Bearing configuration

Abstract

Disclosed is a bearing arrangement, which includes: at least two bearings, each bearing having an inner ring and an outer ring, the inner rings of the at least two bearings being mounted on a shaft; and a balancing piston disposed between the two bearings, wherein the balancing piston includes a first portion and a second portion, the first portion and the second portion axially contacting the outer rings of the two bearings, wherein the balancing piston further includes an inlet for guiding a pressure fluid between the first portion and the second portion to provide pressure to the first portion and the second portion, wherein the balancing piston is configured to adjust an axial force acting on at least one of the two bearings, wherein the balancing piston includes an outlet for guiding the pressure fluid as a lubricant to at least one of the two bearings, and / or the outer diameter of the balancing piston is greater than the outer diameter of the outer ring of the bearing.

Description

Field of the Invention

[0001] The present invention relates to a bearing arrangement. Background Art

[0002] The axial load capacity of a rolling bearing depends on the bearing contact angle and the type, size, and number of rolling elements. Bearings can also be arranged side by side to increase the total load capacity. The contact angle is defined as the contact angle inside the bearing. The larger the contact angle, the higher the axial load capacity.

[0003] At high speeds, the centrifugal force on the rolling elements generates an induced axial force that acts on the shaft in the opposite direction of the external force. The larger the contact angle, the larger the induced force. If the induced force is greater than the external force, it will cause the shaft to undergo axial displacement in the direction opposite to the direction of the external force. This situation must be avoided. For example, this may occur in a screw compressor where the external force is small during startup. The displacement can be limited by using a backup bearing that counteracts the displacement, but the backup bearing will induce additional forces on the (multiple) thrust bearings in addition to the external force and increase the frictional heat. This increases the load on the thrust bearings and shortens the service life. To reduce or eliminate the induced force, a balancing piston can be used to provide a force in the direction opposite to the induced force.

[0004] However, at the same time, lubrication and cooling must be provided to the bearings to avoid damage due to high temperature and improper bearing lubrication. A high contact angle, high speed, and large bearing axial force all generate more friction and frictional heat. To provide a bearing arrangement that can operate at high forces at high speeds, a thrust bearing with a large contact angle is required, and effective lubrication and cooling are required to remove heat. Summary of the Invention

[0005] Accordingly, it is an object of the present invention to provide a bearing arrangement having a balancing piston such that the bearing arrangement can be easily lubricated.

[0006] This object is solved by a bearing arrangement according to the following.

[0007] The bearing arrangement includes at least two bearings, each bearing having an inner ring and an outer ring, and the inner rings of the at least two bearings are mounted on a shaft. The bearings can be any type of bearing, such as ball bearings, roller bearings, tapered roller bearings, etc.

[0008] In a preferred embodiment, one of the at least two bearings may be a thrust bearing and the other bearings may be four-point contact ball bearings. A four-point contact ball bearing is a single row angular contact ball bearing having raceways designed to support axial loads in two directions. For a given axial load, it can also support a limited radial load. A thrust bearing is designed to accommodate only axial loads. The thrust bearing may be a tapered roller bearing or an angular contact ball bearing. The thrust bearing may also be a combination of one or more tapered roller bearings or angular contact ball bearings, or a combination of tapered roller bearings and angular contact ball bearings.

[0009] To keep the thrust bearing seated before and during startup, or to avoid axial displacement of the shaft (e.g., as explained above, axial displacement of the shaft may occur during startup), the bearing configuration includes a spring that cooperates with a balance piston disposed between the two bearings. The balance piston includes a first part and a second part that axially contact the outer rings of the two bearings, wherein the balance piston further includes an inlet for guiding a pressure fluid between the first part and the second part to provide pressure to the first part and the second part, wherein the balance piston is configured to adjust the axial force applied to at least one of the two bearings.

[0010] By using a four-point contact ball bearing as the support bearing and combining it with a balance piston and a spring, a spring force can be generated in the direction of the external force on the support bearing during startup, and then a force in the opposite direction can be generated by the balance piston during steady-state operation. When the balance piston is energized, the balance piston first slightly compresses the spring and then applies a force on the shaft opposite to the external force. Thus, during startup, the thrust bearing(s) will be seated by the spring force, and then in the steady state, the piston force will cancel out the external force, thereby reducing the force on the thrust bearing(s) under steady-state conditions.

[0011] For this purpose, the balance piston applies an axial force through one of the bearings (e.g., the four-point contact ball bearing) in the opposite direction of the spring preload via the first part and the second part. The first part and the second part of the balance piston are pushed apart by the pressure fluid, thereby providing an axial force to reduce the force on the thrust bearing. Since the acting force of the balance piston cancels out the spring force and the external force, the acting force of the balance piston adjusts the axial force applied to at least one of the two thrust bearings. The axial force applied to at least one of the two thrust bearings is the sum of the external force, the spring force / preload, and the acting force of the balance piston.

[0012] In order to lubricate the bearing arrangement, in particular a four-point contact ball bearing, in addition to adjusting the axial force, the balancing piston further includes an outlet for guiding a pressurized fluid as a lubricant to at least one of the two bearings. Thus, the pressurized fluid can be used to provide pressure to adjust the axial force by reducing the force on the thrust bearing, while also being used to lubricate the four-point contact ball bearing. Additional elements for lubricating this bearing can be omitted.

[0013] The outlet for guiding the pressurized fluid as a lubricant to at least one of the two bearings can be provided by a gap between a first part and a second part of the balancing piston. Additionally, for example, when the lubrication through this gap is insufficient, the first part of the balancing piston can include an opening that opens towards one of the four-point contact ball bearings. Alternatively or additionally, the bearing can be lubricated by the shaft and an inner ring spacer. The lubricant can be used to cool and lubricate the four-point contact ball bearing.

[0014] It should be noted that the lubrication through the balancing piston can also be supplementary to another lubrication (e.g., lubrication through an inner ring spacer), or can support such lubrication.

[0015] The inlet of the balancing piston can be connected to an external pressurized fluid supply (source), or in the case of a screw compressor, the inlet of the balancing piston can be connected to the discharge pressurized fluid of the compressor. The pressurized fluid can be, for example, oil or a hydraulic fluid, and the oil or hydraulic fluid can also be used as a lubricant. The inlet can be, for example, an opening in the balancing piston in the radial direction of the bearing arrangement.

[0016] According to an embodiment, the first part and the second part of the balancing piston form an annular piston-cylinder device. Both parts can be formed annularly. In particular, the effective axial pressure surface of the annular piston-cylinder device can be larger than the axial side surface of the outer ring, for example, it can be 1.5 to 3 times larger, preferably 2 to 2.5 times larger. Thus, the surface of the balancing piston pressing against the outer ring surface can be larger, enabling good pressure transfer from the balancing piston to the outer ring. In particular, the outer diameter of the balancing piston is at least 5% larger than the outer diameter of the four-point bearing. In the case of this increased piston area, for a given pressure, the piston force can be increased, and thus a larger balancing force can be generated.

[0017] In another embodiment, the bearing arrangement includes a thrust bearing, a balancing piston, and a four-point contact ball bearing, wherein the outer diameter of the balancing piston is at least 5% larger than the outer diameter of the four-point contact ball bearing.

[0018] According to another embodiment, the outer diameter of the balance piston is larger than the outer diameter of the outer ring of the bearing, and the inner diameter of the balance piston is smaller than the inner diameter of the outer ring of the bearing. Thus, the resultant force generated by the piston pressure is consistent with the contact force on the outer ring of the four-point contact ball bearing. These dimensions of the balance piston can ensure that the balance piston, especially the first part contacting the outer ring of the four-point contact ball bearing, is not prone to warping. Warping of the piston may cause the piston to jam. Additionally, when the balance piston contacts the outer ring only in a small area, warping may also have a negative impact on the contacting bearing. If the resultant force generated by the piston pressure is not consistent with the contact force on the outer ring of the four-point contact ball bearing, the pressure may be unevenly distributed. In this case, the resultant force generated by the piston pressure may deviate from the contact force on the outer ring of the bearing. This may generate an overturning moment that warps the piston. As described above, due to the relationship between the dimensions of the balance piston and the outer ring of the bearing, the pressure can be evenly distributed, and the risk of warping will be reduced.

[0019] According to another embodiment, the contact surface of the balance piston with the area of the outer ring of the four-point contact ball bearing can be convex. This allows the contact point of the balance piston force to remain substantially unchanged in the case of warping.

[0020] According to another embodiment, the bearing arrangement includes an axial inlet for supplying lubricant to the bearing arrangement and an axial outlet for discharging lubricant from the bearing arrangement. The lubricant can be used to lubricate the bearing and at the same time to cool the bearing. The axial inlet can be configured on one axial side of the bearing arrangement, while the axial outlet can be configured on the opposite side of the bearing arrangement. Thus, the lubricant can be individually supplied to each bearing through the entire bearing arrangement, providing lubrication to all bearings.

[0021] In another embodiment, the bearing arrangement includes at least three bearings. In this case, for example, a generally radial inlet can be configured at least between the inner rings of two bearings for supplying lubricant to the bearings. Such an inlet may be coupled to an axial hole of the shaft to supply lubricant to the bearings. The shaft can be configured as a hollow shaft. The shaft can include one or more radial openings or generally radial openings that can be coupled to the inlet located between the inner rings of the bearings to supply lubricant to the bearings. As an option, the inlet configured at least between the inner rings of two bearings can be coupled to an external lubricant reservoir outside the bearing arrangement. Additionally, spacers can be configured between the outer rings and / or inner rings of two bearings, and the inlet configured at least between the inner rings of two bearings can be configured within the spacer.

[0022] To discharge lubricant from the bearing arrangement, the outlet can be arranged at least between the outer rings of two bearings. Thus, lubricant can be supplied through the (one or more) inlets and discharged through the (one or more) outlets, such that there is a lubrication flow through the bearing, improving lubrication and cooling. Like the inlets, such outlets can also be arranged in the spacer.

[0023] In particular, each bearing can be lubricated through a separate inlet and outlet to achieve maximized cooling and lubrication conditions. The flow path of the lubricant can be through the center of the shaft on one side, through the radial holes in the shaft, and to the thrust bearing through the inlet, and the lubricant can be discharged on the other side, where each thrust bearing has a separate flow path and the flow direction is the pumping direction of the bearing. In other words, the flow path of the lubricant is from the radially inner side to the radially outer side of the bearing arrangement. The lubricant from each bearing can be discharged into the space between the outer diameter of the bearing and the housing. Then, the lubricant can be discharged from this space, preferably, the lubricant can be discharged from this space through a common outlet.

[0024] The lubricant can be used for both cooling and lubrication.

[0025] According to another embodiment, the (hollow) shaft is closed at one end by a ring which provides an inlet capable of being coupled to an external lubrication supply source. Additionally, the ring can ensure that the lubricant does not flow back.

[0026] With the bearing arrangement proposed herein, a good combination of cooling and lubrication can be provided, and a thrust bearing with a high axial load capacity can be provided, which allows for a high load capacity at high speeds.

[0027] Further preferred embodiments are defined in the dependent claims as well as in the description and the drawings. Thus, the elements described or shown in combination with other elements can exist alone or in combination with other elements without departing from the scope of protection.

[0028] Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings, wherein the drawings are merely exemplary and are not intended to limit the scope of protection. The scope of protection is defined only by the appended claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 : A schematic cross-sectional view of a part of a bearing arrangement according to a first embodiment of the present invention;

[0030] Figure 2 : Figure 1 A schematic cross-sectional view of the entire bearing arrangement;

[0031] Figure 3 : A schematic cross-sectional view of a bearing arrangement according to a second embodiment of the present invention;

[0032] Figure 4 : Schematic cross-sectional view of a bearing arrangement according to a third embodiment of the present invention, including forces within the bearing arrangement during startup;

[0033] Figure 5 : Figure 4 Schematic cross-sectional view of a bearing arrangement, including forces within the bearing arrangement during steady state; and

[0034] Figure 6 : Schematic cross-sectional view of a part of a bearing arrangement according to a fourth embodiment of the present invention.

[0035] Hereinafter, elements having the same or similar functions are denoted by the same reference numerals.

[0036] bearing arrangement

[0037] 2 Four-point contact ball bearing

[0038] 4 Thrust bearing

[0039] 6 Balance piston

[0040] 8 Inner ring

[0041] 10 Outer ring

[0042] 12 Ball

[0043] 14 Inner ring

[0044] 16 Outer ring

[0045] 18 Rolling element

[0046] 20 Spacer

[0047] 21 Radial inlet

[0048] 22 First part

[0049] 23 Convex surface

[0050] 24 Second part

[0051] 26 Outlet

[0052] 28 Lubricant flow

[0053] 30 Spring element

[0054] 32 Spacer

[0055] 34 Outlet

[0056] 36 Lubricant flow

[0057] 38 Thrust bearing

[0058] 40 Inner ring

[0059] 42 Outer ring

[0060] 44 Rolling elements

[0061] 46 Housing

[0062] 47 Space

[0063] 48 Spacer

[0064] 50 Inlet

[0065] 52 Outlet

[0066] 54 Spacer

[0067] 56 Bearing

[0068] 58 Inner ring

[0069] 60 Outer ring

[0070] 62 Rolling elements

[0071] 64 Shaft

[0072] 66 Axial hole

[0073] 68 Opening

[0074] 70 Ring

[0075] 72 Inlet

[0076] 74 Outlet

[0077] 76 External force

[0078] 78 Piston force

[0079] 79 Piston force

[0080] 80 Spring force

[0081] 82 Bearing force Detailed implementation manners

[0082] Figure 1 A part of bearing arrangement 1 is shown, and bearing arrangement 1 is shown as having two bearings 2, 4. A balancing piston 6 is arranged between the two bearings 2, 4.

[0083] Bearing 2 is a four-point contact ball bearing, having an inner ring 8, an outer ring 10, and rolling elements 12 which are balls. Bearing 2 can support axial loads in two directions and can also support a limited radial load.

[0084] The bearing 4 is a thrust bearing having an inner ring 14, an outer ring 16, and rolling elements 18 which, in this case, are balls. In this embodiment, the bearing 4 only bears axial loads. The bearings 2 and 4 are separated by a spacer 20 at their inner rings 8 and 14.

[0085] To reduce the forces on the bearing 4, the bearing arrangement 1 includes a balancing piston 6. The balancing piston 6 includes a first part 22 and a second part 24. The first part 22 and the second part 24 axially contact the outer rings 10, 16 of the two bearings 2, 4. The balancing piston 6 further includes an inlet 25 which can be connected to an external pressure fluid supply source. The inlet 25 is used to direct pressure fluid between the first part 22 and the second part 24 to supply pressure to the first part 22 and the second part 24.

[0086] The spring element 30 can be used to provide an axial spring force (i.e., generate a preload) to the bearing 2 before and during start-up. The purpose of the spring preload is to keep the thrust bearing 4 in place. However, under steady-state operating conditions, the thrust bearing(s) induce an axial force due to centrifugal force. The induced force is cancelled by the spring force and an external force in the same direction as the spring force. This means that the forces in the thrust bearing(s) are high. The balancing piston 6 can be used to cancel the spring force by compressing the spring, i.e., for cancelling or eliminating the spring force. For this purpose, the balancing piston 6 applies an axial force to the bearing 2 via the first part 22 and the second part 24. This axial force acts in a direction opposite to the spring preload force. The balancing piston force also applies a force to the four-point contact ball bearing in a direction opposite to the external force, and this force is transmitted to the shaft through the four-point contact ball bearing, thereby reducing the forces on the thrust bearing(s) and thus extending the life of the thrust bearing(s). The first part 22 and the second part 24 of the balancing piston 6 are pushed apart by the pressure fluid, thus applying an axial force to the four-point contact ball bearing. This will also be described with reference to Figure 4 and Figure 5 will be described.

[0087] To provide lubrication and cooling of the bearing 2, the balancing piston 6 includes an outlet 26 for directing the pressure fluid as a lubricant to the bearing 2. The lubricant flow is indicated by the arrow 28. Thus, the pressure fluid can provide two functions, providing pressure to regulate the axial force acting on the bearing 4 (which is the sum of the external force, the spring preload, and the force of the balancing piston), while lubricating and cooling the bearing 2.

[0088] The bearing 4 can be spaced apart from the balance piston 6 by a spacer 32. The spacer 32 can include an outlet for discharging lubricant from the bearing 4, and the flow of this lubricant (this lubricant flow) is indicated by the arrow 36. The lubricant for the bearing 4 can be supplied through different openings, which will be illustrated in the following drawings. Since the bearing 2 is lubricated only by the pressure fluid in the balance piston 6, the lubrication of the bearing 4 is separate from that of the bearing 2.

[0089] As an option, the bearing 2 can also be lubricated through the radial holes in the spacer 20. Since the piston 6 must not be energized (pressurized / applied with energy) before startup, lubricating the bearing 2 through the radial holes in the spacer 20 may be necessary if a separate lubricant pump is used during the pre-lubrication cycle before startup.

[0090] Figure 2 is shown Figure 1 The entire bearing configuration 1 is shown and has two thrust bearings 4, 38 in succession (one after the other). It can be seen that the bearing configuration 1 includes four bearings: a four-point contact ball bearing 2, a thrust bearing 4 (which can be referred to as the first thrust bearing 4), a second thrust bearing 38, and a cylindrical roller bearing 56.

[0091] The second thrust bearing 38 includes an inner ring 40, an outer ring 42, and rolling elements 44, which are balls in this case. The bearings 2, 4, and 38 are arranged within a housing 46.

[0092] The bearing 56 is a cylindrical roller bearing that bears radial loads and includes an inner ring 58, an outer ring 60, and cylindrical roller elements 62 arranged between the rings 58, 60. The inner rings 40 and 58 of the bearings 38 and 56 are separated by a spacer 54. The radial loads are transmitted through the housing 46. The outer ring 60 contacts the housing 46. The other bearings 2, 4, 38 only bear axial loads and have a gap 47 between the outer rings 10, 16, 42 and the housing 46 to prevent them from bearing radial loads.

[0093] The outer rings 42 and 60 of bearings 38 and 56 are separated by a spacer 48. In this embodiment, the spacer 48 includes an opening 50 that serves as a radial inlet for supplying lubricant to bearings 56, 38, and 4. The spacer also includes a radial opening 52 that is open towards bearings 38, 4 and towards bearing 56. The flow of the lubricant is indicated by arrows, starting from the inlet 50 and flowing through the outlet 52 to bearing 56 and flowing through bearings 38 and 4, and leaving the bearing arrangement 1 via a spacer 32 having an outlet 34. In this case, bearing 4 is lubricated with the lubricant that has passed through bearing 38. Since both bearing 38 and bearing 4 are ball bearings, which generate less frictional heat than roller bearings, lubricating bearing 4 with the lubricant that has passed through bearing 38 may be sufficient for lubricating and cooling bearing 4. Thus, in this embodiment, the bearing arrangement 1 is lubricated from the radial outside of the bearing arrangement 1. The inlet 50 may be coupled to an external lubricant reservoir (not shown).

[0094] Figure 3 Another embodiment of the bearing arrangement 1 is shown. In this case, the bearing arrangement 1 includes Figure 1 and Figure 2 bearing 2, Figure 2 bearing 56, two pairs of bearings arranged side by side, each pair including Figure 2 bearing 4 and 38.

[0095] In this case, the lubrication of bearings 4, 38, and 56 is performed from the radial inside of the bearing arrangement 1 (i.e., from the side where the shaft 64 is located). For this purpose, the shaft 64 is configured as a hollow shaft having a central hole 66. From this hole 66, a radial outlet 68 leads to an inlet 72 of a spacer 54 between the inner rings 40 and 14 and between the inner rings 40 and 58. In this embodiment, the spacer 32 disposed between the outer rings of bearing 2 and bearing 4 and the spacer disposed between the outer rings of the two pairs of bearings (i.e., between the outer ring of bearing 4 and the outer ring of bearing 38) include outlets 34, 74 for distributing the lubricant from the bearing arrangement 1. Thus, the flow of the lubricant ( / lubricant flow) is as follows (indicated by arrows): from the central hole 66 of the shaft 64 through the opening 68 and via the inlet 72 into bearings 4, 38 and 4, 38 and 56, and then via the outlets 34, 74 to the outside of the bearing arrangement 1. Since there is a lubricant flow for delivering new and fresh lubricant through the bearings, the lubrication can be improved.

