Aerostatic thrust bearing and method of aerostatically supporting a thrust load

Abstract

A scroll compressor includes a first scroll member, a second scroll member, and an aerostatic thrust bearing. The aerostatic thrust bearing forms a gas layer between the second scroll member and a fixed support member to support the second scroll member when the second scroll member rotates and / or moves along an orbit. A method of supporting a rotating / orbiting scroll member in a scroll compressor is also disclosed. The method includes supplying pressurized gas to the aerostatic thrust bearing so that a gas layer is formed between the rotating / orbiting scroll member and the fixed support member.

Description

[0001] This application is a divisional application of an invention patent with an application date of June 15, 2018, application number 201810620817.7, and invention name “Aerostatic thrust bearing and method for aerostatically supporting thrust loads”. Technical Field

[0002] The present disclosure relates to bearings in scroll compressors and methods of providing lubrication in scroll compressors. Background Art

[0003] Scroll compressors utilize intermeshing scroll members to compress fluids. Heating, ventilation, air conditioning, and refrigeration systems ("HVACR") may use scroll compressors to compress gaseous refrigerants. A first scroll member may be intermeshed with a second scroll member. The second scroll member rotates or orbits (non-fixed) relative to the first scroll member. During operation, the second scroll member rotates or orbits so that a certain volume of gas (e.g., refrigerant) is compressed between the intermeshing scroll members. A thrust bearing may be configured to support the second non-fixed scroll member in an axial direction. A crankshaft within a scroll compressor may rotate the second non-fixed scroll member, and the bearing may support the crankshaft as the crankshaft rotates. Summary of the invention

[0004] A scroll compressor utilizes two scroll members with intermeshing spiral wraps to compress a gas such as a refrigerant. The first scroll member has a spiral wrap. The second scroll member has a spiral wrap and rotates or orbits relative to the first scroll member so that a gas volume is trapped between the intermeshing spiral wraps of the first and second scroll members. As the second scroll member rotates or orbits relative to the first scroll member, the trapped gas volume is subsequently compressed. When the gas is compressed between the first and second scroll members, the gas can exert a force in the axial direction. This force may also be referred to as a thrust load.

[0005] In one embodiment, the scroll compressor includes a fixed support member for supporting the second scroll member in an axial direction. The scroll compressor also includes an aerostatic thrust bearing for supporting the second scroll member in an axial direction. The aerostatic thrust bearing supports the second scroll member so that the thrust load of the second scroll member does not significantly change the mutual meshing position of the second scroll member and the first scroll member in the axial direction. The aerostatic thrust bearing supports the second scroll member so that the axial end of the spiral cladding of the second scroll member remains in contact with the substrate of the first scroll member. The aerostatic thrust bearing includes a surface of the second scroll member, a surface of the fixed support member, and a gas distribution structure. In one embodiment, the fixed support member is a structure in the scroll compressor that has a fixed position relative to the second scroll member. The fixed support member also includes a surface facing the substrate. In one embodiment, the fixed support member is part of a bearing seat. The gas distribution structure in the embodiment can be located on the surface of the second scroll member and / or on the surface of the fixed support member.

[0006] In one embodiment, the gas distribution structure is supplied with pressurized gas and distributes the pressurized gas over a surface area between the second scroll member and the fixed support member. For example, the gas distribution structure is a porous material that distributes the received pressurized gas over the surface area. During normal operation of the scroll compressor, a thrust load is applied to the second scroll member. The thrust load on the second scroll member can push the surface of the fixed support member against the surface of the second scroll member. However, in one embodiment, the gas distribution structure distributes the pressurized gas flow between the surfaces of the second scroll member and the fixed support member. Since the pressurized gas is distributed between the surfaces of the second scroll member and the fixed support member, the flowing pressurized gas prevents surface contact (e.g., during normal operation).

[0007] In one embodiment, the aerostatic thrust bearing includes a gas distribution structure having an inner radial seal and an outer radial seal respectively located on the second scroll member or the fixed support member. The gas distribution structure also includes one or more openings in the second scroll member or the fixed support member. During operation, the gas distribution structure distributes pressurized gas to the space between the second scroll member and the fixed support member in the axial direction and between the radial seals in the radial direction. During normal operation of the scroll compressor, the thrust load on the second scroll member applies force in the axial direction. However, in one embodiment, the pressurized gas flows into the space between the second scroll member and the fixed support member. When the pressurized gas flows through the space between the surface of the second scroll member and the fixed support member, the flowing pressurized gas prevents surface contact (e.g., during normal operation), and the radial seal provides flow resistance to the compressed gas that easily flows out of the space between the second scroll member and the surface of the fixed support member.

[0008] In one embodiment, the thrust load pushes the second vortex member to overcome the distributed pressurized gas flowing between the second vortex member and the fixed support member. In this way, the distributed pressurized gas is formed as a layer (e.g., a film) between the second vortex member and the fixed support member. When the second vortex member pushes the flowing layer of the pressurized fluid, the second vortex member compresses the flowing pressurized gas layer. In order to move the second vortex member axially, the second vortex member in the embodiment further compresses the flowing distributed pressurized gas layer. When the pressurized gas layer has been compressed (e.g., pressurized), a large amount of force corresponds to a small amount of compression. In this way, the flowing pressurized gas layer attenuates and / or absorbs the thrust load of the second vortex member. Therefore, the aerostatic thrust bearing supports the second vortex member axially. In one embodiment, the gas distribution structure utilizes the working fluid of the compressor (e.g., refrigerant, refrigerant mixture, etc.) as the pressurized gas.

[0009] In one embodiment, a method is intended to support a rotating or orbiting scroll member in a scroll compressor. In a scroll compressor, a fixed support member is positioned within the scroll compressor so that the surface of the fixed support member faces the surface of the rotating or orbiting scroll member. The method in an embodiment includes providing a gas distribution structure on the surface of the fixed support member or the surface of the rotating or orbiting scroll member, supplying pressurized gas to the gas distribution structure, and the gas distribution structure forms a gas layer between the rotating or orbiting scroll member and the fixed support member. The gas layer is configured to support the thrust load of the rotating or orbiting scroll member.

