling limit B described in the utility model stretches into the elongation △ L sum L1+ △ L that the width L2 of bearing 9 axial throttling limit A can also cause less than the axial throttling hem width degree L1 and main shaft 1 thermal expansion of bearing 9 axial thrusts, and the described axial throttling limit B width L2 that stretches into axial throttling limit A is not less than the axial throttling hem width degree L1 of bearing 9 axial thrusts.In such cases, described effectively axially throttling hem width degree L0 approximates axial throttling hem width degree L1, and the elongation △ L that the main shaft thermal expansion causes is very little to the width L0 influence on effectively axial throttling limit, thereby can not have influence on the working condition and the rigidity of main shaft substantially.
Further, above-mentioned bearing is fore bearing or rear bearing, is provided with seal ring between described thrust bearing and the main shaft, can be by seal ring sealing pressure fluid medium is installed.Described thrust bearing locating piece can be to be used to limit any in axial sliding known structure of thrust bearing, as locking nut or snap ring etc.Described flow controller can be any known flow controller, as orifice restriction device, capillary restrictor, chink type flow controller and reaction type flow controller etc.Described passage is preferably external pipeline or the duct that processes etc.
Compared with prior art, the beneficial effects of the utility model are: it will have two ends now all is that the thrust bearing of radially throttle structure changes the radially thrust bearing of the axial throttle structure of the throttling the other end of an end into, improved main shaft effectively, especially the working condition of high-speed main spindle and rigidity have improved its rigidity.
Description of drawings
Below in conjunction with drawings and Examples the utility model is further elaborated.
Fig. 1 is for having the radially structure principle chart of throttling of liquid sliding thrust bearing now;
Fig. 2 is the utility model L1〉fundamental diagram during L2;
Fundamental diagram when Fig. 3 is the utility model L2 〉=L1+ △ L;
Fig. 4 is a kind of embodiment's of the utility model a structural representation;
Fig. 5 is the another kind of embodiment's of the utility model a structural representation;
Fig. 6 is the G place partial enlarged drawing of Fig. 2;
Fig. 7 is the H place partial enlarged drawing of Fig. 3.
In the drawings:
The 1-main shaft; The 2-fore bearing; The 3-rear bearing;
4, the 8-thrust bearing; The 5-locking nut; The 6-spacer;
9, the 16-bearing; The 10-seal ring; The 11-snap ring;
The axial throttling limit of A-bearing 9; The axial throttling limit of B-thrust bearing 8;
The C-throttle clearance; The D-annular chamber;
F-is throttle clearance radially;
M-is located at the chamber that is communicated with the flowing medium container between bearing 9 and the thrust bearing 8;
The chamber that Q-bearing 9 inside grooves and main shaft 1 cylindrical form;
The axial throttling limit of the inboard of S-bearing 9 between chamber Q and chamber E;
The gap is stablized on F0-annular radial throttling limit;
The elongation that 1 thermal expansion of △ L-main shaft causes;
L0-is throttling hem width degree effectively axially;
The axial throttling hem width degree of L1-bearing 9 axial thrusts;
The axial throttling of L2-limit B stretches into the width of axial throttling limit A;
The P0-system pressure;
The ring-like chamber of P1-D internal pressure;
P2-chamber E internal pressure.
Embodiment
The axial throttle structure of a kind of liquid sliding thrust bearing, as shown in Figure 4, comprise bearing 9, thrust bearing 8 and snap ring 11, described bearing 9 is installed between the stub end and thrust bearing 8 of main shaft 1, by snap ring 11 thrust bearing 8 is limited on the main shaft 1, be provided with radially throttle structure between one end of bearing 9 and corresponding main shaft 1 stub end, this radially throttle structure be on described bearing 9 end faces annular chamber D that is communicated with flow controller to be arranged, throttle clearance F is arranged, bearing 9 the other ends and main shaft 1 between the bearing 9 end faces end face corresponding with main shaft 1 major part, be provided with axial throttle structure between the thrust bearing 8.Described axial throttle structure is, be useful on the axial throttling limit A of main shaft 1 axial thrust in bearing 9 inboards, be provided with thrust bearing 8 between this axial throttling limit A and the main shaft 1, the axial throttling limit B relative with this axial throttling limit A arranged on these thrust bearing 8 excircles, between described axial throttling limit A and the described axial throttling limit B throttle clearance C is arranged, bearing 9, thrust bearing 8 and main shaft 1 form the chamber E that is communicated with flow controller, bearing 9 inside grooves and main shaft 1 outer ring coelosis Q, chamber Q is communicated with the flowing medium container by passage, there is axial throttling limit S the inboard of bearing 9 between chamber Q and chamber E, between main shaft 1 part corresponding with throttling limit S throttle clearance arranged.