[0096] To prevent the lubricant from flowing back ( / flowing back / counter - flowing) from the central hole 66 of the shaft 64, the shaft 64 can be closed with a ring 70, i.e., the central hole 66 can be closed with a ring 70. The lubricant is sprayed into the shaft through the ring 70.

[0097] Figure 4Another embodiment of the bearing arrangement 1 is shown. In this embodiment, the bearings 4 and 38 are not two ball thrust bearings but two tapered roller bearings 4, 38. Different from the Figures 1 to 3 embodiment, the second part 24 of the balancing piston 6 is wider at the outer diameter and requires a larger width to compensate for the space between the outer rings of the bearings.

[0098] As Figure 4 shown, in the first operating phase, i.e., for example during start-up, the external force 76 is zero at start-up and gradually increases with increasing speed. At start-up, in the direction of the external force 76, this external force is increased by the spring force 80 via the backup bearing 2, thereby generating the bearing force 82 for loading and seating the bearings 4, 38.

[0099] In the second operating phase as Figure 5 shown, for example, during the steady state, when the balancing piston is energized (pressurized), it first compresses the spring 30 and then exerts a force 78 on the shaft that is opposite to the external force 76. The balancing piston 6 also exerts a force 79 in the direction opposite to the direction of the force 78, and the force 79 is transmitted to the housing 46 through the spacers and outer rings of the bearings 4, 38, 56. Thus, at start-up, the (multiple) thrust bearings will be seated under the action of the spring force 80, and then in the steady state, the piston force 78 will counteract the external force, thus reducing the force acting on the (multiple) thrust bearings under steady state conditions.

[0100] Figure 6 Another embodiment of the bearing arrangement 1 is shown. As shown, the contact surface 23 of the balancing piston 6 with the region of the outer ring 10 of the four-point contact ball bearing 2 is convex. This allows the contact points of the balancing piston force to remain substantially unchanged in the case of warping.

[0101] Similarly as Figure 6 shown, the bearing 2 can be lubricated through the radial inlet 21 in the spacer 20. Since the piston 6 must not be energized (pressurized) before start-up, it may be necessary to lubricate the bearing 2 through the radial inlet 21 in the spacer 20 if a separate lubricant pump is used in the pre-lubrication cycle before start-up.

[0102] It should be noted that the features of different embodiments of the bearing arrangement 1 can be combined, or certain features of one embodiment can be interchanged with the features of another embodiment. For example, the technical feature of supplying lubricant from the side where the shaft is located can be interchanged with the technical feature of supplying lubricant from the radial outside of the bearing arrangement. In addition, the types of bearings used in the embodiments (ball bearings, tapered roller bearings, cylindrical roller bearings) are only exemplary, and any other types of bearings can be used, and these bearings can be used in different combinations.

[0103] In summary, the bearing arrangement described herein provides high axial load capacity, improved control of axial displacement of the shaft, and furthermore provides lubrication and cooling of the bearing arrangement without additional components.

Claims

1. A bearing arrangement, comprising: At least two bearings, each bearing having an inner ring and an outer ring, the inner rings of the at least two bearings being mounted on a shaft, and A balance piston disposed between the two bearings, wherein the balance piston includes a first portion and a second portion, the first portion and the second portion axially contacting the outer rings of the two bearings, wherein the balance piston further includes an inlet for guiding a pressure fluid between the first portion and the second portion to provide pressure to the first portion and the second portion, wherein the balance piston is configured to adjust an axial force acting on at least one of the two bearings, Characterized in that the balance piston includes an outlet for guiding the pressure fluid as a lubricant to at least one of the two bearings, and an outer diameter of the balance piston is greater than an outer diameter of the outer ring of the bearing; all of the pressure fluid entering between the first portion and the second portion through the inlet flows out through the outlet.

2. The bearing arrangement according to claim 1, characterized in that, The first portion and the second portion form an annular piston cylinder device.

3. The bearing arrangement according to claim 2, characterized in that, An effective axial pressure surface of the annular piston cylinder device is greater than an axial side surface of the outer ring.

4. The bearing arrangement according to claim 1, characterized in that, An inner diameter of the balance piston is less than an inner diameter of the outer ring of the bearing.

5. The bearing arrangement according to claim 1, characterized in that, The bearing arrangement includes an axial inlet for supplying lubricant to the bearing arrangement and an axial outlet for discharging lubricant from the bearing arrangement.

6. The bearing arrangement according to claim 1, characterized in that, The bearing arrangement includes at least three bearings, wherein the inlet is disposed at least between the inner rings of two bearings for supplying lubricant to the bearings.

7. The bearing arrangement according to claim 6, characterized in that, The inlet disposed at least between the inner rings of two bearings can be coupled to an axial hole of the shaft for supplying lubricant to the bearings, or wherein the inlet disposed at least between the inner rings of two bearings can be coupled to an external lubricant reservoir outside the bearing arrangement.

8. The bearing arrangement according to claim 6, characterized in that The outlet is disposed at least between the outer rings of two bearings for discharging lubricant from the bearings.

9. The bearing arrangement according to claim 6, characterized in that, Spacers are disposed between the outer rings and / or between the inner rings of two bearings, and wherein the inlet disposed at least between the inner rings of two bearings and / or the outlet disposed at least between the outer rings of two bearings are disposed within the spacers.

10. The bearing arrangement according to claim 6, characterized in that, One end of the shaft is closed with a ring that provides an inlet capable of being coupled to an external lubricant supply source.

11. A bearing arrangement, comprising: At least two bearings, each bearing having an inner ring and an outer ring, the inner rings of the at least two bearings being mounted on a shaft, and A balance piston disposed between the two bearings, wherein the balance piston includes a first portion and a second portion, the first portion and the second portion axially contacting the outer rings of the two bearings, wherein the balance piston further includes an inlet for guiding a pressure fluid between the first portion and the second portion to provide pressure to the first portion and the second portion, wherein the balance piston is configured to adjust an axial force acting on at least one of the two bearings, It is characterized in that the balance piston includes an outlet for guiding the pressure fluid as a lubricant to at least one of the two bearings; all of the pressure fluid entering between the first part and the second part from the inlet flows out from the outlet.

12. The bearing arrangement according to claim 11, characterized in that, The first part and the second part form an annular piston cylinder device.

13. The bearing arrangement according to claim 12, wherein, The effective axial pressure surface of the annular piston cylinder device is larger than the axial side surface of the outer ring.

14. The bearing arrangement according to claim 11, characterized in that, The inner diameter of the balance piston is smaller than the inner diameter of the outer ring of the bearing.

15. The bearing arrangement according to claim 11, characterized in that, The bearing configuration includes an axial inlet for supplying lubricant to the bearing configuration and an axial outlet for discharging lubricant from the bearing configuration.

16. The bearing arrangement according to claim 11, characterized in that, The bearing configuration includes at least three bearings, wherein the inlet is disposed at least between the inner rings of two bearings for supplying lubricant to the bearings.

17. The bearing arrangement according to claim 16, characterized in that, The inlet disposed at least between the inner rings of two bearings can be coupled to the axial hole of the shaft for supplying lubricant to the bearings, or wherein the inlet disposed at least between the inner rings of two bearings can be coupled to an external lubricant reservoir outside the bearing configuration.

18. The bearing arrangement according to claim 16, characterized in that, The outlet is disposed at least between the outer rings of two bearings for discharging lubricant from the bearings.

19. The bearing arrangement according to claim 16, wherein, Spacers are disposed between the outer rings and / or between the inner rings of two bearings, and wherein the inlet disposed at least between the inner rings of two bearings and / or the outlet disposed at least between the outer rings of two bearings are disposed within the spacers.

20. The bearing arrangement according to claim 16, wherein One end of the shaft is closed with a ring, and the ring provides an inlet that can be coupled to an external lubricant supply source.

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