Rotating shaft system with high bearing capacity

Abstract

The utility model provides a rotating shaft system, which comprises a rotating shaft, a bearing body and a bearing shell, a constant pressure bearing area is arranged in the middle of the bearing body, and a constant flow bearing area is arranged at the end part of the bearing body; the constant-flow bearing area is provided with a bending moment load bearing cavity, and the constant-pressure bearing area is provided with a radial load bearing cavity; an oil discharging groove is formed between the bending moment load bearing cavity and the radial load bearing cavity. The utility model has the advantages of being suitable for the environment of deep and long rotating shaft and large inclination deformation, strong in bearing capacity and the like.

Description

Technical Field

[0001] The utility model relates to the field of shaft bearing, in particular to a shaft system with high bearing capacity. Background Art

[0002] The existing load-bearing bearings are mainly divided into two types: static pressure bearings and dynamic pressure bearings. Compared with dynamic pressure bearings, static pressure bearings rely on the pressure of an external oil pump to carry loads. They have the advantages of high rotation accuracy, long life, good vibration resistance, and low power consumption. They are widely used in precision machine tool spindles. Static pressure bearings can be divided into two categories according to the way high-pressure oil is supplied: 1. Constant flow bearings. Constant flow bearings are provided with a fixed flow of lubricating oil in each oil chamber by a metering pump. The pressure can be changed according to the external load, and the load-bearing capacity is strong. However, each oil chamber of the constant flow bearing needs to be equipped with a constant flow pump and a control valve separately. Its structure is complex, occupies a large space, is costly, and is rarely used; 2. Constant pressure bearings. The pump supplies oil to the bearing at a constant oil supply pressure. The oil enters the corresponding high-pressure oil chamber after passing through the throttle to form the oil chamber pressure. Its oil supply structure is simple, the cost is low, and it is widely used.

[0003] As the application environment of the shaft system becomes more complex and diverse (such as photon slicers, etc.), the shaft depth is set longer and longer, and the requirements for rotation accuracy and load-bearing capacity are also getting higher and higher. However, the existing bearings cannot meet the requirements of high rotation accuracy and high load-bearing capacity of the shaft. During operation, the shaft is prone to large tilt deformation and large bending moment load attached to the bearing, which makes the bearing unable to effectively bear the load and the position with large bearing clearance is prone to pressure release, causing the bearing edge sweeping and burning, and the safety and reliability of the shaft system is poor. In order to solve the above problems, the existing method is usually to set the constant pressure bearing in a double-row form, but the double-row load of the constant pressure bearing increases the load on the inner side of the bearing, and its load-bearing capacity still cannot meet the load-bearing requirements of the environment with long shaft depth and large deformation, and it is also prone to high temperature failure at high speed. Utility Model Content

[0004] The technical problem to be solved by the utility model is to overcome the deficiencies of the prior art and provide a shaft system with high load-bearing capacity, which is suitable for environments with deep and long shafts, large tilting and deformation, strong load-bearing capacity and simple structure.

[0005] In order to solve the above technical problems, the technical solution proposed by the utility model is:

[0006] A rotating shaft system with high load-bearing capacity comprises a rotating shaft, a bearing body sleeved on the shaft journal, and a bearing shell sleeved outside the bearing body, wherein a constant-pressure bearing area is provided in the middle of the bearing body, and a constant-flow bearing area is provided in the end area of ​​the bearing body that bears the shaft bending moment load; the constant-flow bearing area is provided with a moment load bearing cavity that provides a force opposite to the shaft bending moment load, and the constant-pressure bearing area is provided with radial load bearing cavities that are arranged at intervals along the circumference of the bearing body; an oil unloading groove is provided between the moment load bearing cavity and the radial load bearing cavity to prevent the oil in adjacent cavities from interfering with each other.

[0007] As a further improvement of the above technical solution:

[0008] It also includes a constant-flow oil supply channel and a constant-pressure oil supply channel, the constant-flow oil supply channel includes a constant-flow oil supply section provided on the bearing housing, and a constant-flow oil supply ring groove provided on the outer surface of the bearing body, the constant-flow oil supply section is connected with the moment load bearing cavity through the constant-flow oil supply ring groove; the constant-pressure oil supply channel includes a constant-pressure oil supply section provided on the bearing housing, and a constant-pressure oil supply ring groove provided on the outer surface of the bearing body, the constant-pressure oil supply section is connected with the radial load bearing cavity through the constant-pressure oil supply ring groove.

[0009] It also includes an end unloading oil return channel and an internal oil return channel, the oil inlet of the end unloading oil return channel is arranged at the two ends of the bearing shell and located on both axial sides of the bearing body; the internal oil return channel includes an oil collecting ring groove and an internal oil return section that are interconnected, the oil collecting ring groove is arranged on the inner surface of the end of the bearing body close to the bearing end of the rotating shaft and is located on the axial outside of the constant flow bearing area, and the internal oil return section is arranged on the bearing shell.

[0010] The oil unloading groove is an annular oil unloading groove, and the annular oil unloading groove close to the bearing end of the rotating shaft is communicated with the internal oil return section.

[0011] The oil inlet of the constant flow oil supply section, the oil inlet of the constant pressure oil supply section, the oil outlet of the end unloading oil return channel and the oil outlet of the internal oil return section are arranged on the end surface of the bearing body.

[0012] The area at the end of the bearing body that does not bear the bending moment load of the rotating shaft is a non-load-bearing flow zone, the inner diameter of the constant flow bearing zone is the same as the outer diameter of the rotating shaft, and the inner diameter of the non-load-bearing flow zone is larger than the outer diameter of the rotating shaft; the non-load-bearing flow zone and the constant flow bearing zone are connected by a conical transition section to enclose the inner ring of the end of the bearing body.

[0013] The rotating shaft system also includes a ventilation component for preventing external impurities and dust from entering the bearing housing. The ventilation component includes a ventilation channel arranged on the bearing body, and one end of the ventilation channel away from the bearing end of the rotating shaft is connected to an air source.

[0014] The moment load bearing cavity is communicated with the constant flow oil supply ring groove through a radial constant flow channel; the radial load bearing cavity is communicated with the constant pressure oil supply ring groove through a radial constant pressure channel, and the radial constant pressure channel is provided with a throttle.

[0015] Compared with the prior art, the advantages of the utility model are:

[0016] The utility model applies the combination of a constant pressure bearing and a constant flow bearing to a rotating shaft system for the first time, that is, a constant pressure bearing area is provided in the middle of the bearing body, a constant flow bearing area is provided in the end of the bearing body in an area that bears the bending moment load of the rotating shaft, the constant flow bearing area is provided with a bending moment load bearing cavity, and the constant pressure bearing area is provided with radial load bearing cavities arranged at intervals along the circumference of the bearing body, so that the constant pressure bearing and the constant flow bearing are integrated in the same bearing body, and the structure is simple, compact and low in cost.

[0017] At the same time, the radial load and bending moment load of the rotating shaft of the utility model can be carried separately and independently according to the load and bearing properties. That is, the constant pressure bearing area with simple structure and convenient control is used to bear the radial load of the normal load of the rotating shaft; the bending moment load bearing cavity of the constant flow bearing area is used to provide the opposite force of the bending moment load of the rotating shaft. At this time, the constant flow bearing area with high load capacity bears the large bending moment load caused by the deep and long shaft and large deformation of the rotating shaft, which solves the problem that the double-row constant pressure bearing cannot bear the large bending moment load and high temperature of the rotating shaft. While ensuring the high load capacity of the bearing and the high rotation accuracy requirements of the rotating shaft under the deep and long shaft and large deformation environment, it effectively saves costs.

[0018] Since the constant flow bearing area only bears the moment load of the rotating shaft, the load it bears is greatly reduced compared with the existing constant flow bearing, and the constant flow bearing can be reduced to only bear the moment load accordingly. At this time, the constant flow bearing area only needs to be set at the position where the bearing body bears the moment load to bear the large moment load of the rotating shaft. The reduction in the number of constant flow bearing areas greatly reduces the axial size of the constant flow bearing and simplifies the structure of the constant flow bearing, which effectively solves the problem of complex structure and limited application of the existing constant flow bearing.

[0019] At the same time, an oil unloading groove is provided between the moment load bearing cavity and the radial load bearing cavity, so that the lubricating oil in the constant flow bearing area and the constant pressure bearing area can be unloaded from the oil unloading groove, thereby avoiding the problem of mutual interference between the constant flow bearing area and the constant pressure bearing area during load bearing, and ensuring the effective bearing of the radial load and moment load of the rotating shaft.

[0020] The combination of the constant pressure bearing and the constant flow bearing of the utility model can effectively withstand the large bending moment and radial load of the rotating shaft, and has a simple structure and low cost. It avoids the occurrence of bearing edge sweeping and shoe burning, ensures the high load-bearing and high rotation accuracy requirements of the rotating shaft system, and greatly improves the safety and reliability of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The present invention will be described in more detail below based on embodiments and with reference to the accompanying drawings.

[0022] Figure 1 It is a three-dimensional structural diagram of the rotating shaft system of the utility model;

[0023] Figure 2 It is a cross-sectional view of the shaft system of the utility model;

[0024] Figure 3 is another cross-sectional view of the shaft system of the utility model (the shaft is not shown);

[0025] Figure 4 yes Figure 1 Right view of;

[0026] Figure 5 yes Figure 4 A cross-sectional view of section AA;

[0027] Figure 6 yes Figure 4 A cross-sectional view of the FF section;

[0028] Figure 7 yes Figure 5 A cross-sectional view of the BB section;

[0029] Figure 8 yes Figure 4 A cross-sectional view of the GG section;

[0030] Fig. 9 yes Figure 5 A cross-sectional view of the CC section;

[0031] Fig.10 yes Figure 4 A cross-sectional view of the EE section;

[0032] Fig.11 yes Figure 5 A cross-sectional view of the DD section;

[0033] Fig.12 yes Figure 4 A cross-sectional view of the LL section;

[0034] Fig.13 yes Figure 4 A cross-sectional view of the MM section;

[0035] The symbols in the figure represent:

[0036] 1. Rotating shaft; 2. Bearing body; 21. Constant pressure bearing area; 211. Radial load bearing cavity; 22. Constant flow bearing area; 221. Moment load bearing cavity; 23. Oil unloading groove; 231. Annular oil unloading groove; 24. Non-load flow area; 25. Conical transition section; 3. Bearing housing; 4. Constant flow oil supply channel; 41. Constant flow oil supply section; 411. Oil inlet of constant flow oil supply section; 42. Constant flow oil supply ring groove; 43. Radial 1. Directional constant flow channel; 5. Constant pressure oil supply channel; 51. Constant pressure oil supply section; 511. Oil inlet of constant pressure oil supply section; 52. Constant pressure oil supply ring groove; 53. Radial constant pressure channel; 6. End unloading oil return channel; 61. Oil outlet of end unloading oil return channel; 7. Internal oil return channel; 71. Oil collecting ring groove; 72. Internal oil return section; 721. Oil outlet of internal oil return section; 8. Ventilation assembly; 81. Ventilation channel; 9. Throttle. DETAILED DESCRIPTION

[0037] The present invention will be further described in detail below in conjunction with the accompanying drawings and specific embodiments of the specification, but the protection scope of the present invention is not limited thereby.

[0038] Figures 1 to 13 The embodiment of the shaft system with high load-bearing capacity of the utility model is shown. The shaft system of the utility model can be applied to special occasions where the shaft 1 is deep and long and has large tilt deformation, such as a photon slicer. The shaft system of the utility model comprises a shaft 1, a bearing body 2 and a bearing housing 3. One end of the shaft 1 is connected to an external load-bearing component (such as a photon slicer), the bearing body 2 is sleeved on the journal of the shaft 1, and the bearing housing 3 is sleeved outside the bearing body 2.

[0039] In this embodiment, a constant pressure bearing area 21 is provided in the middle of the bearing body 2, and a radial load bearing cavity 211 is provided in the constant pressure bearing area 21, and a plurality of radial load bearing cavities 211 are arranged at intervals along the circumference of the bearing body 2. A constant flow bearing area 22 is provided in the end of the bearing body 2 in the area that bears the moment load of the rotating shaft 1, and a moment load bearing cavity 221 is provided in the constant flow bearing area 22, and the moment load bearing cavity 221 provides an opposite force to the moment load of the rotating shaft 1 to offset the moment load of the rotating shaft 1. The utility model applies the combination of a constant pressure bearing and a constant flow bearing to a rotating shaft system for the first time, so that the constant pressure bearing and the constant flow bearing are integrated in the same bearing body 2, and the structure is simple, compact and low in cost.

[0040] At the same time, the radial load and bending moment load of the rotating shaft 1 of the utility model can be independently borne according to the load and the properties of the bearing, that is, a constant pressure bearing area 21 with a simple structure and convenient control is used to bear the radial load of the normal load of the rotating shaft 1; a bending moment load bearing cavity 221 is used to provide a force opposite to the bending moment load of the rotating shaft 1. At this time, the constant flow bearing area 22 with high load-bearing capacity bears the large bending moment load caused by the deep shaft and large deformation of the rotating shaft 1, which solves the problem that the double-row constant pressure bearings cannot withstand the large bending moment load and high temperature of the rotating shaft 1, and effectively saves costs while ensuring the high load-bearing capacity of the bearing and the high rotation accuracy requirements of the rotating shaft 1 under the environment of deep shaft and large deformation.

[0041] Since the constant flow bearing area 22 only bears the moment load of the rotating shaft 1, the load it bears is greatly reduced compared with the existing constant flow bearing, and the constant flow bearing can be reduced to only bear the moment load accordingly. At this time, the constant flow bearing area 22 only needs to be set at the position where the bearing body 2 bears the moment load to bear the large moment load of the rotating shaft 1. The reduction in the number of constant flow bearing areas 22 greatly reduces the axial size of the constant flow bearing and simplifies the structure of the constant flow bearing, which effectively solves the problem of complex structure and limited application of the existing constant flow bearing.

[0042] At the same time, an oil unloading groove 23 is provided between the moment load bearing cavity 221 and the radial load bearing cavity 211 to prevent the oil in the adjacent moment load bearing cavity 221 and the radial load bearing cavity 211 from interfering with each other, so that the oil in the constant flow bearing area 22 and the constant pressure bearing area 21 can be unloaded from the oil unloading groove 23, avoiding the problem of mutual interference between the constant flow bearing area 22 and the constant pressure bearing area 21 when bearing, and ensuring the effective bearing of the radial load and the moment load of the rotating shaft 1.

[0043] The combined arrangement of the constant pressure bearing and the constant flow bearing of the utility model is simple in structure and low in cost while effectively bearing the large bending moment and radial load of the rotating shaft 1. It avoids the occurrence of bearing edge sweeping and shoe burning, ensures the high load-bearing and high rotation accuracy requirements of the rotating shaft system, and greatly improves the safety and reliability of the system.

[0044] like Figure 2 , Figure 3 and Figure 5 As shown, there are two constant flow bearing areas 22, and the two constant flow bearing areas 22 are arranged on both sides of the constant pressure bearing area 21. The two constant flow bearing areas 22 can respectively bear the large bending moment loads generated by the tilt deformation on both sides of the rotating shaft 1, and the constant pressure bearing area 21 in the middle of the rotating shaft 1 can effectively bear the radial load of the rotating shaft 1, which makes the rotating shaft 1 always float in the pressure oil when the rotating shaft 1 is deep and long and deformed greatly, forming a strong rigidity dynamic pressure oil film to ensure the safe and reliable operation of the rotating shaft system. In other embodiments, the number of constant flow bearing areas 22 and constant pressure bearing areas 21 can be adjusted and set according to the load-bearing requirements of the rotating shaft 1, as long as the bending moment and radial load of the rotating shaft 1 can be effectively carried.

[0045] In this embodiment, the bearing end of the rotating shaft 1 connected to the external bearing component is the left end, and the external bearing component provides the upward load of the rotating shaft 1. At this time, the bearing end of the rotating shaft 1 is tilted upward, and the area of ​​the bearing body 2 that bears the bending load of the rotating shaft 1 at the bearing end of the rotating shaft 1 is located at the inner top of the bearing body 2. Therefore, the constant flow bearing area 22 located at the bearing end of the rotating shaft 1 is arranged at the inner top of the bearing body 2; at the same time, the non-bearing end (right end) of the rotating shaft 1 is tilted downward, and the area of ​​the bearing body 2 that bears the bending load of the rotating shaft 1 at the non-bearing end of the rotating shaft 1 is located at the inner bottom of the bearing body 2. Therefore, the constant flow bearing area 22 located at the non-bearing end of the rotating shaft 1 is arranged at the inner bottom of the bearing body 2. This allows the large bending moment generated on both sides of the tilt of the rotating shaft 1 to be borne by the constant flow bearing area 22. At the same time, the moment load bearing cavity 221 can change the bearing pressure according to the external load. The moment load bearing cavity 221 opens when the external load reaches a certain level, and it has a strong bearing capacity for the large bending moment of the rotating shaft 1.

[0046] In other embodiments, the setting position of the constant flow bearing area 22 in the bearing body 2 is set according to the movement direction of the external load-bearing component, and it is necessary to ensure that the setting position of the constant flow bearing area 22 is located in the area of ​​the bearing body 2 that bears the bending moment load of the rotating shaft 1. If the external load-bearing component provides a downward load on the rotating shaft 1, the end of the rotating shaft 1 close to the external load-bearing component is tilted downward. At this time, the constant flow bearing area 22 located on the load-bearing end side of the rotating shaft 1 is set at the inner bottom end of the bearing body 2, and the constant flow bearing area 22 located at the non-load-bearing end of the rotating shaft 1 is set at the inner top end of the bearing body 2; similarly, if the external load-bearing component provides a horizontal load on the rotating shaft 1, the two ends of the rotating shaft 1 generate horizontal movement. At this time, the constant flow bearing areas 22 at both ends of the bearing body 2 are respectively set on the horizontal sides of the bearing body 2 to offset the horizontal bending moment load of the rotating shaft 1.

[0047] In other embodiments, the number of constant flow bearing areas 22 at both ends of the rotating shaft 1 can also be set to two, and the two constant flow bearing areas 22 are symmetrically arranged in the radial direction of the bearing body 2, which enables the upper and lower sides of the rotating shaft 1 to have bearing pressure, thereby realizing large bending moment bearing of the rotating shaft 1.

[0048] Furthermore, if Figures 4 to 13As shown, the shaft system also includes a constant flow oil supply channel 4 and a constant pressure oil supply channel 5. The constant flow oil supply channel 4 includes a constant flow oil supply section 41 and a constant flow oil supply ring groove 42. The constant flow oil supply section 41 is provided on the bearing housing 3, and the constant flow oil supply ring groove 42 is provided on the outer surface of the bearing body 2. The constant flow oil supply section 41 is connected to the moment load bearing cavity 221 through the constant flow oil supply ring groove 42. The constant pressure oil supply channel 5 includes a constant pressure oil supply section 51 and a constant pressure oil supply ring groove 52. The constant pressure oil supply section 51 is provided on the bearing housing 3, and the constant pressure oil supply ring groove 52 is provided on the outer surface of the bearing body 2. The constant pressure oil supply section 51 is connected to the radial load bearing cavity 211 through the constant pressure oil supply ring groove 52. Its oil supply structure is simple and compact, and the oil can be effectively transported to the constant flow bearing area 22 and the constant pressure bearing area 21 to ensure the bearing effect.

[0049] At the same time, the setting of the constant flow oil supply ring groove 42 makes the setting position of the moment load bearing cavity 221 and the constant flow oil supply section 41 adjustable, thereby ensuring that the position of the moment load bearing cavity 221 can be flexibly adjusted according to the area of ​​the bearing body 2 that bears the moment load of the rotating shaft 1, and the setting position of the constant flow oil supply section 41 in the bearing body 2 can also be flexibly adjusted according to the actual layout requirements. Similarly, the setting of the constant pressure oil supply ring groove 52 makes the setting position of the radial load bearing cavity 211 and the constant pressure oil supply section 51 adjustable, thereby ensuring that the setting number and position of the radial load bearing cavity 211 can be flexibly adjusted according to the requirement of the bearing body 2 to bear the radial load of the rotating shaft 1, and the setting position of the constant pressure oil supply section 51 in the bearing body 2 can also be flexibly adjusted according to the actual layout requirements.

[0050] Furthermore, the shaft system also includes an end unloading oil return channel 6 and an internal oil return channel 7. Figure 5 As shown, the oil inlet of the end unloading oil return channel 6 is arranged at the two ends of the bearing housing 3, and the oil inlet of the end unloading oil return channel 6 is located on both sides of the axial direction of the bearing body 2, which allows the oil in the constant pressure bearing area 21 and the constant flow bearing area 22 to be discharged through the end unloading oil return channel 6 when flowing into the bearing boxes on both sides of the bearing body 2, which avoids the occurrence of the phenomenon that the bearing box is overfilled with oil and affects the safe operation of the shaft system. Fig.12 As shown, the internal oil return channel 7 includes an oil collecting ring groove 71 and an internal oil return section 72 which are interconnected. The oil collecting ring groove 71 is provided on the inner surface of the end of the bearing body 2 close to the bearing end of the rotating shaft 1, and the oil collecting ring groove 71 is located axially outside the constant flow bearing area 22. The internal oil return section 72 is provided on the bearing housing 3, which enables the oil flowing to the bearing body 2 in the bearing end position where the rotating shaft 1 is stressed and has a large load to be discharged in time, thereby improving the heat dissipation and cooling effect of the bearing body 2 at the bearing end position of the rotating shaft 1, and ensuring the bearing capacity of the bearing body 2. The oil return structure of the utility model is compact and does not need to occupy extra space, which ensures that the oil can be effectively returned and discharged, and ensures the reliable bearing of the bearing body 2.

[0051] Preferably, if Fig.12As shown, the oil unloading groove 23 is an annular oil unloading groove 231. The annular oil unloading groove 231 close to the load-bearing end of the rotating shaft 1 is connected to the internal oil return section 72, which further ensures the timely discharge of oil from the bearing body 2 at the load-bearing end of the rotating shaft 1 where the force and load are large, and further improves the effective load-bearing of the bearing body 2 at the load-bearing end of the rotating shaft 1.

[0052] like Figure 4 As shown, the oil inlet 411 of the constant flow oil supply section, the oil inlet 511 of the constant pressure oil supply section, the oil outlet 61 of the end unloading oil return channel and the oil outlet 721 of the internal oil return section are arranged on the end surface of the bearing body 2. The setting of the constant flow oil supply ring groove 42, the constant pressure oil supply ring groove 52 and the oil collecting ring groove 71 makes the setting position of each oil port flexible and adjustable, ensuring the orderly arrangement of multiple oil supply channels and oil return channels, and its structure is simple and easy to process. In other embodiments, the setting positions of the oil inlet 411 of the constant flow oil supply section, the oil inlet 511 of the constant pressure oil supply section, the oil outlet 61 of the end unloading oil return channel and the oil outlet 721 of the internal oil return section can be flexibly adjusted according to actual conditions.

[0053] like Figures 6 to 9 As shown, the moment load bearing cavity 221 is connected to the constant flow oil supply ring groove 42 through the radial constant flow channel 43; Fig.10 , Fig.11 As shown, the radial load bearing cavity 211 is connected to the constant pressure oil supply ring groove 52 through the radial constant pressure channel 53, and a throttle 9 is arranged in the radial constant pressure channel 53. Its structure is simple and compact, ensuring that the oil is effectively supplied to the corresponding load bearing cavity.

[0054] At the same time, the setting of the throttle 9 can meet the load-bearing requirements of the constant pressure bearing area 21. The constant pressure bearing area 21 can maximize the dynamic pressure effect at high speed, and the shaft 1 has a strong radial load bearing capacity when rotating at high and low speeds. In this embodiment, the throttle 9 can be set as a small hole throttle, a capillary throttle, a slide valve throttle or a film throttle.

[0055] like Figure 6 and Figure 8 As shown, the constant flow oil supply section 41 includes a constant flow vertical section and a constant flow horizontal section that are interconnected. The constant flow vertical section is connected to the constant flow oil supply ring groove 42, and the constant flow horizontal section is connected to the quantitative oil pump. The pumping amount of the quantitative oil pump is determined according to the load of the rotating shaft 1 and the size of the constant flow bearing area 22. The quantitative oil pump supplies a fixed flow of oil to the moment load bearing cavity 221 through the constant flow oil supply channel 4. The pressure in the moment load bearing cavity 221 is equal to the pressure of the quantitative oil pump.

[0056] In this embodiment, the rotating shaft 1 is tilted and deformed under the upward force of the external load-bearing component, the lower gap of the left end area (load-bearing end) of the bearing body 2 increases, the oil resistance decreases, and the oil flow increases, and the upper gap decreases, the oil resistance increases, and the oil flow decreases. At this time, the constant flow bearing area 22 of the left end area of ​​the bearing body 2 is located at the top of the bearing body 2 to transport a fixed flow of oil to the upper gap position of the constant flow bearing area 22. At this time, the lower pressure of the left end area of ​​the bearing body 2 decreases, and the upper pressure increases, thereby ensuring sufficient bearing capacity of the rotating shaft 1 under the pressure difference between the upper and lower oil chambers.

[0057] At the same time, the upper gap of the right end area (non-bearing end) of the bearing body 2 increases, the oil resistance decreases, and the oil flow increases, while the lower gap decreases, the oil resistance increases, and the oil flow decreases. At this time, the constant flow bearing area 22 of the right end area of ​​the bearing body 2 is located at the bottom of the bearing body 2 to deliver a fixed flow of lubricating oil to the lower gap position of the right end of the bearing body 2. At this time, the upper pressure of the right end area of ​​the bearing body 2 decreases, and the lower pressure increases, thereby ensuring sufficient bearing capacity of the rotating shaft 1 under the pressure difference between the upper and lower oil chambers. The utility model avoids the leakage of most of the oil from the large gap position between the rotating shaft 1 and the bearing body 2, and the occurrence of bearing edge sweeping and tile burning, so that the bearing body 2 can effectively withstand large bending moment loads, greatly improving the safety and reliability of the system.

[0058] like Fig.10 As shown, the constant pressure oil supply section 51 includes a constant pressure vertical section and a constant pressure horizontal section which are connected to each other. The constant pressure vertical section is connected to each constant pressure oil supply ring groove 52 , and the constant pressure horizontal section is connected to a constant pressure oil pump, which supplies oil to the radial load bearing cavity 211 .

[0059] like Fig.11 As shown, the constant pressure bearing area 21 is provided with four radial load bearing cavities 211, and the four radial load bearing cavities 211 are evenly arranged along the circumference of the bearing body 2 to ensure that the constant pressure bearing area 21 can reliably bear the radial load of the rotating shaft 1. In other embodiments, the number and position of the radial load bearing cavities 211 can be adjusted according to actual conditions, as long as it can ensure that the radial load of the rotating shaft 1 can be reliably borne.

[0060] When the rotating shaft 1 is tilted and deformed, the constant pressure bearing area 21 is subjected to the radial load of the rotating shaft 1, and the upper clearance of the constant pressure bearing area 21 increases and the oil resistance decreases; the lower clearance of the constant pressure bearing area 21 decreases and the oil resistance increases. At this time, the damping of the throttle 9 changes with the radial load of the rotating shaft 1, so that the upper throttling clearance decreases and the throttling resistance increases, and the lower throttling clearance increases and the throttling resistance decreases. At this time, the oil pressure of the upper radial load bearing chamber 211 decreases, and the oil pressure of the lower radial load bearing chamber 211 increases. At this time, the pressure difference between the upper and lower radial load bearing chambers 211 lifts the rotating shaft 1, ensuring that the rotating shaft 1 always floats in the pressure oil.

[0061] like Figure 3and Figure 5 As shown, the end unloading oil return channel 6 includes an end unloading vertical section and an end unloading horizontal section that are connected to each other. The end unloading vertical section is connected to both axial sides of the bearing body 2, and the end unloading horizontal section is connected to the external return oil collection component to ensure effective oil return and discharge. Fig.12 As shown, the internal oil return section 72 includes an internal vertical section and an internal horizontal section that are interconnected, the internal vertical section is connected to the oil collecting ring groove 71 and the annular oil discharge groove 231, and the internal horizontal section is connected to the external oil return collection component to ensure that the oil is effectively returned and discharged. Its oil return structure is simple and compact, and does not need to occupy extra space.

[0062] Furthermore, if Fig.13 As shown, the rotating shaft system of the utility model also includes a ventilation component 8, which includes a ventilation channel 81. The ventilation channel 81 is horizontally arranged on the bearing body 2, and the end of the ventilation channel 81 away from the bearing end of the rotating shaft 1 is connected to an air source to prevent external impurities and dust at the bearing end of the rotating shaft 1 from entering the internal area of ​​the bearing housing 3.

[0063] like Figure 7 and Fig. 9 As shown, the area at the end of the bearing body 2 that does not bear the moment load of the rotating shaft 1 is the non-load-bearing flow area 24. The inner diameter of the constant-flow bearing area 22 is the same as the outer diameter of the rotating shaft 1 to effectively bear the moment load of the rotating shaft 1; the inner diameter of the non-load-bearing flow area 24 is larger than the outer diameter of the rotating shaft 1 to reduce the processing requirements of the bearing body 2 at the non-load-bearing area; the non-load-bearing flow area 24 is connected to the constant-flow bearing area 22 through a conical transition section 25 to enclose the inner ring of the end of the bearing body 2. The combination of the constant-flow bearing area 22 and the non-load-bearing flow area 24 makes it easy to process the bearing body 2 while reliably bearing the moment load of the rotating shaft 1, so that the return oil is effectively discharged from the non-load-bearing flow area 24, ensuring the reliable and safe operation of the rotating shaft system.

[0064] Although the present invention has been described with reference to preferred embodiments, various modifications may be made thereto and parts thereof may be replaced with equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various embodiments may be combined in any manner as long as there is no structural conflict. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A rotating shaft system with high load-bearing capacity, comprising a rotating shaft, a bearing body sleeved on a journal of the rotating shaft, and a bearing housing sleeved outside the bearing body, It is characterized in that A constant pressure bearing area is provided in the middle of the bearing body, and a constant flow bearing area is provided in the end area of ​​the bearing body that bears the bending moment load of the rotating shaft; the constant flow bearing area is provided with a moment load bearing cavity that provides an opposite force to the bending moment load of the rotating shaft, and the constant pressure bearing area is provided with radial load bearing cavities arranged at intervals along the circumference of the bearing body; an oil unloading groove is provided between the moment load bearing cavity and the radial load bearing cavity to prevent the oil in adjacent cavities from interfering with each other.

2. The shaft system with high load-bearing capacity according to claim 1, It is characterized in that It also includes a constant-flow oil supply channel and a constant-pressure oil supply channel, the constant-flow oil supply channel includes a constant-flow oil supply section provided on the bearing housing, and a constant-flow oil supply ring groove provided on the outer surface of the bearing body, the constant-flow oil supply section is connected with the moment load bearing cavity through the constant-flow oil supply ring groove; the constant-pressure oil supply channel includes a constant-pressure oil supply section provided on the bearing housing, and a constant-pressure oil supply ring groove provided on the outer surface of the bearing body, the constant-pressure oil supply section is connected with the radial load bearing cavity through the constant-pressure oil supply ring groove.

3. The shaft system with high load-bearing capacity according to claim 2, It is characterized in that It also includes an end unloading oil return channel and an internal oil return channel, the oil inlet of the end unloading oil return channel is arranged at the two ends of the bearing shell and located on both axial sides of the bearing body; the internal oil return channel includes an oil collecting ring groove and an internal oil return section that are interconnected, the oil collecting ring groove is arranged on the inner surface of the end of the bearing body close to the bearing end of the rotating shaft and is located on the axial outside of the constant flow bearing area, and the internal oil return section is arranged on the bearing shell.

4. The shaft system with high load-bearing capacity according to claim 3, It is characterized in that The oil unloading groove is an annular oil unloading groove, and the annular oil unloading groove close to the bearing end of the rotating shaft is communicated with the internal oil return section.

5. The shaft system with high load-bearing capacity according to claim 3, It is characterized in that The oil inlet of the constant flow oil supply section, the oil inlet of the constant pressure oil supply section, the oil outlet of the end unloading oil return channel and the oil outlet of the internal oil return section are arranged on the end surface of the bearing body.

6. A shaft system with high load-bearing capacity according to any one of claims 1 to 5, It is characterized in that The area at the end of the bearing body that does not bear the bending moment load of the rotating shaft is a non-load-bearing flow zone, the inner diameter of the constant flow bearing zone is the same as the outer diameter of the rotating shaft, and the inner diameter of the non-load-bearing flow zone is larger than the outer diameter of the rotating shaft; the non-load-bearing flow zone and the constant flow bearing zone are connected by a conical transition section to enclose the inner ring of the end of the bearing body.

7. A shaft system with high load-bearing capacity according to any one of claims 1 to 5, It is characterized in that It also includes a ventilation component for preventing external impurities and dust from entering the interior of the bearing shell. The ventilation component includes a ventilation channel arranged on the bearing body, and one end of the ventilation channel away from the bearing end of the rotating shaft is connected to an air source.

8. A shaft system with high load-bearing capacity according to any one of claims 2 to 5, It is characterized in that The moment load bearing cavity is communicated with the constant flow oil supply ring groove through a radial constant flow channel; the radial load bearing cavity is communicated with the constant pressure oil supply ring groove through a radial constant pressure channel, and the radial constant pressure channel is provided with a throttle.

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