[0010] In one embodiment, a scroll compressor utilizes one or more aerostatic bearings to support a crankshaft as the crankshaft rotates. In one embodiment, one or more aerostatic radial bearings support the crankshaft radially as the crankshaft rotates. The aerostatic radial bearing for supporting the crankshaft includes a radial surface (e.g., a journal surface) of the crankshaft, a surface of a fixed support member facing the crankshaft, and a gas distribution structure. In one embodiment, pressurized gas is supplied to the gas distribution structure, and the aerostatic radial bearing forms a flowing pressurized gas layer between the radial surface of the crankshaft and the surface of the fixed support member facing the crankshaft. The gas layer supports the crankshaft radially as the crankshaft rotates. In one embodiment, the gas distribution structure for the aerostatic radial bearing may be located on the radial surface of the crankshaft and / or on the surface of the fixed support member.

[0011] In one embodiment, a crankshaft aerostatic thrust bearing supports the crankshaft in the axial direction when the crankshaft rotates. The crankshaft aerostatic thrust bearing includes an axial end face of the crankshaft, a surface facing the axial end face of the crankshaft, and a gas distribution structure. In one embodiment, compressed gas is supplied to the gas distribution structure so that the crankshaft aerostatic thrust bearing forms a gas layer between the axial end face of the crankshaft and the surface facing the axial end face. The gas layer supports the crankshaft in the axial direction when the crankshaft rotates. In one embodiment, the gas distribution structure for the crankshaft aerostatic thrust bearing may be located on the axial surface of the crankshaft and / or the axial surface of the fixed support member.

[0012] In one embodiment, an aerostatic radial bearing is provided around an eccentric end of a crankshaft engaged with a second scroll member. The aerostatic radial bearing includes a radial surface of the eccentric end of the crankshaft (e.g., a journal surface of the eccentric end), a surface of the second scroll member (e.g., an inner surface of a sleeve of the second scroll member), and a gas distribution structure. In one embodiment, pressurized gas is supplied to the gas distribution structure so that the aerostatic radial bearing forms a gas layer between an outer radial surface of an outer surface of the eccentric end and a surface of the second scroll member. The aerostatic radial bearing may allow the eccentric end to transfer its motion to the second scroll member due to rotation without transferring its rotation. In one embodiment, the gas distribution structure of the aerostatic radial bearing for the eccentric end of the crankshaft may be located on a surface of the second scroll member and / or on a radial surface of the eccentric end of the crankshaft.

[0013] In one embodiment, for example, as described above, one or more of the bearings of the scroll compressor can use pressurized gas instead of other lubricants (e.g., oil), so that the compressor is an oil-free scroll compressor. In one embodiment, for example, as described above, all bearings of the scroll compressor can use pressurized gas instead of other lubricants (e.g., oil), so that the compressor is an oil-free scroll compressor. In one embodiment, the oil-free scroll compressor can utilize the working fluid of the compressor (e.g., refrigerant, refrigerant mixture, etc.) as the pressurized fluid. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 A schematic diagram of a refrigerant circuit including a compressor, a condenser, an expansion device and an evaporator is shown.

[0015] Figure 2 A cross section of an embodiment of a vertical single-stage scroll compressor including an aerostatic thrust bearing including a gas distribution structure in the bearing housing is shown.

[0016] Figure 3A Shows Figure 2 An enlarged cross-sectional view of an aerostatic thrust bearing in a vertical single-stage scroll compressor is shown.

[0017] Figure 3B A schematic diagram of an aerostatic thrust bearing in an embodiment of a scroll compressor is shown.

[0018] Figure 4 A top view of a bearing housing and gas distribution structure in an embodiment of a scroll compressor is shown.

[0019] Figure 5 A top view of a bearing housing and gas distribution structure in an embodiment of a scroll compressor is shown.

[0020] Figure 6 A cross-sectional view of an end portion of an orbiting scroll and a corresponding bearing seat in an embodiment of a scroll compressor is shown.

[0021] Figure 7 A cross-sectional view of an embodiment of a vertical single-stage scroll compressor including an aerostatic thrust bearing including a gas distribution structure in the orbiting scroll is shown.

[0022] Figure 8 A cross-sectional view of an embodiment of an oil-free vertical single-stage scroll compressor including aerostatic bearings in the orbiting scroll and crankshaft is shown.

[0023] Fig. 9 Shows Figure 8 A partial cross-sectional view of the aerostatic radial bearing viewed along direction 9-9.

[0024] Fig. 10A An embodiment including an axial dynamic seal is shown. Figure 8 Magnified view of the crankshaft aerostatic thrust bearing.

[0025] Fig. 10B An embodiment including a radial dynamic seal is shown. Figure 8 Magnified view of the crankshaft aerostatic thrust bearing.

[0026] Fig.11 A cross-sectional view of one embodiment of an oil-free vertical single-stage scroll compressor is shown that includes an aerostatic bearing for supporting a crankshaft and an orbiting scroll.

[0027] Fig.12 A cross-sectional view of an embodiment of an oil-free vertical single-stage compressor including aerostatic bearings in the orbiting scroll and crankshaft is shown.

[0028] Fig.13 A cross-sectional view of an embodiment of a vertical single-stage scroll compressor including a gas distribution structure and a radially sealed aerostatic thrust bearing is shown.

[0029] Fig.14 Shows Figure 2An enlarged cross-sectional view of an aerostatic thrust bearing in a vertical single-stage scroll compressor is shown.

[0030] Fig.15 A cross-sectional view of one embodiment of an oil-free vertical single-stage scroll compressor is shown, the compressor including an aerostatic bearing supporting a crankshaft and an aerostatic thrust bearing supporting an orbiting scroll including a radial seal supporting the orbiting scroll. DETAILED DESCRIPTION

[0031] A scroll compressor compresses gas between the intermeshing spiral wraps of its scroll members. Since the scroll members compress gas between their spiral wraps, the compressed gas can push the non-fixed scroll member in an axial direction. This thrust, also known as a thrust load, may cause the non-fixed scroll member to become incorrectly positioned axially and / or contact other internal parts of the scroll compressor (e.g., a fixed support member, a bearing seat supporting the crankshaft). When positioned incorrectly, since the non-fixed scroll member does not contact the fixed scroll member, the end of the spiral wrap of the non-fixed scroll member may not form a seal with the base plate of the fixed scroll member. The rotation or orbiting of the non-fixed scroll member can amplify the thrust load, particularly toward the outer diameter of the base plate of the non-fixed scroll member.

[0032] Some previous scroll compressors have utilized pressurized oil in the space behind the non-fixed scroll member to support the non-fixed scroll member in the axial direction. Some previous scroll compressors have used oil-based thrust bearings between the fixed support member (e.g., bearing seat) of the scroll compressor and the non-fixed scroll member to support the non-fixed scroll member in the axial direction. In some such previous scroll compressors, the thrust bearing typically includes an additional piece placed between the non-fixed scroll member and the fixed support member. These previous thrust bearings also require flowing pressurized oil to support the non-fixed scroll member.

[0033] Some previous scroll compressors have used aerodynamic air bearings, which may also be referred to as thrust foil bearings, to support the non-fixed scroll member. The aerodynamic air bearing forms a dynamic cushion of air between the non-fixed scroll member and the support structure to support the non-fixed scroll member. The aerodynamic air bearing relies on the movement (e.g., rotation or orbital motion) of the non-fixed scroll member to provide support, which causes contact between the non-fixed scroll member and the support structure when the scroll compressor is stopped and started. However, the aerodynamic air bearing provides weaker support relative to the area of ​​its surface (e.g., the support surface facing the support structure) because it requires a support surface that includes an inactive surface.

[0034] Embodiments of scroll compressors that utilize an aerostatic thrust bearing to support a non-stationary scroll member are disclosed herein. In one embodiment, the aerostatic thrust bearing is supplied with pressurized gas. The aerostatic thrust bearing includes a gas distribution structure that distributes the pressurized gas between the non-stationary scroll member and the fixed support member of the scroll compressor. In this manner, a layer of flowing pressurized gas is formed to support the non-stationary scroll member and the thrust load. The aerostatic thrust bearing is an "aerostatic" type bearing because it forms a layer of flowing gas between surfaces from which the gas flows. "Aerostatic" type bearings are different from "aerodynamic" type bearings.

[0035] In one embodiment, the aerostatic thrust bearing provides support for the non-fixed scroll member without contacting the non-fixed scroll member. This is advantageous because the aerostatic thrust bearing in one embodiment provides lower friction losses because it does not require any solid-solid contact to provide support for the non-fixed scroll member. In addition, the friction between the flowing pressurized gas layer and the non-fixed scroll member is less than the friction between the liquid lubricant and the non-fixed scroll member. Less friction produces less shear stress in the lubricant. The aerostatic thrust bearing in one embodiment is advantageous because less energy is lost due to friction and / or shear stress of the pressurized gas compared to thrust bearings using liquid lubricants (e.g., oil). In one embodiment, the aerostatic thrust bearing supplies pressurized gas to support the non-fixed scroll member. In one embodiment, the flow of pressurized gas does not depend on the rotation of the non-fixed scroll member. Thus, the support provided by the aerostatic thrust bearing in one embodiment does not rely on the rotation of the non-fixed scroll member or the crankshaft to provide support for the non-fixed scroll member. Aerostatic thrust bearings are advantageous because they can provide support during the start-up and stop of the compressor. Furthermore, in one embodiment, an aerostatic thrust bearing is advantageous because it does not require an inactive surface to support the non-stationary scroll member.

[0036] Embodiments of the scroll compressor may also include one or more aerostatic bearings to support the crankshaft when the crankshaft of the compressor rotates. One embodiment may also include an aerostatic radial bearing for an end (e.g., an eccentric end) of the crankshaft, which engages a non-fixed scroll member. Each aerostatic bearing may include a gas distribution structure. Each aerostatic bearing may utilize pressurized gas to form a gas layer or layers that support the crankshaft when the crankshaft rotates. In this way, the scroll compressor may be an oil-free scroll compressor. In one embodiment, the scroll compressor may be a scroll compressor for an HVACR system, and the pressurized gas may be a refrigerant.

[0037] HVACR systems can be used to cool or heat one or more conditioned spaces. HVACR systems can utilize a working fluid (e.g., a refrigerant) in a loop to cool a type of process fluid (e.g., air, water). For example, HVACR systems may cool an area in some cases by operating a refrigerant in a heat exchange relationship with the air. The cooled air can then be ventilated to an area to cool the area.

[0038] Figure 1 is a schematic diagram of a heat transfer loop 1 according to one embodiment. The heat transfer loop 1 generally includes a compressor 2, a condenser 3, an expansion device 4, and an evaporator 5. In one embodiment, the heat transfer loop 1 can be modified to include additional components. For example, in one embodiment, the heat transfer loop 1 can include an economizer heat exchanger, one or more flow control devices, a storage tank, a dryer, a suction liquid heat exchanger, etc.

[0039] The heat transfer loop 1 is generally applicable to various systems (e.g., vapor compression systems) used to control environmental conditions (e.g., temperature, humidity, air quality) in a space, which is generally referred to as a conditioned space. Exemplary systems including the heat transfer loop 1 include, but are not limited to, HVACR systems, transport refrigeration systems, etc.

[0040] The components of the heat transfer loop 1 are fluidically connected. The heat transfer loop 1 can be configured as a cooling system (e.g., a fluid cooler for HVACR, an air conditioning system, etc.) capable of operating in a cooling mode, and / or the heat transfer loop 1 can be configured to operate as a heat pump system that can operate in a cooling mode and a heating / defrost mode.

[0041] The heat transfer loop 1 described applies known principles of gas compression and cooling. The heat transfer loop can be configured to heat or cool a process fluid (e.g., water, air). In one embodiment, the heat transfer loop 1 can represent a chiller that cools a process fluid such as water. In one embodiment, the heat transfer loop 1 can represent an air conditioner and / or a heat pump that includes a process fluid such as air.

[0042] In the operation of the refrigerant circuit 1, the working fluid (e.g., refrigerant) flows from the evaporator 5 into the compressor 2 in a gaseous state at a relatively low pressure. The compressor 2 compresses the gas into a high pressure state, which also heats the gas. After compression, the relatively high pressure and high temperature gas flows from the compressor 2 to the condenser 3. In addition to the refrigerant flowing through the condenser 3, an external fluid (e.g., external air, external water, chiller water, etc.) also flows through the condenser 3. According to known principles, the external fluid absorbs heat from the working fluid as the working fluid flows through the condenser 3. The working fluid condenses into a liquid and then flows into the expansion device 4. The expansion device 4 reduces the pressure of the working fluid. The pressure reduction allows the working fluid to expand and convert into a mixed vapor / liquid state. Then the relatively low temperature vapor / liquid working fluid flows into the evaporator 5. The process fluid (e.g., air, water, etc.) also flows through the evaporator 5. According to known principles, the working fluid absorbs heat from the process fluid as the process fluid flows through the evaporator 5. As the working fluid absorbs heat, the working fluid evaporates into vapor. The working fluid then returns to the compressor 2. When the heat transfer circuit 1 is operating, for example, in cooling mode, the above process continues.