Be provided with seal ring 10 between described thrust bearing 8 and the main shaft 1, axially limit the position of thrust bearing 8 by snap ring 11.Be provided with the chamber M that is communicated with the flowing medium container by passage between described bearing 9 and the thrust bearing 8.
Embodiment 2
The axial throttle structure of a kind of liquid sliding thrust bearing, as shown in Figure 5, comprise the bearing 9 that is contained on the main shaft 1,16, thrust bearing 8 and snap ring 11, described main shaft 1 stub end is equipped with bearing 16, be provided with radially throttle structure between this bearing 16 and main shaft 1 stub end, this radially throttle structure be, the annular chamber D that is communicated with flow controller is arranged on the described bearing 16, between end face of bearing 16 and the corresponding end face of main shaft 1 major part radially throttle clearance F is arranged, the axial throttle structure of described liquid sliding thrust bearing is installed in the little head end of bearing 9 and main shaft 1, thrust bearing 8 is limited on the main shaft 1 by locking nut 5, bearing 9 and main shaft 1, be provided with 1 described axial throttle structure between the thrust bearing 8 as embodiment.
Two kinds of concrete examples when embodiment 1 and embodiment 2 are L2 〉=L1+ △ L utilize L1 certainly〉situation of L2 or L1≤L2＜L1+ △ L is also within protection domain of the present utility model.
Claims (8)
1. axial throttle structure of liquid sliding thrust bearing, comprise bearing (9), thrust bearing (8) and thrust bearing locating piece, it is characterized in that, described bearing (9) inboard is useful on the axial throttling limit A of main shaft (1) axial thrust, be provided with thrust bearing (8) between this axial throttling limit A and the main shaft (1), the axial throttling limit B relative with this axial throttling limit A arranged on this thrust bearing (8) excircle, between described axial throttling limit A and the described axial throttling limit B throttle clearance C is arranged, bearing (9), thrust bearing (8) and main shaft (1) form the chamber E that is communicated with flow controller, bearing (9) inside groove and main shaft (1) outer ring coelosis Q, there is axial throttling limit S the inboard of bearing (9) between chamber Q and chamber E, between main shaft (1) part corresponding with throttling limit S throttle clearance arranged.
2. the axial throttle structure of liquid sliding thrust bearing according to claim 1 is characterized in that, is provided with one or more chamber M that are communicated with the flowing medium container by passage between described bearing (9) and the thrust bearing (8).
3. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2 is characterized in that, described axial throttling limit B stretches into the axial throttling hem width degree L1 of the width L2 of axial throttling limit A less than bearing (9) axial thrust.
4. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2, it is characterized in that the width L2 that described axial throttling limit B stretches into axial throttling limit A is not less than the axial throttling hem width degree L1 of bearing (9) axial thrust and elongation △ L sum L1+ △ L that main shaft (1) thermal expansion causes.
5. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2, it is characterized in that, the elongation △ L sum L1+ △ L that the width L2 that described axial throttling limit B stretches into axial throttling limit A causes less than the axial throttling hem width degree L1 and main shaft (1) thermal expansion of bearing (9) axial thrust, and the described axial throttling limit B width L2 that stretches into axial throttling limit A is not less than the axial throttling hem width degree L1 of bearing (9) axial thrust.
6. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2 is characterized in that described bearing (9) is fore bearing or rear bearing.
7. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2 is characterized in that, is provided with seal ring (10) between described thrust bearing (8) and the main shaft (1).
8. the axial throttle structure of liquid sliding thrust bearing according to claim 1 and 2 is characterized in that, described thrust bearing locating piece is locking nut (5) or snap ring (11).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205385953U CN201827234U (en) | 2010-09-21 | 2010-09-21 | Axial throttling structure of liquid sliding antithrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205385953U CN201827234U (en) | 2010-09-21 | 2010-09-21 | Axial throttling structure of liquid sliding antithrust bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201827234U true CN201827234U (en) | 2011-05-11 |
Family
ID=43965773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205385953U Expired - Fee Related CN201827234U (en) | 2010-09-21 | 2010-09-21 | Axial throttling structure of liquid sliding antithrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201827234U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111594548A (en) * | 2020-07-06 | 2020-08-28 | 德本恒嘉精机(昆山)有限公司 | Hydrostatic bearing sleeve |
-
2010
- 2010-09-21 CN CN2010205385953U patent/CN201827234U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111594548A (en) * | 2020-07-06 | 2020-08-28 | 德本恒嘉精机(昆山)有限公司 | Hydrostatic bearing sleeve |
| CN111594548B (en) * | 2020-07-06 | 2023-09-19 | 德本恒嘉精机(昆山)有限公司 | Hydrostatic bearing sleeve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110511 Termination date: 20180921 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |