KR102689077B1 - Hybrid fluid film bearing and electrically driven pump having the same - Google Patents

Abstract

Hybrid fluid bearings are provided. The hybrid fluid bearing includes a bearing housing mounted in a ring-coupled form on the outer diameter surface of the rotating shaft; A bearing sleeve mounted between the rotating shaft and the bearing housing and having a gap between the rotating shaft and the bearing housing, respectively; A compliant damper provided in the gap between the bearing housing and the bearing sleeve; And a liquid provided in the gap between the bearing housing and the bearing sleeve to define the degree of the gap, and sealing one side in the longitudinal direction of the gap where the compliant damper is provided, and pressurized and supplied between the bearing housing and the bearing sleeve. It may include a spring ring seal that allows oxygen or liquid fuel to flow to the other side of the gap in the longitudinal direction.

Description

Hybrid fluid bearing and electrical pump having the same {Hybrid fluid film bearing and electrically driven pump having the same}

The present invention relates to a hybrid fluid bearing and an electric pump equipped therewith, and more specifically, to a hybrid fluid bearing and an electric pump equipped therewith, which can improve the dynamic stability of a supported rotating shaft.

Recently, as demand for ultra-high-speed rotating machines that can be operated in extreme operating environments increases in industries related to energy, propulsion, and power, high-performance and high-efficiency fluid bearing technology has received great attention.

This is because bearings play a very large role in developing and operating high-speed and high-efficiency turbine, compressor, and pump systems.

Meanwhile, in the rotor system of a conventional turbo pump for a liquid rocket engine, the oxidizer pump and the fuel pump are connected by a coupling, and the oxidizer pump and fuel pump are each supported by two ball bearings.

The rotating body of this turbo pump for a liquid rocket engine rotates as a turbine located at the end of the fuel pump.

As such, conventional turbopumps for liquid rocket engines have problems with complex structures, high weight, and low energy efficiency.

One technical problem to be solved by the present invention is to provide a hybrid fluid bearing and an electric pump including the same, which can improve the dynamic stability of a supported rotating shaft.

Another technical problem to be solved by the present invention is to provide a lightweight electric pump for a liquid rocket engine with a simplified structure and improved energy efficiency.

The technical problems to be solved by the present invention are not limited to those described above.

In order to solve the above technical problems, the present invention provides a hybrid fluid bearing.

According to one embodiment, the hybrid fluid bearing includes a bearing housing mounted in a ring-coupled form on the outer diameter surface of the rotating shaft; A bearing sleeve mounted between the rotating shaft and the bearing housing and having a gap between the rotating shaft and the bearing housing, respectively; A compliant damper provided in the gap between the bearing housing and the bearing sleeve; And a liquid provided in the gap between the bearing housing and the bearing sleeve to define the degree of the gap, and sealing one side in the longitudinal direction of the gap where the compliant damper is provided, and pressurized and supplied between the bearing housing and the bearing sleeve. It may include a spring ring seal that allows oxygen or liquid fuel to flow to the other side of the gap in the longitudinal direction.

According to one embodiment, it is provided at both ends of the bearing sleeve in the longitudinal direction and may further include a non-contact annular seal that seals the gap between the rotating shaft and the bearing sleeve.

According to one embodiment, the non-contact annular seal may be provided as any one seal selected from a labyrinth seal, a flat seal, a floating seal, a hole pattern seal, a honeycomb seal, a foil seal, and a pocket seal.

According to one embodiment, the compliant damper may be provided as one selected from a wire mesh damper, a bump foil, an elastomer damper, a wave spring, a wire mesh damper, a coil spring, a cantilever beam foil, and a wing foil.

According to one embodiment, the spring ring seal may be provided in a cone shape in which the diameters of the axial inner end and the outer end are different, but the diameter of the axial inner end is relatively smaller than the diameter of the axial outer end. .

According to one embodiment, the spring ring seal may be provided as any one spring ring seal selected from a C-type spring ring seal, an S-type spring ring seal, an M-type spring ring seal, and a U-type spring ring seal.

According to one embodiment, the outer diameter of the spring ring seal may be fixed to the inner diameter surface of the bearing housing, and the inner diameter of the spring ring seal may be fixed to the outer diameter surface of the bearing sleeve.

According to one embodiment, the spring ring seal may be elastically deformed in the radial direction of the rotating shaft to enable elastic deformation of the compliant damper.

According to one embodiment, the bearing housing includes: a housing body whose center is axially open to enable insertion of the rotating shaft; and a first insertion groove formed in the depth direction from the inner diameter surface of the housing main body, into which the outer diameter side of the spring ring seal is inserted.

According to one embodiment, the bearing sleeve includes a sleeve body whose center is axially open to enable insertion of the rotating shaft and has an outer diameter smaller than the inner diameter of the housing body; and a second insertion groove formed in the depth direction from the outer diameter surface of the sleeve body and into which the inner diameter side of the spring ring seal is inserted.

According to one embodiment, the bearing sleeve is formed on the other side in the longitudinal direction of the gap formed between the bearing housing and the bearing sleeve, and guides liquid oxygen or liquid fuel pressurized and supplied between the bearing housing and the bearing sleeve toward the rotating shaft. It may further include a guide hole.

According to one embodiment, an anti-rotation pin is provided between the bearing housing and the bearing sleeve, and is supported by the bearing housing when the rotating shaft rotates, and may further include an anti-rotation pin that restrains the rotation of the bearing sleeve.

According to one embodiment, the bearing sleeve may be provided with a receiving groove that accommodates the other longitudinal end of the anti-rotation pin, the longitudinal end of which is fixed to the bearing housing.

Meanwhile, the present invention provides an electric pump.

According to one embodiment, the electric pump includes a rotating shaft supported by the hybrid fluid bearing described above; a liquid oxygen pump unit provided on one side in the longitudinal direction of the rotating shaft; a fuel pump unit provided on the other side of the rotating shaft in the longitudinal direction; and an electric motor unit that is axially coupled to the rotating shaft to provide a rotating driving force to the rotating shaft, and is provided behind the fuel pump unit or between the liquid oxygen pump unit and the fuel pump unit, wherein the hybrid fluid bearing is a journal bearing. It may be provided as a combination of a thrust bearing or a combination of a plurality of ball bearings.

According to an embodiment of the present invention, a bearing housing mounted in a ring-coupled form on the outer diameter surface of the rotating shaft; A bearing sleeve mounted between the rotating shaft and the bearing housing and having a gap between the rotating shaft and the bearing housing, respectively; A compliant damper provided in the gap between the bearing housing and the bearing sleeve; And a liquid provided in the gap between the bearing housing and the bearing sleeve to define the degree of the gap, and sealing one side in the longitudinal direction of the gap where the compliant damper is provided, and pressurized and supplied between the bearing housing and the bearing sleeve. It may include a spring ring seal that allows oxygen or liquid fuel to flow to the other side of the gap in the longitudinal direction.

Accordingly, a hybrid fluid bearing that can improve the dynamic stability of the supported rotating shaft can be provided.

Additionally, according to an embodiment of the present invention, an electric pump may be provided in which a rotating shaft is supported by such a hybrid fluid bearing.

According to an embodiment of the present invention, an electric pump may be provided in which an electric motor is provided integrally with a rotating shaft, and both an oxidizer pump and a fuel pump are employed in the longitudinal direction of the rotating shaft.

Accordingly, a lightweight electric pump with a simplified structure and improved energy efficiency can be provided.

According to one embodiment of the present invention, this electric pump can be applied to a liquid rocket engine.

1 and 2 are schematic diagrams for explaining an electric pump for a liquid rocket engine whose rotating shaft is supported by a hybrid fluid bearing according to an embodiment of the present invention.
Figure 3 is a schematic diagram for explaining a hybrid fluid bearing according to the first embodiment of the present invention.
Figure 4 is a perspective view showing a spring ring seal of a hybrid fluid bearing according to the first embodiment of the present invention.
Figure 5 is a side view of Figure 4.
Figure 6 is a schematic diagram for explaining a hybrid fluid bearing according to a second embodiment of the present invention.
Figure 7 is a schematic diagram for explaining a hybrid fluid bearing according to a third embodiment of the present invention.
Figure 8 is a side view showing a spring ring seal of a hybrid fluid bearing according to a third embodiment of the present invention.
Figure 9 is a schematic diagram for explaining a hybrid fluid bearing according to a fourth embodiment of the present invention.
Figure 10 is a diagram showing a spring ring seal of a hybrid fluid bearing according to a fourth embodiment of the present invention.
Figure 11 is a schematic diagram for explaining a hybrid fluid bearing according to the fifth embodiment of the present invention.
Figure 12 is a diagram showing a spring ring seal of a hybrid fluid bearing according to a fifth embodiment of the present invention.
Figure 13 is a cross-sectional view showing the spring ring seal of a hybrid fluid bearing according to the sixth embodiment of the present invention.
Figure 14 is a cross-sectional view showing a spring seal of a hybrid fluid bearing according to a seventh embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the attached drawings. However, the technical idea of the present invention is not limited to the embodiments described herein and may be embodied in other forms. Rather, the embodiments introduced herein are provided so that the disclosed content will be thorough and complete and so that the spirit of the present invention can be sufficiently conveyed to those skilled in the art.

In this specification, when an element is referred to as being on another element, it means that it may be formed directly on the other element or that a third element may be interposed between them. Additionally, in the drawings, the shape and size are exaggerated for effective explanation of technical content.

Additionally, in various embodiments of the present specification, terms such as first, second, and third are used to describe various components, but these components should not be limited by these terms. These terms are merely used to distinguish one component from another. Accordingly, what is referred to as a first component in one embodiment may be referred to as a second component in another embodiment. Each embodiment described and illustrated herein also includes its complementary embodiment. Additionally, in this specification, 'and/or' is used to mean including at least one of the components listed before and after.

In the specification, singular expressions include plural expressions unless the context clearly dictates otherwise. In addition, terms such as “include” or “have” are intended to designate the presence of features, numbers, steps, components, or a combination thereof described in the specification, but are not intended to indicate the presence of one or more other features, numbers, steps, or components. It should not be understood as excluding the possibility of the presence or addition of elements or combinations thereof. Additionally, in this specification, “connection” is used to mean both indirectly connecting and directly connecting a plurality of components.

In addition, in the following description of the present invention, if a detailed description of a related known function or configuration is judged to unnecessarily obscure the gist of the present invention, the detailed description will be omitted.

1 and 2 are schematic diagrams for explaining an electric pump for a liquid rocket engine whose rotating shaft is supported by a hybrid fluid bearing according to an embodiment of the present invention, and Figure 3 is a hybrid fluid according to the first embodiment of the present invention. It is a schematic diagram for explaining the bearing, and FIG. 4 is a perspective view showing the spring ring seal of the hybrid fluid bearing according to the first embodiment of the present invention, and FIG. 5 is a side view of FIG. 4.

As shown in Figures 1 and 2, the hybrid fluid bearing 100 according to the first embodiment of the present invention rotates the rotating shaft 20 provided in, for example, the electric pump 10 for a liquid rocket engine. It can be used to support .

Here, the electric pump 10 for a liquid rocket engine may include a liquid oxygen pump unit 30, a fuel pump unit 40, and an electric motor unit 50.

The liquid oxygen pump unit 30 may be provided on one side of the rotating shaft 20 in the longitudinal direction. This liquid oxygen pump unit 30 may include a liquid oxygen (LOX) pump inducer 31 and an impeller 32.

Additionally, the fuel pump unit 40 may be provided on the other side of the rotating shaft 20 in the longitudinal direction. This fuel pump unit 40 may include a fuel pump inducer 41 and an impeller 42.

In addition, the electric motor unit 50 may be axially coupled to the rotary shaft 20 to provide rotational driving force to the rotary shaft 20.

At this time, as shown in FIG. 1, the electric motor unit 50 is provided at the rear of the fuel pump unit 40, or as shown in FIG. 2, the liquid oxygen pump unit 30 and the fuel pump unit 40. It can be provided in between.

This electric motor unit 50 includes a motor 51 that rotates the rotary shaft 20, a stator 52 mounted in a ring-coupled form on the outer diameter surface of the motor 51, and a form surrounding the state 52. It may include a cooling jacket (53) provided with.

That is, as shown in FIG. 1, a liquid oxygen pump unit 30, a fuel pump unit 40, and an electric motor unit 50 are sequentially provided in the longitudinal direction of one rotation shaft 20 to form a liquid rocket engine. An electric pump (10) can be achieved.

In this case, a hybrid fluid bearing 100 made of a journal bearing 100a is mounted on the rear of the liquid oxygen pump unit 30 and the front and rear rotating shafts 20 of the electric motor unit 50, and the rotating shaft ( 20), and the rear rotation shaft 20 of the journal bearing 100a mounted on the rear rotation shaft 20 of the electric motor unit 50 includes two thrust bearings 100b. The hybrid fluid bearing 100 may be continuously mounted to support the rotation of the rotating shaft 20.

In addition, as shown in FIG. 2, a liquid oxygen pump unit 30, an electric motor unit 50, and a fuel pump unit 40 are sequentially provided in the longitudinal direction of one rotation shaft 20 to form a liquid rocket engine. It can also be used as an electric pump (10).

In this case, the rotating shaft 20 between the liquid oxygen pump unit 30 and the electric motor unit 50 and between the electric motor unit 50 and the fuel pump unit 40 each has a journal bearing 100a. Two hybrid fluid bearings 100 are installed to support the rotation of the rotating shaft 20, and a journal bearing ( Two hybrid fluid bearings 100 made of thrust bearings 100b are mounted in series on the rear rotary shaft 20 of 100a) to support the rotation of the rotary shaft 20.

That is, according to an embodiment of the present invention, the hybrid fluid bearing 100 may be provided as a journal bearing 100a or may also be provided as a thrust bearing 100b. Additionally, although not shown, the hybrid fluid bearing 100 may be provided as a ball bearing.

This means that the hybrid fluid bearing 100 used to support the rotation of the rotating shaft 20 provided in the electric pump 10 for a liquid rocket engine can also be applied to a system using ball bearings.

According to an embodiment of the present invention, the electric motor unit 50 may be provided integrally with the rotation shaft 20. Accordingly, according to an embodiment of the present invention, the structure of the liquid rocket engine can be simplified, the launch weight can be reduced, and energy efficiency can be increased.

In addition, according to an embodiment of the present invention, both the liquid oxygen pump unit 30 and the fuel pump unit 40 are applied to one rotating shaft 20 on which the electric motor unit 50 is integrated. In addition, by supporting the rotating shaft 20 through the hybrid fluid bearing 100 according to the first embodiment of the present invention, the dynamic stability of the rotating body, that is, the rotating shaft 20, can be improved, A lightweight pump system can be provided.

Referring to FIG. 3, as described above, the hybrid fluid bearing 100 according to the first embodiment of the present invention, which supports the rotation of the rotating shaft 20 of the electric pump 10 for a liquid rocket engine, is a bearing housing. It may be formed to include (110), a bearing sleeve 120, a compliant damper 130, and a spring ring seal (140).

At this time, for lubrication of the hybrid fluid bearing 100, liquid oxygen or liquid fuel is pressurized at a high pressure at the same time as the electric pump (10 in FIG. 1) is operated and supplied to the bearing through the bearing housing 110 or a separate supply pipe. It may be supplied to the space (gap; G) between the housing 110 and the bearing sleeve 120.

Pressurized fluid, such as liquid oxygen or liquid fuel, supplied to the gap G, which is the space between the bearing housing 110 and the bearing sleeve 120, is supplied to the inside of the bearing sleeve 120 (lower side of the bearing sleeve based on the drawing) and the bearing. It may be supplied again to one side (right side in the drawing) of the sleeve 120.

Here, the pressurized fluid supplied to the gap (G) between the bearing housing 110 and the bearing sleeve 120 can flow into the interior of the bearing sleeve 120, and a separate supply pipe is connected to the bearing sleeve 120. It may be connected and supplied to the inside of the bearing sleeve 120 therefrom.

The bearing housing 110 may be mounted in a ring-coupled form on the outer diameter surface of the rotating shaft 20. The bearing housing 110 may be mounted on the outer diameter surface of the rotating shaft 20 via the bearing sleeve 120 and the compliant damper 130.

That is, the bearing housing 110 has an outer diameter of the rotating shaft 20 in order to protect the parts or devices constituting the hybrid fluid bearing 100, including the bearing sleeve 120 and the compliant damper 130, from the external environment. It can be mounted in a ring-coupled form on the surface.

According to the first embodiment of the present invention, the bearing housing 110 may include a housing body 111.

The housing body 111 forms the exterior of the bearing housing 110. The housing body 111 may have its center open in the axial direction to allow insertion of the rotating shaft 20. For example, the housing body 111 may be provided in a hollow cylindrical or ring shape.

The bearing sleeve 120 may be mounted between the rotating shaft 20 and the bearing housing 110. At this time, the bearing sleeve 120 may have a gap G between the bearing sleeve 120 and the rotating shaft 20. Additionally, the bearing sleeve 120 may have a gap G between the bearing housing 110 and the bearing sleeve 120 .

As described above, the gap G between the bearing sleeve 120 and the rotating shaft 20 and the gap G between the bearing sleeve 120 and the bearing housing 110 are pressurized with liquid oxygen or liquid fuel. Fluid may be supplied.

According to the first embodiment of the present invention, the bearing sleeve 120 may include a sleeve body 121.

The sleeve body 121 may be axially open in the center to allow insertion of the rotating shaft 200. This sleeve body 121 may be provided in a cylindrical or ring shape.

At this time, the sleeve body 121 may have an outer diameter smaller than the inner diameter of the housing body 111. Accordingly, the sleeve body 121 can be assembled to the housing body 111 in a form that is inserted into the inner diameter surface of the housing body 111.

According to the first embodiment of the present invention, the bearing sleeve 120 may further include a guide hole 123.

The guide hole 123 may be formed on the other longitudinal side (right side in the drawing) of the gap G formed between the bearing housing 110 and the bearing sleeve 120. These guide holes 123 can guide liquid oxygen or liquid fuel pressurized into the gap G between the bearing housing 110 and the bearing sleeve 120 toward the rotating shaft 20.

Meanwhile, the hybrid fluid bearing 100 according to the first embodiment of the present invention may further include a bearing sleeve anti-rotation pin 160.

The anti-rotation pin 160 may be provided between the bearing housing 110 and the bearing sleeve 120. This anti-rotation pin 160 is supported by the bearing housing 110 when the rotary shaft 20 rotates and can restrict the rotation of the bearing sleeve 120.

Accordingly, the bearing sleeve 120 may include a receiving groove 124. The receiving groove 124 can accommodate the other longitudinal end of the anti-rotation pin 160, the longitudinal end of which is fixed to the bearing housing 110. That is, the bearing sleeve 120 can be very loosely assembled with the anti-rotation pin 160 through the receiving groove 124. In other words, when the other longitudinal end of the anti-rotation pin 160 is accommodated in the receiving groove 124, the inner surface of the receiving groove 124 and the anti-rotation pin 160 may have a gap.

This means that with the bearing sleeve 120 connected to the bearing housing 110 through the anti-rotation pin 160, the dynamic and static load conditions, alignment, assembly conditions, thermal balance conditions, etc. acting on the hybrid fluid bearing 100. This is to not only allow the position of the bearing sleeve 120 to be determined freely, but also to prevent the bearing sleeve 120 from being restricted by the bearing housing 110.

As another example, when the hybrid fluid bearing 100 is provided as a ball bearing, the outer ring assembly of the ball bearing may be very loosely assembled with the anti-rotation pin 160.

According to the first embodiment of the present invention, the bearing sleeve 120 is only restricted from rotating by the anti-rotation pin 160, and can freely move between the bearing housing 110 and the rotating shaft 20. .

At this time, a wave spring (not shown) with very low rigidity may be fixed to one or both sides of the bearing sleeve 120 in the longitudinal direction to restrain the axial movement of the bearing sleeve 120.

Continuing with reference to FIG. 3 , the compliant damper 130 may be provided in the gap G formed between the bearing housing 110 and the bearing sleeve 120. The compliant damper 130 may be fixed in such a way that its upper and lower ends are in close contact with the bearing housing 110 and the bearing sleeve 120, respectively.

According to the first embodiment of the present invention, the compliant damper 130 may be provided as a wire mesh damper.

Although the wire mesh damper has high rigidity and damping force, its structural characteristics may not vary significantly depending on the characteristics of the working fluid and operating temperature. In addition, the wire mesh damper can significantly improve the dynamic stability of the rotating shaft 20 by imparting additional rigidity and damping to the hybrid fluid bearing 100, and can maintain the bearing housing 110 and the bearing housing 110 even under extreme temperature conditions such as extremely low temperatures. By acting as a buffer against deformation of the bearing sleeve 120, the operational reliability of the hybrid fluid bearing 100 can be greatly improved.

In addition, the wire mesh damper provides system damping that can be operated stably without damage even at operating speeds where the rotating body, that is, the rotating shaft 20, operates near or above the critical speed, and transmits from the rotating shaft 20 By insulating the exciting force transmitted from the bearing housing 110 from the exciting force transmitted from the bearing housing 110, the lifespan of each element component can be extended and machine stability can be improved.

However, the wire mesh damper is only an example, and the compliant damper 130 in the first embodiment of the present invention is not specifically limited to the wire mesh damper.

For example, in addition to the wire mesh damper, the compliant damper 130 may be provided as one selected from a bump foil, an elastomeric damper, a wave spring, a wire mesh damper, a coil spring, a cantilever beam foil, and a wing foil.

A spring ring seal 140 may be provided in the gap G formed between the bearing housing 110 and the bearing sleeve 120. This spring ring seal 140 can define the degree of the gap (G). That is, the width of the gap G formed between the bearing housing 110 and the bearing sleeve 120 may be determined by the spring ring seal 140 installed between the bearing housing 110 and the bearing sleeve 120.

According to the first embodiment of the present invention, the spring ring seal 140 seals one side in the longitudinal direction of the gap G where the compliant damper 130 is provided, thereby sealing the bearing housing 110 and the bearing sleeve 120. Liquid oxygen or liquid fuel supplied under pressure can be allowed to flow to the other side of the gap (G) in the longitudinal direction.

According to the first embodiment of the present invention, the outer diameter of the spring ring seal 140 is fixed to the inner diameter surface of the bearing housing 110, and the inner diameter of the spring ring seal 140 is fixed to the outer diameter surface of the bearing sleeve 120. It can be.

At this time, according to the first embodiment of the present invention, the diameter of the axial inner end and the outer end of the spring ring seal 140 may be different.

As shown in FIGS. 4 and 5, the spring ring seal 140 may be provided in a shape in which the diameter of the axial inner end is relatively smaller than the diameter of the axial outer end. Additionally, the spring ring seal 140 may be provided in the form of a thin, elastic ring.

Accordingly, during assembly, when the spring ring seal 140 is pushed between the bearing housing 110 and the bearing sleeve 120, the spring ring seal 140 contacts the bearing housing 110 and the bearing sleeve 120 and becomes elastic. It can be transformed. As a result, the spring ring seal 140 can be easily inserted between the bearing housing 110 and the bearing sleeve 120.

In this way, the spring ring seal 140, which is inserted and fixed between the bearing housing 110 and the bearing sleeve 120 and defines the degree of the gap (G) formed by the bearing housing 110 and the bearing sleeve 120, is the above-mentioned One side of the gap (G) in the longitudinal direction can be sealed.

Therefore, the spring ring seal 140 is the space between the bearing housing 110 and the bearing sleeve 120 through the bearing housing 110, that is, the gap (G) formed between the bearing housing 110 and the bearing sleeve 120. It serves to seal one side of the gap (G) in the longitudinal direction so that liquid oxygen or liquid fuel supplied under pressure can flow to the other side of the gap (G) in the longitudinal direction, and at the same time, elastic deformation of the compliant damper (130) Accordingly, the rotating shaft 20 may be elastically deformed in the radial direction.

Accordingly, the elastic deformation of the compliant damper 130 may not be restricted by the spring ring seal 140.

Meanwhile, the spring ring seal 140 also serves as a centering spring that fixes the radial position of the bearing sleeve 120, that is, ensures that the eccentricity of the bearing sleeve 120 is fixed close to 0. can do.

Since this centering spring holds the structural characteristics of the compliant damper 130 in a position where they change linearly, it can increase the accuracy of predicting and analyzing the characteristics of the compliant damper 130. Accordingly, accuracy and reliability can be improved when designing a rotating system.

In addition, the centering spring has the advantage of reducing the amplitude of change in the vibration of the rotating body due to unbalanced mass conditions caused by the balancing operation of the rotating body, and thus reducing sensitivity to the balancing operation.

In general, the compliant damper 130 has the disadvantage of being difficult to predict because it behaves non-linearly when it has a large amount of deformation at a large eccentric position.

The pressurized fluid supplied to the gap (G) between the bearing housing 110 and the bearing sleeve 120, which is configured to flow in only one direction by the spring ring seal 140, flows on one side of the bearing sleeve 120. A large amount may flow into the (right side of the drawing).

This form can allow the motor 51 to be cooled more efficiently. This may mean that the heat generated from the motor 51 can be managed more efficiently by assisting the cooling passage formed inside the motor housing.

In addition, the pressurized fluid supplied to the gap (G) formed between the bearing housing 110 and the bearing sleeve 120 also serves to cool one side of the hybrid fluid bearing 100, thereby improving the life and longevity of the hybrid fluid bearing 100. It contributes to improving reliability.

Additionally, this type has the advantage of securing a larger amount of working fluid supplied for lubrication of the hybrid fluid bearing 100 and minimizing the decrease in efficiency of the electric pump (10 in FIG. 1).

Here, the cavitation of the working fluid supplied under pressure to the gap (G) formed by the bearing housing 110 and the bearing sleeve 120 is difficult to predict and its characteristics are also non-linear, making it difficult to predict and analyze the vibration characteristics of the rotating body. There is a problem.

To solve this problem, the spring ring seal 140 is used in the first embodiment of the present invention. When the spring ring seal 140 is used, the pressure of the working fluid pressurized and supplied to the gap G formed between the bearing housing 110 and the bearing sleeve 120 can be maintained at a certain level, and the pressure of the working fluid supplied under pressure can be maintained at a certain level in the gap G. Cavitation phenomenon that may occur can also be prevented.

Meanwhile, the hybrid fluid bearing 100 according to the first embodiment of the present invention may further include a noncontact annular seal 150.

The non-contact annular seal 150 may be provided at both ends of the bearing sleeve 120 in the longitudinal direction. This non-contact annular seal 150 can seal the gap G between the rotating shaft 20 and the bearing sleeve 120. Accordingly, liquid oxygen or liquid fuel supplied under pressure to the gap G between the bearing housing 110 and the bearing sleeve 120 can be prevented from flowing in the longitudinal direction of the rotating shaft 20.

That is, according to the first embodiment of the present invention, the non-contact annular seal 150 provided at both ends in the longitudinal direction of the bearing sleeve 120 is pressurized and supplied to the compliant damper 130 through the bearing housing 110. The amount of fluid leaking onto the surface of the rotating shaft 200 after passing through the bearing sleeve 120 in the axial direction can be minimized.

According to the first embodiment of the present invention, this non-contact annular seal 150 is divided into labyrinth seals, flat seals, floating seals, hole pattern seals, honeycomb seals, foil seals and pocket seals, depending on the pressure conditions and operating conditions. It can be provided with any one selected seal.

Hereinafter, a hybrid fluid bearing according to a second embodiment of the present invention will be described with reference to FIG. 6.

Figure 6 is a schematic diagram for explaining a hybrid fluid bearing according to a second embodiment of the present invention.

Referring to FIG. 6, the hybrid fluid bearing 200 according to the second embodiment of the present invention includes a bearing housing 210, a bearing sleeve 220, a compliant damper 130, a spring ring seal 140, and a non-contact annular It may be formed including a seal 150 and a rotation prevention pin 160.

Since the second embodiment of the present invention differs from the first embodiment of the present invention only in the structure of the bearing housing and bearing sleeve, the remaining identical components are assigned the same reference numerals and detailed descriptions thereof are provided. The explanation will be omitted.

According to the second embodiment of the present invention, the bearing housing 210 may include a housing body 211 and a first insertion groove 212.

The housing body 211 forms the exterior of the bearing housing 210. The housing body 211 may have its center open in the axial direction to allow insertion of the rotating shaft 20. For example, the housing body 211 may be provided in a hollow cylindrical or ring shape.

The first insertion groove 212 may be formed in the housing body 211. Specifically, the first insertion groove 212 may be formed in the depth direction from the inner diameter surface of the housing body 211. The outer diameter side of the spring ring seal 140 may be inserted into this first insertion groove 212.

Additionally, according to the second embodiment of the present invention, the bearing sleeve 220 may include a sleeve body 221 and a second insertion groove 222.

The sleeve body 221 may be axially open at the center to allow insertion of the rotating shaft 20. This sleeve body 221 may be provided in a cylindrical or ring shape.

At this time, the sleeve body 221 may have an outer diameter smaller than the inner diameter of the housing main body 211. Accordingly, the sleeve body 221 can be assembled to the housing body 211 in a form that is inserted into the inner diameter surface of the housing body 211.

The second insertion groove 222 may be formed in the sleeve body 221. Specifically, the second insertion groove 222 may be formed in the depth direction from the outer diameter surface of the sleeve body 221. The inner diameter side of the spring ring seal 140, whose outer diameter side is inserted into the first insertion groove 212, may be inserted into this second insertion groove 222.

As such, according to the second embodiment of the present invention, the outer diameter and inner diameter of the spring ring seal 140 are formed in the first insertion groove 212 and the sleeve body 221 respectively formed on the inner diameter surface of the housing body 211. ) is inserted into the second insertion groove 222 formed on the outer diameter surface. Accordingly, the spring ring seal 140 can be more stably fixed between the bearing housing 210 and the bearing sleeve 120.

Hereinafter, a hybrid fluid bearing according to a third embodiment of the present invention will be described with reference to FIGS. 7 and 8.

Referring to FIG. 7, the hybrid fluid bearing 300 according to the third embodiment of the present invention includes a bearing housing 210, a bearing sleeve 220, a compliant damper 130, a spring ring seal 340, and a non-contact annular It may be formed including a seal 150 and a rotation prevention pin 160.

Since the third embodiment of the present invention is different from the first and second embodiments of the present invention only in the structure of the spring ring seal, the same reference numerals are assigned to the remaining identical components and these Detailed description will be omitted.

According to the third embodiment of the present invention, the spring ring seal 340 has an outer diameter and an inner diameter of the first insertion groove 212 and the sleeve main body 221 formed on the inner diameter surface of the housing main body 211, respectively. It can be inserted into the second insertion groove 222 formed on the outer diameter surface.

At this time, according to the third embodiment of the present invention, the spring ring seal 340 may be provided in a cone shape with a gradually decreasing diameter. That is, based on the direction in which the spring ring seal 340 is assembled, the spring ring seal 340 may be provided in a form in which the diameter of the axial inner end is relatively smaller than the diameter of the axial outer end.

Hereinafter, a hybrid fluid bearing according to a fourth embodiment of the present invention will be described with reference to FIGS. 9 and 10.

Referring to FIG. 9, the hybrid fluid bearing 400 according to the fourth embodiment of the present invention includes a bearing housing 210, a bearing sleeve 220, a compliant damper 130, a spring ring seal 440, and a non-contact annular It may be formed including a seal 150 and a rotation prevention pin 160.

Since the fourth embodiment of the present invention is different from the first and second embodiments of the present invention only in the structure of the spring ring seal, the same reference numerals are assigned to the remaining identical components and these Detailed description will be omitted.

According to the fourth embodiment of the present invention, the spring ring seal 440 has a first insertion groove 212 and a sleeve body 221 formed on the outer diameter side and the inner diameter side of the housing body 211, respectively. ) can be inserted into the second insertion groove 222 formed on the outer diameter surface.

At this time, as shown in FIG. 10, according to the fourth embodiment of the present invention, the spring ring seal 440 may be provided as a spring ring seal with a C-shaped cross section.

Hereinafter, a hybrid fluid bearing according to a fifth embodiment of the present invention will be described with reference to FIGS. 11 and 12.

Referring to FIG. 11, the hybrid fluid bearing 500 according to the fifth embodiment of the present invention includes a bearing housing 210, a bearing sleeve 220, a compliant damper 130, a spring ring seal 540, and a non-contact annular It may be formed including a seal 150 and a rotation prevention pin 160.

Since the fifth embodiment of the present invention differs from the first and second embodiments of the present invention only in the structure of the spring ring seal, the same reference numerals are assigned to the remaining identical components and these Detailed description will be omitted.

According to the fifth embodiment of the present invention, the spring ring seal 540 has a first insertion groove 212 and a sleeve body 221 formed on the outer diameter side and the inner diameter side of the housing body 211, respectively. ) can be inserted into the second insertion groove 222 formed on the outer diameter surface.

At this time, as shown in FIG. 12, according to the fifth embodiment of the present invention, the spring ring seal 540 may be provided as a spring ring seal with an S-shaped cross section.

Meanwhile, Figure 13 is a cross-sectional view showing a spring ring seal according to a sixth embodiment of the present invention, and Figure 14 is a cross-sectional view showing a spring ring seal according to a seventh embodiment of the present invention.

As shown in FIG. 13, the spring ring seal 640 according to the sixth embodiment of the present invention may be provided as a spring ring seal with an M-shaped cross section.

Additionally, as shown in FIG. 14, the spring ring seal 740 according to the seventh embodiment of the present invention may be provided as a spring ring seal with a U-shaped cross section.

As described above, according to embodiments of the present invention, spring ring seals may be provided in various forms. These spring ring seals are simple to manufacture and process, do not require a large space for installation, have a very simple assembly process, are light in weight, and have the advantages of very simple adjustment of rigidity and elasticity for sealing characteristics and centering. .

Above, the present invention has been described in detail using preferred embodiments, but the scope of the present invention is not limited to the specific embodiments and should be interpreted in accordance with the appended claims. Additionally, those skilled in the art should understand that many modifications and variations can be made without departing from the scope of the present invention.

100; hybrid fluid bearing 110; bearing housing
111; Housing body 112; 1st insertion groove
120; bearing sleeve 121; sleeve body
122; second insertion groove 123; guide hall
124; acceptance home 130; compliant damper
140; spring ring seal 150; Non-contact annular seal
160; Anti-rotation pin 20; rotating shaft
30; Liquid oxygen pump unit 40; Fuel pump part
31, 41; inducer 32, 42; impeller
50; Electric motor unit 51; motor
52; stater 53; cooling jacket
10; electric pump

Claims (14)

A bearing housing mounted in a ring-coupled form on the outer diameter surface of the rotating shaft;
A bearing sleeve mounted between the rotating shaft and the bearing housing, having a first gap with the rotating shaft and a second gap with the bearing housing;
a compliant damper provided in the second gap; and
Liquid oxygen or liquid fuel is provided in the second gap to define the degree of the second gap, and is pressurized and supplied to the second gap by sealing one longitudinal side of the second gap where the compliant damper is provided. A spring ring seal that allows the first pressurized fluid consisting of to flow to the other side in the longitudinal direction of the second gap,
The second gap is created to allow the first pressurized fluid to flow in only one direction by the spring ring seal,
The bearing sleeve is formed on the other side of the second gap in the longitudinal direction and further includes a guide hole that guides the first pressurized fluid to the first gap,
The first pressurized fluid passes through the guide hole while flowing to the other side in the longitudinal direction of the second gap by the spring ring seal, and is pressurized and supplied to the first gap from a separate supply pipe connected to the bearing sleeve. A hybrid fluid bearing joined to a second pressurized fluid consisting of liquid oxygen or liquid fuel.
According to claim 1,
A hybrid fluid bearing further comprising a non-contact annular seal provided at both longitudinal ends of the bearing sleeve and sealing the second gap.
According to clause 2,
A hybrid fluid bearing, wherein the non-contact annular seal is any one selected from a labyrinth seal, a flat seal, a floating seal, a hole pattern seal, a honeycomb seal, a foil seal, and a pocket seal.
According to claim 1,
A hybrid fluid bearing wherein the compliant damper is one selected from a wire mesh damper, a bump foil, an elastomeric damper, a wave spring, a wire mesh damper, a coil spring, a cantilever beam foil, and a wing foil.
According to claim 1,
The spring ring seal is,
A hybrid fluid bearing in which the axial inner end and the outer end have different diameters, and are provided in a conical shape where the axial inner end has a relatively smaller diameter than the axial outer end.
According to claim 1,
The spring ring seal is a hybrid fluid bearing provided with any one spring ring seal selected from a C-type spring ring seal, an S-type spring ring seal, an M-type spring ring seal, and a U-type spring ring seal.
According to claim 1,
A hybrid fluid bearing wherein the outer diameter of the spring ring seal is fixed to the inner diameter surface of the bearing housing, and the inner diameter of the spring ring seal is fixed to the outer diameter surface of the bearing sleeve.
According to claim 1,
The spring ring seal is elastically deformed in the radial direction of the rotating shaft to enable elastic deformation of the compliant damper.
According to claim 1,
The bearing housing is,
a housing body whose center is axially open to enable insertion of the rotating shaft; and
A hybrid fluid bearing that is formed in the depth direction from the inner diameter surface of the housing main body and includes a first insertion groove into which the outer diameter side of the spring ring seal is inserted.
According to clause 9,
The bearing sleeve is,
a sleeve body whose center is axially open to enable insertion of the rotating shaft and has an outer diameter smaller than an inner diameter of the housing body; and
A hybrid fluid bearing that is formed in the depth direction from the outer diameter surface of the sleeve body and includes a second insertion groove into which the inner diameter side of the spring ring seal is inserted.
delete According to claim 1,
A hybrid fluid bearing further comprising an anti-rotation pin provided between the bearing housing and the bearing sleeve and supported by the bearing housing to restrict rotation of the bearing sleeve when the rotating shaft rotates.
According to claim 12,
A hybrid fluid bearing, wherein the bearing sleeve has a receiving groove for accommodating the other longitudinal end of the anti-rotation pin, the longitudinal end of which is fixed to the bearing housing.
a rotating shaft supported by a hybrid fluid bearing according to claim 1;
a liquid oxygen pump unit provided on one side in the longitudinal direction of the rotating shaft;
a fuel pump unit provided on the other side of the rotating shaft in the longitudinal direction; and
An electric motor unit is axially coupled to the rotary shaft to provide rotational driving force to the rotary shaft, and is provided behind the fuel pump unit or between the liquid oxygen pump unit and the fuel pump unit.
The hybrid fluid bearing is a combination of a journal bearing and a thrust bearing or a combination of a plurality of ball bearings.