CN114799238A - High-bearing large dynamic horizontal dynamic and static pressure main shaft system - Google Patents
High-bearing large dynamic horizontal dynamic and static pressure main shaft system Download PDFInfo
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- CN114799238A CN114799238A CN202210741530.6A CN202210741530A CN114799238A CN 114799238 A CN114799238 A CN 114799238A CN 202210741530 A CN202210741530 A CN 202210741530A CN 114799238 A CN114799238 A CN 114799238A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/70—Stationary or movable members for carrying working-spindles for attachment of tools or work
Abstract
The invention discloses a high-bearing large dynamic horizontal type dynamic and static pressure main shaft system.A main shaft hole penetrating through two ends and an oil pool is arranged in a box body, positioning sleeves I and II are fixed in the box body, rolling and dynamic and static pressure bearings are fixed at two ends of the main shaft hole, and the inner side and the outer side of a rolling bearing are abutted against the positioning sleeve I and a bearing cover I on the box body; the inner side and the outer side of the dynamic and static pressure bearing are abutted with a positioning sleeve II and a bearing cover II fixed on the box body; the main shaft is in interference fit with the rolling bearing and in clearance fit with the dynamic and static pressure bearings; framework oil seals I and II are fixed in counter bores I and II of the bearing covers I and II, and sealing lips extend towards the main shaft to form interference fit sealing; the box body is provided with an oil inlet I which is communicated with an oil outlet of the vertical oil duct I and an oil outlet of the circulating system, and the vertical oil duct I is communicated with an oil inlet of an outer spacer sleeve between the rolling bearings; the oil inlet II is arranged on the box body and is communicated with the vertical oil duct II and the high-pressure oil supply system, the vertical oil duct II is communicated with the oil supply groove of the dynamic and static pressure bearing, and the dynamic and static pressure bearing box has the advantages of being strong in bearing capacity, large in speed change range, capable of rotating forward and backward and even in temperature distribution.
Description
Technical Field
The invention relates to the technical field of machine tool spindles, in particular to a high-bearing dynamic horizontal type dynamic and static pressure spindle system which is strong in bearing capacity, large in speed change range, capable of rotating positively and negatively and uniform in temperature distribution.
Background
With the development of ultra-precision machining technology and high-speed machine tools, higher requirements are put forward on the speed and the precision of a machine tool spindle. At present, a machine tool spindle mainly uses several bearings such as a rolling bearing, a magnetic bearing, a dynamic and static pressure bearing, a dynamic pressure bearing and the like as support components. However, the rolling bearing has limited bearing capacity, and after the rolling bearing is used for a period of time, due to fatigue wear of the rolling body and the raceway, the main shaft needs to be frequently disassembled and replaced, so that the previous precision and working requirements are difficult to guarantee, and the bearing is particularly worsened under the condition of ultrahigh speed; the magnetic bearing not only has a complex structure, but also has immature technology and high cost, and cannot be applied in a large scale; although the hydrostatic bearing has strong bearing capacity and high precision, the liquid lubrication has large damping and heat productivity, so the speed and the rotation direction are limited, and the air lubrication has small friction force and is suitable for the working conditions of high speed and even ultra high speed, but the air film has low rigidity and poor overload resistance, and can only be used for a high-speed light-load machine tool main shaft; the simple dynamic pressure bearing is used as a supporting component, so that dry abrasion is inevitably generated when the spindle is started and stopped, and the normal operation of the spindle and even the whole equipment is influenced. Therefore, the technology of simultaneously adopting hybrid bearings is also available at present, but most of the technologies can only achieve basic functions, and the throttler is complex to arrange and control, and causes rigidity reduction and overlarge local stress, and finally causes insufficient bearing capacity or one-way rotation direction. The machine tool main shaft generally adopts a plurality of supporting modes of simultaneously preparing a rolling bearing, a hydrostatic bearing and a rolling bearing, a dynamic and static pressure bearing and a rolling bearing at the front and the back, simultaneously adopting the hydrostatic bearing at the front and the back, and the like.