[0043] Figure 2 A cross section of an embodiment of a scroll compressor 10 is shown having an aerostatic thrust bearing for supporting a non-stationary scroll member 14. The aerostatic thrust bearing includes a gas distribution structure 64 located on a surface of a bearing seat 58. The embodiment shown herein is a vertical single-stage scroll compressor, but it should be understood that the description and features described herein may also be applied to multi-stage scroll compressors, tilted scroll compressors, and / or horizontal scroll compressors. In addition, it should be recognized that the description and features described herein may be applied to scroll compressors having a co-orbiting scroll or a co-rotating scroll.

[0044] Figure 2 The scroll compressor 10 shown may also be, for example, the above-mentioned Figure 1 The compressor 2 in the refrigerant circuit 1.

[0045] Known aspects of applying scroll compressors for compression, scroll compressor 10 can utilize two intermeshing scroll members 12, 14 to compress a certain volume of gas (e.g., trapped volume 16, trapped volume 17) between their respective intermeshing spiral wraps 18, 20. Scroll compressor 10 may have a non-fixed scroll member 14 and a fixed scroll member 12. Fixed scroll member 12 is a scroll member located in a fixed position within an outer housing 22, and is constructed or designed not to rotate or move (e.g., orbit) during operation of scroll compressor 10. Fixed scroll member 12 may be referred to as a fixed scroll, a non-orbiting scroll, or a fixed scroll. In one embodiment, fixed scroll 12 may be directly attached to the outer housing 22 of scroll compressor 10. Fixed scroll 12 has a base plate 13 and a spiral wrap 18 protruding in the direction toward non-fixed scroll 14.

[0046] The non-stationary scroll member 14 is a scroll member that engages with the end of the crankshaft 24. During the operation of the scroll compressor, the non-stationary member orbits relative to the fixed scroll member 12. The non-stationary scroll member 14 may also be referred to as an orbiting scroll member or an orbiting scroll member, etc. The orbiting scroll member 14 has a base plate 26 and a spiral shroud 20 that protrudes in a direction toward the fixed scroll member 12. The base plate 26 may also have a rear surface 28 that faces in a direction generally opposite to the spiral shroud 20.

[0047] like Figure 2 As shown, the fixed scroll 12 and the orbiting scroll 14 are in a correct meshing position corresponding to each other. When properly positioned, the axial end of the spiral wrap 20 of the orbiting scroll 14 (e.g., the end of the spiral wrap that is not connected to the base plate 26) contacts the base plate 13 of the fixed scroll 12. Similarly, the axial end of the spiral wrap 18 of the fixed scroll 12 (e.g., the end of the spiral wrap 18 that is not connected to the base plate 13) contacts the base plate 26 of the orbiting scroll 14. This contact creates an axial seal between the spiral wraps 18, 20 and each opposing base plate 13, 26. The seal prevents compressed gas from escaping from one trapped volume to another trapped volume (e.g., from the trapped volume 16 to the trapped volume 17). In the example shown in FIG. Figure 2 In the vertical scroll compressor 10 shown, the axial direction is also a vertical direction.

[0048] In one embodiment, the axial ends of one or both of the spiral wraps 18, 20 may include a tip seal to help facilitate sealing between the spiral wrap and the opposing substrates 13, 26. However, if the orbiting scroll 14 moves in the axial direction, the sealing of the trapped volumes (e.g., trapped volumes 16, 17) described may not be adequate. Typically, due to its fixed position, movement of the fixed components is not a problem. The lack of such a seal can result in, for example, a loss of efficiency of the scroll compressor 10 or an inability of the scroll compressor 10 to compress the inlet gas.

[0049] In one embodiment, the scroll compressor 10 may include a coupling device, such as Figure 2 . In one embodiment, a coupling device (such as Oldham coupling 30) and radial bearing 48 can be used so that radial motion (relative to crankshaft 24) of eccentric end 56 is transmitted to orbiting scroll 14 without transmitting rotational motion. Therefore, in one embodiment, orbiting scroll 14 orbits relative to fixed scroll 12 without rotating.

[0050] It should be understood that, in one embodiment, the spiral wrap 18, 20 need not be a perfect spiral (e.g., Archimedean spiral, logarithmic spiral). For example, in one embodiment, the curvature of the spiral wrap 18, 20 may be non-constant and / or the ends of one (or both) of the spiral wrap 18, 20 may be non-spiral (e.g., most of the spiral wrap 18 may be spiral, but the end portions may protrude radially).

[0051] In one embodiment, the housing 22 of the scroll compressor 10 has an upper portion 32A and a lower portion 32B. In one embodiment, the volume contained within the upper portion 32A can be defined as an upper volume 34A of the scroll compressor 10, and the volume contained within the lower portion 32B can be defined as a lower volume 34B. Figure 2 As shown in the embodiment of the present invention, the upper volume 34A and the lower volume 34B are fluidly separated by the fixed scroll 12 and the orbiting scroll 14. In one embodiment, the gas can flow only between the volumes 34A, 34B by traveling through the intermeshing scrolls 18, 20 (and being compressed) or the gas distribution structure 64 (described below). However, in one embodiment, the volumes 34A, 34B can be fluidly separated by other components of the scroll compressor 10 or other components and the scrolls 12, 14, for example.

[0052] like Figure 2As shown, in one embodiment, the intermeshing spiral covers 18, 20 have a discharge volume 40. In the scroll compressor 10, the discharge volume 40 is the volume where the intermeshing spiral covers 18, 20 terminate and the compressed gas leaves the scroll members 12, 14. The discharge volume 40 is fluidly connected to the upper volume 34A of the scroll compressor 10. A valve 42 (e.g., a check valve) can regulate the flow of pressurized gas between the upper volume 34A and the discharge volume 40.

[0053] During operation of the scroll compressor 10, compressed gas flows out of the scroll compressor 10 by flowing from the discharge volume 40 to the upper volume 34A and out of the scroll compressor 10 through the discharge port 38. The intermeshing scroll members 12, 14 also have an inlet 41 from which gas flows into the intermeshing scroll members 12, 14. The inlet 41 is fluidly connected to the lower volume 34B of the scroll compressor 10. Inlet gas (e.g., working fluid to be compressed by the scroll compressor 10) flows into the scroll compressor 10 through the suction port 36. During operation of the scroll compressor 10, the inlet gas flows into the intermeshing scroll members 12, 14 by entering the scroll compressor 10 through the suction port 36, flowing through the lower volume 34B and entering the inlet 41.

[0054] In the illustrated embodiment, pressurized gas flows through upper volume 34A to exit scroll compressor 10. However, in one embodiment, discharge volume 40 may be directly fluidly connected to discharge port 38 such that gas exits scroll compressor 10 by flowing directly from discharge volume 40 to discharge port 38.

[0055] As described above, the crankshaft 24 in the embodiment moves along the orbit of the movable scroll member 14. The crankshaft 24 can be rotated by, for example, an electric motor 44. The electric motor 44 includes a rotor 46 and a stator 47. The rotor 46 and the crankshaft 24 are fixed together so that they rotate together. For example, the rotor 46 and the crankshaft 24 can be fixed together using an interference fit or other types of fits. The electric motor 44 can operate using known principles to rotate the crankshaft 24. In one embodiment, the crankshaft 24 can be driven to rotate by other mechanisms other than the electric motor 44, such as an external electric motor, an internal combustion engine, or other such mechanisms. Therefore, such an embodiment may not include the following. Figure 2 An electric motor 44 , a rotor 46 and a stator 47 are shown.

[0056] In one embodiment, the scroll compressor 10 includes bearings 50, 52, 54 that can support the crankshaft 24 while still allowing the crankshaft 24 to rotate. The radial bearings 50, 52 can support the crankshaft 24 in the radial direction while allowing the crankshaft 24 to rotate. The crankshaft thrust bearing 54 can support the crankshaft 24 in the axial direction while still allowing the crankshaft 24 to rotate. In one embodiment, the scroll compressor 10 can include one or more bearings 50, 52, 54 to support the crankshaft 24.

[0057] like Figure 2 As shown, in one embodiment, the end 56 of the crankshaft 24 is an eccentric end 56 relative to the rest of the crankshaft 24. The eccentric end 56 is eccentric when the axis of the end of the crankshaft 24 is radially offset from the axis of rotation of the crankshaft 24. The eccentric end 56 of the crankshaft 24 also includes a bearing 48. The bearing 48 can prevent the crankshaft 24 from transmitting its rotation to the movable scroll 14. However, radial movement of the eccentric end 56 (e.g., movement of the eccentric end 56 perpendicular to the axis of rotation) is still transmitted to the movable scroll 14. Therefore, in one embodiment, the movable scroll 14 orbits relative to the fixed scroll 12 instead of rotating. In an embodiment, the radial bearings 48, 50, 52 can be, for example, ball bearings, roller bearings, etc.

[0058] The thrust bearing 54 supports the crankshaft 24 in the axial direction while still allowing the crankshaft 24 to rotate. In one embodiment, the thrust bearing 54 is located between one end of the crankshaft 24 (e.g., the end of the crankshaft 24 opposite its eccentric end 56) and a second fixed support member (e.g., a lower bearing seat 59).

[0059] A lubricant (e.g., oil) may be provided to the bearings 48, 50, 52, 54 along the crankshaft 24. In one embodiment, the lubricant may be supplied from a lubricant groove 33 located at the bottom of the lower volume 34B of the scroll compressor 10. In one embodiment, the lubricant flows to the bearings 48, 50, 52, 54 through an internal passage 62 located within the crankshaft 24. Figure 2 As shown, the internal passage 62 is not parallel to the rotational axis of the crankshaft 24. Because the internal passage 62 is not parallel to the rotational axis of the crankshaft 24, the centrifugal force of the rotating crankshaft 24 can be used to draw lubricant from the lubrication oil groove 33 and into the bearings 48, 50, 52, 54. However, in one embodiment, the internal passage 62 can be parallel to the rotational axis of the crankshaft 24.

[0060] Alternatively or additionally, the scroll compressor 10 may include a pump 60 to pump oil from the lubricant groove 33 through the internal passage 62 and into the bearings 48, 50, 52, 54. The illustrated embodiment includes three radial bearings 48, 50, 52 and a thrust bearing 54 to support the crankshaft. However, an embodiment may include one or more bearings 48, 50, 52, 54 in any particular position along the crankshaft 24. The bearings may be included to be suitable for supporting the crankshaft 24 and allowing the movable scroll 14 to properly rotate and / or orbit relative to the fixed scroll 12.

[0061] When the volume filled with gas (e.g., trapped volume 16, trapped volume 17) is compressed between scroll members 18, 20, the compressed gas exerts a force in the axial direction on scroll members 12, 14. Since fixed scroll member 12 cannot move easily due to its fixed position within compressor 10, this axial force can push orbiting scroll member 14 in the axial direction, such as Figure 2 . This effect may also be referred to as a thrust load. It should be appreciated that due to the various locations of the gas-filled volumes (e.g., trapped volumes 16, 17), the thrust load may push the orbiting scroll 14 along one or more points along the base plate 26. The gas-filled volumes exert different amounts of thrust because they are compressed to different pressures. The thrust load does not exert the same amount of force on the radius of the base plate 26 of the orbiting scroll 14.

[0062] If the thrust load is not supported, it can cause the orbiting scroll 14 to move in an axial direction from its mutually meshed position with the fixed scroll 12. If the orbiting scroll is pushed out of its position, it can also cause an insufficient seal in the axial direction between the axial ends of the spiral wraps 18, 20 and each relative scroll base plate 26, 13. Inadequate sealing can result in a loss of efficiency of the scroll compressor 10, or in some cases, the scroll compressor 10 lacks the ability to compress the inlet gas. If the thrust is not supported, the orbiting scroll 14 may be pushed out of position, causing the orbiting scroll 14 to contact and damage the fixed support member (e.g., the bearing seat 58) supporting the crankshaft 24 and / or other internal components of the scroll compressor 10.

[0063] In one embodiment, the scroll compressor 10 may include an aerostatic thrust bearing for supporting (e.g., counteracting, suppressing) thrust loads. The aerostatic thrust bearing supports thrust loads by axially supporting the orbiting scroll 14. In one embodiment, the aerostatic thrust bearing includes the rear surface 28 of the orbiting scroll 14, the axial surface 66 of the bearing seat 58, and the gas distribution structure 64.

[0064] In one embodiment, the source of pressurized gas for gas distribution structure 64 is the working fluid of scroll compressor 10. For example, when scroll compressor 10 is used to compress refrigerant, compressed refrigerant produced by scroll compressor 10 may be used to support orbiting scroll 14 by aerostatic thrust bearings.

[0065] like Figure 2 As shown, gas distribution structure 64 is located on axial surface 66 of bearing adapter 58. In one embodiment, gas distribution structure 64 is fluidly connected to upper volume 34A via passage 68. Passage 68 allows pressurized gas within upper volume 34A to flow to aerostatic thrust bearing 64. Thus, pressurized gas is supplied from upper volume 34A to gas distribution structure 64.

[0066] exist Figure 2 In the illustrated embodiment, the passage 68 is shown as being completely within the outer housing 22 of the scroll compressor 10. However, other embodiments may include a passage 68 that passes through the housing 22. For example, the scroll compressor 10 may include a passage 68 that fluidly connects the discharge port 38 to the gas distribution structure 64 or a passage 68 that provides pressurized gas from an external source rather than from gas compressed by the scroll compressor 10. The illustrated embodiment shows a single passage 68 from the upper volume 34A to the gas distribution structure 64. However, an embodiment may include one or more passages 68 to the gas distribution structure 64.

[0067] like Figure 2 As shown, an optional booster 70 can be used to provide pressurized gas for the aerostatic thrust bearing. In one embodiment, the booster 70 is a second source of pressurized gas. The booster 70 provides pressurized gas when the pressure and / or flow rate of the gas discharged by the scroll compressor 10 is insufficient to support the thrust load. For example, the booster 70 can be used during the start-up and / or stop of the scroll compressor 10. In the illustrated embodiment, the booster 70 is fluidly connected to the passage 68. However, in one embodiment, the booster 70 can be alternatively or additionally fluidly connected to the upper volume 34A or the discharge port 38.

[0068] In one embodiment, the pressurizer 70 can be a container such as a volume of compressed gas that has been inflated during normal operation of the compressor 10. In one embodiment, the pressurizer 70 can be a smaller compressor. In an embodiment including the pressurizer 70, a valve (e.g., a flow control valve 71, a check valve) can be provided in the passage 68 and / or the discharge volume 40 to ensure that the pressurized gas flows from the pressurizer 70 to the gas distribution structure 64. The pressurizer 70 is shown to be located outside the scroll compressor 10. However, in one embodiment, the pressurizer 70 can be located inside the scroll compressor 10.

[0069] In one embodiment, a flow control device 71 (e.g., a flow control valve) may be disposed within the passage 68. The flow control device 71 may control the amount of pressurized gas flowing into the gas distribution structure 64. Alternatively, in one embodiment, the flow control device 71 may be a structure such as a narrowing of the passage 68 that provides a pressure drop to regulate the amount of pressurized gas flowing through the passage 68.

[0070] In the illustrated embodiment, the pressurizer 70 is a secondary source of pressurized gas. However, in one embodiment, the pressurizer 70 may be the primary source of pressurized gas. In one embodiment, the pressurizer 70 may be an external source of compressed gas that provides all of the pressurized gas for one or more aerostatic thrust bearings in the compressor 10. In such an embodiment, the passageway may be connected to the pressurizer 70 instead of the upper volume 34A.

[0071] refer to Figure 2 , Figure 3A and 3B The gas distribution structure 64 supplies pressurized gas from the upper volume 34A through the passage 68. The gas distribution structure 64 distributes the pressurized gas to the space 43 between the movable scroll member 14 and the bearing seat 58. Figure 3A As shown, the upper surface 72 of the gas distribution structure 64 distributes the pressurized gas into the space 43. As the rear surface 28 of the orbiting scroll 14 pushes the fluid flowing through the space 43 (due to the thrust), the distributed pressurized gas is compressed between the axial surface 66 of the bearing seat 58 and the rear surface 28 of the orbiting scroll 14. Therefore, the flow of the distributed pressurized gas forms a pressurized gas layer between the orbiting scroll 14 and the bearing seat 58. This gas layer can support the orbiting scroll 14 and its thrust load.

[0072] As the orbiting scroll 14 orbits, the thrust load may cause the orbiting scroll 14 to wobble toward one radial end of the orbiting scroll 14. The wobble is the tilting (e.g., precession) of the orbiting scroll 14 relative to the crankshaft 24 and / or the bearing housing 58. When the wobble occurs, the base plate 26 is no longer perpendicular to the crankshaft 24. The wobble may occur because the moments applied by the compression and drive forces, as well as the inertia and / or thrust caused by the orbiting motion of the orbiting scroll 14, are unevenly applied to the diameter of the base plate 26.

[0073] When oscillating, the distance between the rear surface 28 of the movable scroll member 14 and the axial surface 66 of the bearing seat 58 (e.g., Figure 3A The distance 39 shown in FIG. 3 is no longer constant over the entire circumference of the movable scroll member 14 and the bearing seat 58, and for example, when viewed from a horizontal direction (eg, Figure 2), the movable scroll 14 is tilted so that its base plate 26 is closer to the bearing seat 58 at one radial end and farther from the bearing seat 58 at the opposite radial end. In the area where the distance between the rear surface 28 and the axial surface 66 is small, the swing / precession will apply additional force to further compress the pressurized gas layer. However, the compression of the flowing pressurized gas layer causes the flowing pressurized gas layer to provide a greater force to support the movable scroll 14. The pressurized gas layer provides greater support because it provides a greater reaction force to resist further compression when the movable scroll 14 pushes the pressurized gas layer. In one embodiment, the movable scroll 14 and the bearing seat 58 are positioned relative to each other so that the axial distance 39 between the rear surface 28 and the axial surface 66 is small. The small distance 39 between the rear surface 28 and the axial surface 66 allows the aerostatic thrust bearing to fully support the movable scroll 14 and its thrust load with a relatively small pressurized gas flow.

[0074] In the manner described above, pressurized gas is supplied to gas distribution structure 64 so that it can form a pressurized gas layer between orbiting scroll 14 and bearing housing 58. Aerostatic thrust bearings utilize a pressurized gas layer to support thrust loads and prevent orbiting scroll 14 from axially moving out of its proper meshing position.

[0075] In the illustrated embodiment, the gas distribution structure 64 is located on the bearing seat 58. It should be understood that the bearing seat 56 is an example of a fixed support member. In one embodiment, the fixed support member can be other structures having a fixed position (relative to the orbiting scroll 14) and having a surface facing the rear surface 28 of the orbiting scroll 14.

[0076] Figure 3A and 3B Shows Figure 2 An enlarged view of the aerostatic thrust bearing during operation of the scroll compressor 10 is shown. Figure 3A As shown, the upper surface 72 of the gas distribution structure 64 distributes the pressurized gas into the space 43. Figure 3A As shown, the gas distribution structure 64 is embedded in the axial surface 66 of the bearing seat 58. However, the gas distribution structure 64 in the embodiment may protrude from the axial surface 66 or be completely located (e.g., positioned) above the axial surface 66. In one embodiment, the gas distribution structure 64 has a thickness 73 and includes an outer side 79 and an inner side 81. The illustrated embodiment has a gas distribution structure 64 that has a uniform thickness 73 in the radial direction (e.g., along directions D and E). However, in one embodiment, the thickness 73 of the gas distribution structure 63 is not uniform in the radial direction.

[0077] In one embodiment, the gas distribution structure 64 may include one or more inlets 74. Figure 3AAs shown, the gas distribution structure 64 includes an inlet 74 for supplying pressurized gas. The illustrated embodiment shows the rear surface 76 of the gas distribution structure 64 including the inlet 74. However, embodiments may alternatively or additionally include the inlet 74 in one or more sides 79, 81 of the gas distribution structure 64. The illustrated embodiment shows the gas distribution structure 64 with a specific inlet 74. Alternatively, a surface or a portion of a surface of the gas distribution structure 64 (e.g., the rear surface 76, the outer side 79, and the inner side 81) may be an inlet surface for the gas distribution structure 64.

[0078] Optionally, all or part of the circumference of the aerostatic thrust bearing may be provided in the gas distribution structure 64. Figure 4 The groove 78 can provide a passage to distribute gas to the gas distribution structure 64. For example, in one embodiment, the groove 78 can fluidly connect multiple inlets 74 of the gas distribution structure 64. In one embodiment, the groove 78 can be along the inlet surface of the gas distribution structure 64 instead of a specific inlet 74. In such an embodiment, the groove itself can form the inlet surface. The passage 68 can then be fluidly connected to the groove 78 to supply pressurized gas to the inlet surface of the gas distribution structure 64. Optionally, in one embodiment, the groove 78 can be positioned in the bearing seat 58 along the rear surface 76 of the gas distribution structure 64.

[0079] In one embodiment, the gas distribution structure 64 is made of a material that allows gas to flow therethrough in a distributed manner. For example, the gas distribution structure 64 can be a porous material. In one embodiment, the gas distribution structure 64 is a porous carbon substrate. In one embodiment, the gas distribution structure 64 has a structure or material that allows the incoming pressurized gas to be distributed through its upper surface 72 (as shown by the arrow marked B). In this way, the gas distribution structure 64 can evenly distribute the inlet gas to the space 43 between the movable scroll 14 and the bearing seat 58 along its upper surface 72. This distribution of gas allows the aerostatic thrust bearing to form a compressed gas layer that can support the thrust load of the movable scroll 14 in the direction of arrow C. Once introduced into the space 43 between the movable scroll 14 and the bearing seat 58, the distributed compressed gas flows in direction D and / or direction E. Some of the distributed pressurized gas can also flow in the circumferential direction (for example, along the direction of the circumference of the movable scroll 14, along the direction of the groove 72, perpendicular to the directions E, D and A). However, the distributed pressurized gas flowing in the circumferential direction eventually flows out from between the movable scroll 14 and the bearing housing 58 by traveling in the radial direction (eg, direction D, direction E).

[0080] Figure 3BSchematic diagram of the movable scroll member 14 and the bearing seat 58 in one embodiment. The side surfaces 79 and 81 respectively define the outer radius 84 and the inner radius 86 of the gas distribution structure 64 (such as Figure 4 In one embodiment, outer edge 85 defines the outer periphery of rear surface 28 of orbiting scroll 14. If side surface 79 is located outside the outer periphery of rear surface 28, then in one embodiment, upper surface 72 does not face rear surface 28. This provides a bypass for pressurized gas because it can flow out of gas distribution structure 64 without passing through space 43 between orbiting scroll 14 and bearing housing 58 (as shown in FIG. Figure 3A ). However, when located more outboard (e.g., further toward the periphery of the aft surface 28), the aerostatic thrust bearing can provide greater support for the outer radius of the aft surface 28. Therefore, the side 79 of the gas distribution structure 64 is positioned close to but still within the periphery of the aft surface 28. In such a position, the aerostatic thrust bearing provides excellent support for the radial end (e.g., periphery) of the baseplate 28 of the orbiting scroll member 14 while properly and / or efficiently utilizing the pressurized gas by avoiding bypass.

[0081] Additionally, tilt or wobble of the orbiting scroll 14 may be further inhibited by positioning the side 79 (and outer radius 84) of the gas distribution structure 64 further outward. It should be appreciated that in one embodiment, the gas distribution structure 64 has an upper surface 72 that is large enough to support the orbiting scroll 64 in the axial direction and prevent the formation of large pressure gradients as described below.

[0082] like Figure 2 As shown, the bearing housing 58 and the movable scroll member 14 are located in the lower volume 34B of the scroll compressor 10. Thus, the space 43 ( Figure 3A 34B. In another way, the space 43 can be defined as a specific portion of the lower volume 34B located between the movable scroll 14 and the bearing seat 58. Due to the flow of the distributed pressurized gas, the space 43 has a higher pressure relative to the rest of the lower volume 34B. Therefore, the pressurized gas distributed by the gas distribution structure 64 flows from the space 43 in the direction E or D into the lower volume 34B after being used to support the thrust load. In this way, the gas used by the aerostatic thrust bearing is mixed with the inlet gas from the suction port 36 and is recompressed by the scroll compressor 10.

[0083] like Figure 4 As shown, in one embodiment, the upper surface 72 of the gas distribution structure 64 has a donut shape in a top view. Figure 47 is a top view of the upper surface 72 of the bearing housing 58 and the gas distribution structure 64. The bearing housing 58 includes a cylindrical through hole 80 that allows the crankshaft 24 and the orbiting scroll 14 to be connected. The annular shape allows the gas distribution structure 64 to extend along the rear surface 28 ( Figure 2 , Figure 3A and Figure 3B The pressurized gas supply is distributed over the entire circumference of the device (shown in FIG).

[0084] like Figure 4 As shown, the upper surface 72 of the gas distribution structure 64 has an inner diameter 86, an outer diameter 84, and a radial distance 82. In one embodiment, the upper surface 72 has a uniform shape around the circumference of the bearing adapter 58. However, in one embodiment, the upper surface 72 may be non-uniform around the circumference of the bearing adapter 58. For example, in one embodiment, the radial distance 82 of the upper surface 72 and / or the distance between the through hole 80 and the inner radius 86 may not be constant around the circumference of the bearing adapter 58.