At present, the mode of the dynamic and static pressure bearing and the rolling bearing combines the characteristics of strong bearing capacity, high precision, low rolling bearing cost and convenient use of the dynamic and static pressure bearing, is particularly suitable for the use requirements of medium-high speed and high precision at present, and is most widely applied at present; however, in order to solve the problems of large local stress and easy fatigue of the rolling bearing, it is necessary to adopt methods such as oil immersion and spraying for lubrication and temperature reduction, and the hybrid bearing needs to be improved from the aspects of structure and restrictor control, so as to overcome the problems of insufficient bearing capacity, unidirectional rotation and difficult heat dissipation of the hybrid bearing. In the prior art, in order to solve the defects of the hybrid bearing, a face-to-face wedge-shaped groove or an arc-shaped rectangular surface is arranged in an oil groove to realize bidirectional rotation, but the problems of rigidity reduction, overlarge local stress, insufficient bearing capacity and difficulty in heat dissipation are not solved because the dynamic pressure effect in any direction rotation is consistent with the effect of a one-way wedge-shaped groove. The dynamic and static pressure bearing of the self-compensating liquid is formed by changing the structural characteristics of the inner surface of the dynamic and static pressure bearing instead of an external restrictor, so that the dynamic pressure effect is enhanced on the basis of keeping the static pressure bearing capacity, and on the other hand, the damping is favorably increased, so that the running precision of the dynamic and static pressure bearing of the self-compensating liquid is enhanced. However, the traditional opposite oil pad throttling self-compensating bearing needs to manufacture a throttling oil pad opposite to the working oil cavity, so that the size of the bearing is increased, and the throttling oil pad offsets the oil film force of the working oil cavity; the Kane type angular surface throttling self-compensating bearing is compact in structure, but fluid diffusion on a throttling surface exists, and the throttled oil pressure is influenced.
Because the existing main shaft support needs to lubricate and cool the rolling bearing, and the static pressure and dynamic pressure bearings need to supply high-pressure oil, how to solve the problem that the oil is not polluted from the outside and different kinds of pollution are generated between the static pressure bearing and the dynamic pressure bearing is very important. At present, the lathe main shaft generally adopts O shape sealing washer, lip elastic seal circle, contact seal structure such as complicated mechanical seal, and labyrinth non-contact seal, but contact seal is because the dynamic friction is vice not only can produce the heat, influence the heat stability of main shaft, and the dynamic friction is vice still can lead to life to reduce by a wide margin and arouse the vibration under lubricated bad condition, seriously influence the reliability of sealed and the precision of main shaft, labyrinth seal then need form longer sealed passageway and just can guarantee sealed effect, consequently also lead to the main shaft to occupy great axial space along the labyrinth seal of axial arrangement, the head of a bed incasement space that not only occupies is great, it is also comparatively difficult to arrange.
Disclosure of Invention
The invention aims to provide a high-bearing large dynamic horizontal type dynamic and static pressure main shaft system which is strong in bearing capacity, large in speed change range, capable of rotating forwards and backwards and uniform in temperature distribution.
The invention is realized by the following steps: the oil tank is arranged in the middle of the box body along the length direction, a main shaft hole penetrating through two ends and the oil tank is transversely formed in the box body, a positioning sleeve I and a positioning sleeve II are fixedly arranged on two sides of the main shaft hole close to the oil tank respectively, the rolling bearings are fixedly arranged in the main shaft hole close to a driving end in a matched mode, the outer ring of the bearing close to the oil tank of the matched rolling bearing is abutted to the positioning sleeve I, and the outer ring far away from the bearing close to the oil tank is abutted to a bearing cover I fixedly arranged on the end face of the box body; the dynamic and static pressure bearing is fixedly arranged in a main shaft hole close to the end of the shaft, the side close to the oil pool of the dynamic and static pressure bearing is abutted with the positioning sleeve II, and the outer side of the side far away from the dynamic and static pressure bearing is abutted with a bearing cover II fixedly arranged on the end face of the box body; one side of the main shaft is in interference fit with an inner ring inner hole of the rolling bearing, and the other side of the main shaft is in clearance fit with an inner hole of the dynamic and static pressure bearing;
the framework oil seal I is fixedly arranged in a counter bore I in the inner side of the bearing cover I, and the sealing lip I extends towards the main shaft to form interference fit sealing;
an oil inlet I is formed in the upper portion, close to the driving end, of the box body and is communicated with a vertical oil duct I in the box body, an oil hole axially formed in an outer spacer sleeve between the vertical oil duct I and the rolling bearing is communicated, the diameter of an inner hole of the positioning sleeve I is larger than the outer diameter of the main shaft, and the oil inlet I and an oil outlet of the oil supply circulating system are communicated with the lubricating rolling bearing through a pipeline;
the upper portion of the head end close to the shaft of the box body is provided with an oil inlet hole II and is communicated with a vertical oil duct II in the box body, the vertical oil duct II is communicated with an oil supply groove in the outer circular surface of the hybrid bearing, and the oil inlet hole II is communicated with an oil supply port of a high-pressure oil supply system through a pipeline.
The invention has the beneficial effects that:
1. the invention adopts the traditional configuration mode of the dynamic and static pressure bearing at the shaft head end and the rear end rolling bearing, not only can bear radial and bidirectional axial loads, but also has strong bearing capacity and high precision of the dynamic and static pressure bearing, low cost of the rolling bearing and convenient use, and is particularly suitable for the use requirements of medium-high speed and high precision.
2. The oil pool is arranged in the middle of the box body, the oil inlet I is arranged on the box body and communicated with the vertical oil duct I, and the oil inlet I is communicated with the oil hole in the outer spacer sleeve between the vertical oil duct I and the rolling bearing, so that lubricating oil in the rolling bearing is collected in the box body, the rolling bearing can be lubricated and radiated conveniently, the temperature of the rolling bearing, a main shaft and the box body is more balanced through the flow of oil in the box body and the rolling bearing, and the oil leakage on the end surface can be avoided; and the hydrostatic bearing can make the temperature of the hydrostatic bearing, the main shaft and the box body more balanced through the vertical oil duct II in the box body and the oil inlet hole II at the upper part, thereby effectively improving the thermal stability of the traditional system of the main shaft and ensuring the output precision of the machine tool.
3. The invention adopts a framework oil seal I at the outer side of the rolling bearing and a framework oil seal II at the outer side of the dynamic and static pressure bearing, although the contact type sealing can cause heating, the oil liquid required to be sealed needs to be recycled, so that the heat can be taken away in time, the sealing performance is ensured, the bad heat influence on a machine tool shafting can be reduced, and particularly according to the fact that the oil liquid pressure of a dynamic and static pressure bearing is high, the outer side of the dynamic and static pressure bearing is also provided with a non-contact labyrinth seal, the inner side is sealed by the dynamic and static pressure bearing, the sealing protection capability of the outer side of the dynamic and static pressure bearing is further improved in a targeted manner, the leakage of the inner part also enters the framework oil seal to lubricate the framework oil seal, so that the protection capability of the foreign matters outside entering the bearing is improved, the increase of heating and the complex structure caused by the increase of sealing can be avoided, and the design structure of the replaceable sealing seat enables the manufacture and the later maintenance to be more convenient and faster.
4. According to the dynamic and static pressure bearing, the plurality of V-shaped grooves are arranged at intervals in the circumferential direction in the oil groove, so that oil in the V-shaped grooves can form a bearing oil film in the starting and stopping process to avoid dry friction on the surface of a friction pair, the oil can flow from deep to shallow along the V-shaped grooves at high speed to form and enhance the dynamic pressure effect of oil wedge, the structure of the V-shaped grooves can ensure that the positive and negative rotation can form an effective dynamic pressure effect of the oil wedge, and the static pressure of the bearing works in the starting process, so that the working state that the dynamic pressure is dominant can be realized by electrically adjusting the pressure of oil supply oil at high speed after the starting is finished, and an effective high-pressure lubricating film can be formed in a wider rotating speed range.
5. The V-shaped grooves of the dynamic and static pressure bearing simultaneously play a role of a static pressure bearing, so that the difficulty in arrangement and control of the throttler can be reduced, and the plurality of V-shaped grooves arranged in a single static pressure oil cavity can homogenize the local pressure during oil wedging pressure effect, so that the problems of more rigidity reduction, overlarge local stress and insufficient bearing capacity caused by the fact that the pressure is uniform are solved. And set up the oil return groove between adjacent oil pocket, can effectively prevent the mutual interference of fluid between each oil groove of bearing to the operation is more stable.
6. The hybrid bearing is also provided with oil guide grooves communicated with adjacent V-shaped grooves, so that oil in the oil groove can automatically flow back to adjacent and even farther low-pressure V-shaped grooves from the high-pressure V-shaped grooves to achieve automatic balance of high-pressure and low-pressure oil in the oil groove, the oil supporting capacity of a high-pressure area at the same rotating speed is obviously improved, the rotating precision is increased, the problem that the oil pressure of a high-pressure area of a traditional single wedge-shaped groove is reduced to a limited extent is solved, and a rotating shaft can reach higher rotating speed under the drive of a motor with the same power or reduce energy consumption at the same rotating speed; moreover, the high-pressure area oil pressure is obviously reduced, and the plurality of V-shaped grooves which can enlarge the heat dissipation area can enable the rotating shaft to reach lower oil temperature at the same speed or reach higher rotating speed under the condition of allowable oil temperature.
7. According to the dynamic and static pressure bearing, the outer ring groove and the throttling platform in the inner circumferential direction are arranged on the outer circular surface of the body, the outer diameter of the throttling platform is smaller than the diameter of the outer circular surface of the body, and the oil guide hole connected with the oil groove penetrates through the throttling platform, so that a small gap can be formed between the outer circular surface of the throttling platform and the outer seat during working, high-pressure oil in the outer ring groove is blocked when flowing to the oil guide hole, the oil pressure in the oil groove is lower than the pressure in the outer ring groove to form a throttling effect, the oil damping in the oil groove is increased, and the capability of resisting the speed disturbance of the rotating shaft is improved, so that the rotating precision is increased, and the vibration absorption and noise reduction are facilitated; in addition, the gap throttling effect formed by the throttling table does not need an additional connecting channel and an additional auxiliary structure, so that the structure is more compact and the manufacturing requirement is lower.
In conclusion, the invention has the characteristics of strong bearing capacity, large speed change range, capability of forward and reverse rotation and uniform temperature distribution.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a front view of FIG. 1;
FIG. 3 is a left side view of FIG. 2;
FIG. 4 is a cross-sectional view of FIG. 2 (fasteners not shown);
FIG. 5 is a top view of FIG. 2;
FIG. 6 is one of the cross-sectional views of FIG. 5 (fasteners not shown);
FIG. 7 is a second cross-sectional view of FIG. 5 (fasteners not shown);
FIG. 8 is one of the enlarged partial views of FIG. 7 (fasteners not shown);
FIG. 9 is a second enlarged partial view of FIG. 7 (fasteners not shown);
FIG. 10 is a schematic view of a hybrid bearing according to the present invention;
FIG. 11 is a longitudinal cross-sectional view of FIG. 10;
FIG. 12 is a transverse cross-sectional view of FIG. 10;
in the figure: 1-a box body, 1A-an oil sump, 1B-a spindle hole, 1C-an oil inlet hole I, 1D-a vertical oil duct I, 1E-an oil inlet hole II, 1F-a vertical oil duct II, 1G-a horizontal oil duct, 1H-an oil discharge port, 1J-an oil discharge port, 2-a spindle, 3-a rolling bearing, 5-a hydrodynamic bearing, 5A-a body, 5B-an oil groove, 5C-an oil return groove, 5D-an oil guide hole, 5E- "V" -shaped groove, 5F-an oil guide groove, 5G-an arc rectangular surface, 5H-an oil collection groove, 5J-an outer ring groove, 5K-a throttle table, 5M-an oil supply groove, 5N-a seal groove, 6-a positioning sleeve I, 7-a positioning sleeve II, 8-a bearing cover I, 9-bearing cover II, 9A-annular lip, 10-framework oil seal I, 10A-sealing lip I, 11-framework oil seal II, 11A-sealing lip II, 12-outer spacer bush, 13-movable ring seat, 13A-annular groove, 13B-large ring platform, 13C-chip groove I, 14-chip groove II, 15-sealing seat I, 16-sealing seat II, 17-adapter sleeve and 18-dust cover.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
As shown in fig. 1 to 9, the invention includes a box body 1, a main shaft 2, a rolling bearing 3, and a hybrid bearing 5, wherein an oil pool 1A is arranged in the middle of the box body 1 along the length direction, a main shaft hole 1B penetrating through both ends and the oil pool 1A is transversely arranged on the box body 1, a positioning sleeve i 6 and a positioning sleeve ii 7 are respectively fixedly arranged on both sides of the main shaft hole 1B near the oil pool 1A, the rolling bearing 3 is fixedly arranged in the main shaft hole 1B near the driving end in a paired manner, an outer ring of the rolling bearing 3 near the oil pool 1A is abutted against the positioning sleeve i 6, and an outer ring of the bearing far away from the oil pool 1A is abutted against a bearing cover i 8 fixedly arranged on the end face of the box body 1; the dynamic and static pressure bearing 5 is fixedly arranged in a main shaft hole 1B at the end close to the shaft head, the side close to an oil pool 1A of the dynamic and static pressure bearing 5 is abutted with a positioning sleeve II 7, and the outer side of the far side is abutted with a bearing cover II 9 fixedly arranged on the end face of the box body 1; one side of the main shaft 2 is in interference fit with an inner ring inner hole of the rolling bearing 3, and the other side of the main shaft is in clearance fit with an inner hole of the dynamic and static pressure bearing 5;
the framework oil seal structure is characterized by further comprising a framework oil seal I10 and a framework oil seal II 11, wherein the framework oil seal I10 is fixedly arranged in a counter bore I on the inner side of the bearing cover I8, a sealing lip I10A extends towards the main shaft 2 to form interference fit sealing, the framework oil seal II 11 is fixedly arranged in a counter bore II on the inner side of the bearing cover II 9, and a sealing lip II 11A extends towards the main shaft 2 to form interference fit sealing;
the upper part of the box body 1 close to the driving end is provided with an oil inlet I1C and is communicated with a vertical oil duct I1D in the box body 1, the vertical oil duct I1D is communicated with an oil hole axially arranged on an outer spacer 12 between the rolling bearing 3, the diameter of an inner hole of a positioning sleeve I6 is larger than the outer diameter of the main shaft 2, and the oil inlet I1C is communicated with an oil outlet of an oil supply circulating system through a pipeline to lubricate the rolling bearing 3;
the upper portion of the box body 1 near the shaft end is provided with an oil inlet hole II 1E and communicated with a vertical oil duct II 1F in the box body 1, the vertical oil duct II 1F is communicated with an oil supply groove in the outer circular surface of the dynamic and static pressure bearing 5, and the oil inlet hole II 1E is communicated with an oil supply port of a high-pressure oil supply system through a pipeline.
As shown in fig. 7 and 9, a counter bore iii is provided on the outer side of the bearing cap ii 9, an annular lip 9A which is coaxial with the main shaft 2 and extends outward is provided on the end face of the counter bore iii, the main shaft 2 is further fixedly provided with a moving ring seat 13 on the outer side of the bearing cap ii 9, an annular groove 13A is provided on the end face of the inner side of the moving ring seat 13, and the annular lip 9A extends into the annular groove 13A and forms a gap seal.
The outer circular surface of the movable ring seat 13 close to the outer side is provided with a large ring platform 13B, the annular groove 13A is formed in the end surface of the inner side of the large ring platform 13B, the outer circular surface of the large ring platform 13B is in clearance fit with a counter bore III of the bearing cover II 9, and/or the outer circular surface of the movable ring seat 13 close to the inner side is in clearance fit with an inner hole of the bearing cover II 9.
The outer circular surface of the large circular platform 13B is provided with a circumferential chip groove I13C, and a circumferential chip groove II 14 is formed between the inner circular surface of the movable circular seat 13 close to the inner side and the inner hole of the bearing cover II 9.
The sealing lip I10A of the framework oil seal I10 is in interference fit sealing with the outer circular surface of the main shaft 2, or a step I is arranged on the main shaft 2 on the inner side of the bearing cover I8, a sealing seat I15 abutting against the step I is fixedly arranged on the outer circle of the main shaft 2, and the sealing lip I10A of the framework oil seal I10 is in interference fit sealing with the outer circular surface of the sealing seat I15; the outer disc interference fit of II 11A of the sealing lip of II 11 of skeleton oil blanket and main shaft 2, perhaps be provided with step II on the inboard main shaft 2 of rotating ring seat 13, fixed sealing seat II 16 that is provided with butt step II on the excircle of main shaft 2, the outer disc interference fit of II 11A of the sealing lip of II 11 of skeleton oil blanket and sealing seat II 16 is sealed.
As shown in fig. 7 and 8, the spindle 2 is provided with a adapter sleeve 17 in threaded engagement on the outer circle of the outer side of the seal seat i 15, the inner side surface of the adapter sleeve 17 abuts against the seal seat i 15, and the diameter of the outer circle is smaller than the inner diameter of the bearing cover i 8; the bearing cover I8 is characterized in that a dust cover 18 is detachably and fixedly arranged in a counter bore in the outer side of the bearing cover I8, and the inner side of the dust cover 18 extends towards the spindle 2 and is in clearance fit with the outer side face of the adapter sleeve 17.
As shown in fig. 10, 11 and 12, the hybrid bearing 5 includes a body 5A, oil grooves 5B, oil return grooves 5C, and oil guide holes 5D, where the body 5A is a circular structure and a plurality of oil grooves 5B are uniformly axially distributed on an inner circle, the oil return grooves 5C are axially disposed between adjacent oil grooves 5B on the inner circle of the body 5A and at least one end of each oil return groove 5C penetrates through an end surface of the body 5A or communicates with an oil return passage disposed in the body 5A, and the oil guide holes 5D are radially disposed on the body 5A and one end of each oil guide hole is communicated with the oil grooves 5B; the oil groove is characterized in that axially extending V-shaped grooves 5E are formed in the oil groove 5B at intervals along the circumferential direction, oil guide grooves 5F for communicating the adjacent V-shaped grooves 5E are further formed in the oil groove 5B along the circumferential direction, at least one V-shaped groove 5E and/or oil guide groove 5F is communicated with the oil guide hole 5D in the oil groove 5B, the groove top surface of the oil groove 5B is communicated with the oil return groove 5C through the inner surface of the body 5A in the circumferential direction, and the groove top surface of the oil groove 5B is in clearance fit with the outer circular surface of the main shaft 2.
At least three V-shaped grooves 5E are arranged in the oil groove 5B, the oil guide grooves 5F are circumferentially arranged at two ends of the oil groove 5B, and one V-shaped groove 5E in the oil groove 5B or the oil guide groove 5F at one side is communicated with the oil guide hole 5D; an inner arc rectangular surface 5G is formed between adjacent V-shaped grooves 5E in the oil groove 5B, and the diameter of the inner arc rectangular surface 5G is not less than that of the inner circular surface of the body 5A.
Circumferential oil collecting grooves 5H are formed in the two axial outer sides of the oil groove 5B on the inner circular surface of the body 5A respectively, and two ends of each oil collecting groove 5H are communicated with the adjacent oil return grooves 5C respectively; an outer ring groove 5J is circumferentially arranged on the outer circle of the body 5A, the outer ring groove 5J is communicated with an oil supply system, a plurality of throttling platforms 5K are arranged inside the outer ring groove 5J at intervals along the circumferential direction, an oil inlet of the oil guide hole 5D is formed in the middle of the top face of each throttling platform 5K, and the top face of each throttling platform 5K is lower than the outer circular face of the body 5A.
The throttling table 5K is of an outer arc rectangular surface structure, the outer diameter of the throttling table is smaller than that of the outer circular surface of the body 5A, oil supply grooves 5M are formed in two sides of the outer circular groove 5J of the throttling table 5K, and sealing grooves 5N are circumferentially formed in two axial ends of the outer circular groove 5J of the body 5A.
The working principle and the working process of the invention are as follows:
as shown in fig. 1 to 12, before the machine tool spindle is started, the oil pump is started and the high-pressure oil supply system connected to the hybrid bearing 5 is connected. The bearing oil film formed under the hydrostatic pressure in the V-shaped groove 5E of the hybrid bearing supports the main shaft 2, so that the main shaft 2 is separated from the inner hole of the hybrid bearing 5 and is suspended in the oil film, and the contact abrasion of the main shaft 2 and the inner hole of the hybrid bearing 5 is avoided; meanwhile, lubricating oil flows into the rolling bearing 3 from the oil inlet I through an oil hole axially arranged on the outer spacer bush 12 to lubricate the rolling bearing 3, and redundant lubricating oil flows back into the oil pool 1A from a gap between the transverse through groove on the positioning bush I6 and the outer diameter of the main shaft 2. After the main shaft 2 rotates, high-pressure oil in the dynamic and static pressure bearing 5 flows from the deep part to the shallow part of the V-shaped groove 5E to form an oil wedge dynamic pressure effect, the dynamic pressure effect in the V-shaped groove 5E is gradually increased along with the increase of the rotating speed, and the dynamic pressure effect and the static pressure of the oil in the V-shaped groove 5E are used for bearing the main shaft and the external load together; under the high-speed working condition, oil in the oil groove 5B automatically flows back to the adjacent and even farther low-pressure V-shaped groove 5E from the high-pressure V-shaped groove 5E, the automatic balance and the oil temperature uniformity of the high-pressure oil and the low-pressure oil in the oil groove 5B are achieved, meanwhile, the bearing capacity and the rigidity of the oil film in the hybrid bearing 5 are greatly improved, the oil film can also well play a role in homogenizing manufacturing errors, and the overall performance of the hybrid bearing 5 can be greatly improved under the combined action of the hybrid effect of the dynamic pressure and the static pressure. The outer ring groove 5J and the throttle platform 5K outside the body 5A are structured, so that a small gap can be formed between the outer circular surface of the throttle platform 5K and the spindle hole 1B during working, oil flowing to the oil guide hole 5D is blocked to form a throttling effect, and the oil damping in the oil groove 5B is increased, so that the capability of resisting the speed disturbance of the rotating shaft is improved, the rotating precision is increased, and the shock absorption and the noise reduction are facilitated; after the main shaft 2 rotates, the rolling bearing 3 can fully lubricate the rolling bearing 3 and take away heat generated by friction under the continuous oil supply of external lubricating oil, so that the service life of the rolling bearing 3 is prolonged, and the lubricating oil circulates through the vertical oil duct I1D in the box body 1, the rolling bearing 3 and the clearance on the main shaft 2, so that the overall thermal stability of the main shaft system can be effectively improved, and the output precision of a machine tool is ensured.
And during operation, the framework oil seal I10 outside the rolling bearing 3 can meet the sealing requirement of normal pressure lubricating oil in the rolling bearing 3, especially, a sealing lip I10A fixedly arranged on the main shaft 2 and provided with a sealing seat I15 and the framework oil seal I10 forms a friction pair, only the worn sealing seat I15 and/or the framework oil seal I10 need to be replaced after long-time use, and the abrasion and scrapping of the main shaft 2 caused by the direct interference fit of the sealing lip I10A and the main shaft 2 are avoided. The non-contact labyrinth seal is arranged on the outer side of the hybrid bearing, so that the sealing protection capability of the outer side of the hybrid bearing is further improved in a targeted manner, the protection capability of foreign matters on the outer side entering the bearing is improved, and the phenomenon that the heating is increased and the structure is complicated due to the increase of the seal can be avoided.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (10)
1. A high-bearing large dynamic horizontal type hybrid main shaft system comprises a box body (1), a main shaft (2), a rolling bearing (3) and a hybrid bearing (5), it is characterized in that the middle part of the box body (1) along the length direction is provided with an oil pool (1A), a main shaft hole (1B) penetrating through both ends and the oil pool (1A) is transversely arranged on the box body (1), a positioning sleeve I (6) and a positioning sleeve II (7) are respectively and fixedly arranged on two sides of the main shaft hole (1B) close to the oil pool (1A), the rolling bearings (3) are fixedly arranged in a main shaft hole (1B) close to the driving end in a matching way, the outer ring of the bearing close to the oil sump (1A) side of the paired rolling bearings (3) is abutted with the positioning sleeve I (6), and the outer ring of the bearing far away from the oil sump (1A) side is abutted with a bearing cover I (8) fixedly arranged on the end face of the box body (1); the hybrid bearing (5) is fixedly arranged in a main shaft hole (1B) close to the shaft head end, the side close to an oil pool (1A) of the hybrid bearing (5) is abutted with the positioning sleeve II (7), and the outer side far away from the side is abutted with a bearing cover II (9) fixedly arranged on the end face of the box body (1); one side of the main shaft (2) is in interference fit with an inner ring inner hole of the rolling bearing (3), and the other side of the main shaft is in clearance fit with an inner hole of the dynamic and static pressure bearing (5);
the spindle is characterized by further comprising a framework oil seal I (10) and a framework oil seal II (11), wherein the framework oil seal I (10) is fixedly arranged in a counter bore I on the inner side of the bearing cover I (8), a sealing lip I (10A) extends towards the spindle (2) to form interference fit sealing, the framework oil seal II (11) is fixedly arranged in a counter bore II on the inner side of the bearing cover II (9), and the sealing lip II (11A) extends towards the spindle (2) to form interference fit sealing;
an oil inlet I (1C) is formed in the upper portion, close to the driving end, of the box body (1) and is communicated with a vertical oil duct I (1D) in the box body (1), the vertical oil duct I (1D) is communicated with an oil hole axially formed in an outer spacer sleeve (12) between the rolling bearings (3), the diameter of an inner hole of the positioning sleeve I (6) is larger than the outer diameter of the main shaft (2), and the oil inlet I (1C) is communicated with an oil outlet of an oil supply circulating system through a pipeline to lubricate the rolling bearings (3);
the upper portion of box (1) near-shaft head end is provided with inlet port II (1E) and with II (1F) intercommunications of vertical oil duct in box (1), oil feed groove intercommunication on II (1F) of vertical oil duct and the outer disc of hybrid bearing (5), inlet port II (1E) and high-pressure oil feeding system's oil feed mouth pass through the pipeline intercommunication.
2. The high-bearing large dynamic horizontal type hybrid spindle system according to claim 1, wherein a counter bore iii is arranged on the outer side of the bearing cover ii (9), an annular lip (9A) which is coaxial with the spindle (2) and extends outwards is arranged on the end face of the counter bore iii, a moving ring seat (13) is further fixedly arranged on the outer side of the bearing cover ii (9) of the spindle (2), an annular groove (13A) is arranged on the end face of the inner side of the moving ring seat (13), and the annular lip (9A) extends inwards the annular groove (13A) and forms a gap seal.
3. The high-bearing large dynamic horizontal type hybrid spindle system according to claim 2, wherein a large ring table (13B) is disposed on an outer circumferential surface of the movable ring seat (13) close to the outer side, the annular groove (13A) is disposed on an inner end surface of the large ring table (13B), and an outer circumferential surface of the large ring table (13B) is in clearance fit with a counter bore iii of the bearing cover ii (9) and/or an outer circumferential surface of the movable ring seat (13) close to the inner side is in clearance fit with an inner bore of the bearing cover ii (9).
4. The high-bearing large dynamic horizontal type hybrid spindle system according to claim 3, wherein a circumferential chip pocket I (13C) is formed in an outer circumferential surface of the large annular table (13B), and a circumferential chip pocket II (14) is formed between an inner-side outer circumferential surface of the movable annular base (13) and an inner hole of the bearing cover II (9).
5. The high-bearing large dynamic horizontal hybrid spindle system according to claim 2, wherein a sealing lip I (10A) of the framework oil seal I (10) is in interference fit sealing with the outer circular surface of the spindle (2), or a step I is arranged on the spindle (2) on the inner side of the bearing cover I (8), a sealing seat I (15) abutting against the step I is fixedly arranged on the outer circle of the spindle (2), and the sealing lip I (10A) of the framework oil seal I (10) is in interference fit sealing with the outer circular surface of the sealing seat I (15); the sealing lip II (11A) of skeleton oil blanket II (11) is sealed with the outer disc interference fit of main shaft (2), perhaps is provided with step II on main shaft (2) of rotating ring seat (13) inboard, fixed sealing seat II (16) that are provided with butt step II on the excircle of main shaft (2), the sealing lip II (11A) of skeleton oil blanket II (11) is sealed with the outer disc interference fit of sealing seat II (16).
6. The high-bearing large dynamic horizontal type hybrid spindle system according to claim 5, wherein the spindle (2) is provided with a adapter sleeve (17) in threaded engagement on the outer circle of the outer side of the seal seat I (15), the inner side surface of the adapter sleeve (17) is abutted against the seal seat I (15) and the diameter of the outer circle is smaller than the inner diameter of the bearing cover I (8); the bearing cover is characterized in that a dustproof cover (18) is detachably and fixedly arranged in a counter bore in the outer side of the bearing cover I (8), and the inner side of the dustproof cover (18) extends towards the main shaft (2) and is in clearance fit with the outer side face of the adapter sleeve (17).
7. The high-bearing large dynamic horizontal type dynamic and static main shaft system according to any one of claims 1 to 6, wherein the dynamic and static bearing (5) comprises a body (5A), oil grooves (5B), oil return grooves (5C) and oil guide holes (5D), the body (5A) is of a circular ring structure, a plurality of oil grooves (5B) are axially and uniformly distributed on the inner circle of the body (5A), the oil return grooves (5C) are axially arranged between adjacent oil grooves (5B) on the inner circle of the body (5A), at least one end of each oil return groove penetrates through the end face of the body (5A) or is communicated with an oil return channel arranged in the body (5A), and the oil guide holes (5D) are radially arranged on the body (5A) and one end of each oil guide hole is communicated with the oil grooves (5B); the oil groove is characterized in that axially extending V-shaped grooves (5E) are formed in the oil groove (5B) at intervals along the circumferential direction, oil guide grooves (5F) communicated with adjacent V-shaped grooves (5E) are further formed in the oil groove (5B) along the circumferential direction, at least one V-shaped groove (5E) and/or one oil guide groove (5F) in the oil groove (5B) is communicated with the oil guide hole (5D), the groove top surface of the oil groove (5B) is communicated with the oil return groove (5C) through the inner surface of the body (5A) in the circumferential direction, and the groove top surface of the oil groove (5B) is in clearance fit with the outer circular surface of the main shaft (2).
8. The high-load-bearing large dynamic horizontal type hybrid spindle system according to claim 7, wherein at least three "V" shaped grooves (5E) are provided in the oil groove (5B), the oil guide grooves (5F) are circumferentially provided at both ends of the oil groove (5B), one "V" shaped groove (5E) in the oil groove (5B) or the oil guide groove (5F) at one side is communicated with the oil guide hole (5D); an inner arc rectangular surface (5G) is formed between adjacent V-shaped grooves (5E) in the oil groove (5B), and the diameter of the inner arc rectangular surface (5G) is not less than that of the inner circular surface of the body (5A).
9. The high-bearing large dynamic horizontal dynamic and static pressure main shaft system according to claim 8, wherein the inner circular surface of the main body (5A) is provided with circumferential oil collecting grooves (5H) at two axial outer sides of the oil groove (5B), and two ends of the oil collecting groove (5H) are respectively communicated with the adjacent oil return grooves (5C); the oil supply device is characterized in that an outer ring groove (5J) is circumferentially arranged on the outer circle of the body (5A), the outer ring groove (5J) is communicated with an oil supply system, a plurality of throttling tables (5K) are circumferentially arranged inside the outer ring groove (5J) at intervals, an oil inlet of the oil guide hole (5D) is formed in the middle of the top face of each throttling table (5K), and the top face of each throttling table (5K) is lower than the outer circular face of the body (5A).
10. The high-bearing large dynamic horizontal type hybrid spindle system according to claim 9, wherein the throttling table (5K) is of an outer arc rectangular surface structure, the outer diameter of the throttling table is smaller than the outer diameter of the outer circular surface of the body (5A), the outer circular groove (5J) is provided with oil supply grooves (5M) on two sides of the throttling table (5K), and the outer circular surface of the body (5A) is respectively provided with sealing grooves (5N) circumferentially at two axial ends of the outer circular groove (5J).
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| CN202210741530.6A CN114799238B (en) | 2022-06-28 | 2022-06-28 | High-bearing large dynamic horizontal dynamic and static pressure main shaft system |
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