[0085] like Figure 4 As shown, the gas distribution structure 64 includes a plurality of inlets 74. In one embodiment, one or more passages 68 ( Figure 2 and 3A ) can be fluidly connected to each inlet 74. In one embodiment, one or more passages 68 (shown in Figure 2 and 3A 74) can be fluidly connected to one or more grooves (e.g., groove 78) that fluidly connect two or more inlets 74. The inlets 74 and grooves 78 are shown by dashed lines because they are not visible in the view shown in the figure. The illustrated embodiment includes a gas distribution structure with six inlets 74. However, an embodiment can include one or more inlets 74 and / or one or more inlet surfaces as discussed herein.

[0086] like Figure 4As shown, the groove 78 runs along the entire circumference of the gas distribution structure 64. However, in one embodiment, the groove 78 may only run along a portion of the circumference of the gas distribution structure 64. In one embodiment, one or more grooves 78 may be provided in the gas distribution structure 64 and / or the bearing seat 58. In the embodiment shown, the groove 78 runs only in the circumferential direction. However, in one embodiment, the groove 78 may run in the radial direction, the circumferential direction, or the circumferential direction and the radial direction. In one embodiment, the groove 78 may have a plurality of portions, and each portion may be oriented in the radial direction, the circumferential direction, or the circumferential direction and the radial direction. The groove 78 in the embodiment shown is aligned with all the inlets 74. However, the groove 78 in the embodiment may not be completely aligned with the inlet 74. In such an embodiment, the groove 78 may have one or more additional portions (not shown) that connect the groove 78 to the inlet 74. The additional portion may run in the radial direction, the circumferential direction, or a combination thereof.

[0087] The upper surface 72 of the gas distribution structure 64 can have an area (A). In one embodiment and as described above, the distributed pressurized gas flows from the space 43 into the lower volume 34B. The lower volume 34B can have a pressure (P I In one embodiment, the pressure (P I ) depends on the pressure of the inlet gas entering the scroll compressor 10. The pressurized gas supplied to the gas distribution structure 64 may have a pressure (P p ). Therefore, in one embodiment, the amount of thrust load (F) that can be supported by aerostatic thrust can be expressed as follows:

[0088]

[0089] Aerostatic thrust bearings will also have an efficiency (E f ). Efficiency (E f ) is an efficiency factor that depends on various factors. For example, these factors may include the distance between the orbiting scroll 14 and the bearing seat 58, how evenly the gas distribution structure 64 distributes the incoming pressurized gas across its upper surface 72, the thickness of the gas distribution structure 64, and the permeability of the material of the gas distribution structure 64.

[0090] Efficiency (E f ) can be a constant factor or a non-constant factor. For example, during stable operation, the orbiting scroll 14 can have a relatively small amount of non-oscillation. Since the distance between the orbiting scroll 14 and the bearing seat 58 is generally constant, the efficiency (E f) may be constant. However, the orbiting scroll 14 may oscillate during operation, so that the distance between the orbiting scroll 14 and the bearing seat 58 is not constant around the circumference of the orbiting scroll 14. This may, for example, result in a decrease in the efficiency (E) of the aerostatic bearing. f ) is non-constant.

[0091] In one embodiment, the scroll compressor 10 may utilize a constant inlet gas flow rate and compress the inlet gas by a minimum amount (e.g., a minimum compression ratio). In this case, in one embodiment, the minimum pressure (P P ) and the maximum inlet gas pressure (P I ) is known. Thus, the gas distribution structure 64 can be configured to have a maximum pressure (P P ) and the minimum inlet gas pressure (P I ) is the force area (A) supporting the thrust load (F).

[0092] In one embodiment, the gas distribution structure 64 may have a ring shape (eg Figure 4 ) to maximize the surface area (A) of the gas distribution structure 64. Maximizing the surface area (A) of the gas distribution structure 64 may be useful, for example, when the thrust load is large and / or the pressure difference between the inlet gas and the supplied pressurized gas is small because the inlet gas has a moderate pressure. For example, a scroll compressor 10 with a higher compression ratio and / or a larger planar area will generally have a larger thrust load.

[0093] For example, the pressure of the inlet gas may affect the pressure of the lower volume 34A. If the inlet gas is provided at a higher pressure, the pressure difference (P P -P I ) can be smaller. Therefore, the gas distribution structure 64 can have an upper surface 72 with a larger surface area (A) to account for this smaller pressure difference.

[0094] One embodiment may divide the lower volume 34B. For example, the aerostatic thrust bearing in one embodiment may be isolated from the lower volume 34B by including one or more dynamic seals between the rear surface 28 of the movable scroll 14 and the axial surface 66 of the bearing seat 58. The one or more dynamic seals may guide the flow of the distributed pressurized gas. The lower volume 34B may have a first portion (not shown) into which the distributed pressurized gas flows (e.g., the pressurized gas in the space 43 will flow into the first portion). A second portion (not shown) of the lower volume 34B may be used to provide inlet gas from the suction port 36 to the inlet 41. The first portion will be separated from the second portion of the fluid. In such an embodiment, P in the above formula IInstead of being based on the pressure of the inlet gas, the pressure of the first portion of the lower volume 34B will be. In such an embodiment, the inlet gas will no longer be a direct factor in the amount of thrust load (F) that the aerostatic thrust bearing can support.

[0095] In one embodiment, an aerostatic thrust bearing including a gas distribution structure 64 having a smaller surface area (A) can utilize a smaller flow of pressurized gas. The pressurized gas used by the aerostatic thrust bearing is compressed by the compressor 10 gas but not exhausted. The energy used by the compressor 10 to compress the pressurized gas provided to the aerostatic thrust bearing can be considered a system loss in some cases. Therefore, the gas distribution structure 64 having a smaller surface area (A) does not provide a larger system loss to the compressor 10. In one embodiment, the gas distribution structure having a smaller surface area (A) has a smaller impact on the overall efficiency of the compressor 10.

[0096] The thrust load does not exert an equal amount of force across the diameter of the base plate 28 of the orbiting scroll 14. In one embodiment, as the gas is compressed to a higher pressure, the thrust is greater toward the center of the base plate 28. Figure 3B , in one embodiment, thrust F1 is less than thrust F2. A gas distribution structure 64 having a small surface area (A) that provides sufficient support for the movable scroll 14 can produce a large pressure gradient along the rear surface 28. For example, the force F3 applied by the distributed pressurized gas can be significantly greater than the thrust F1. Large pressure gradients can cause deflection of the base plate 28 and the movable scroll 14. Therefore, the gas distribution structure 64 has a sufficiently large surface area (A) to avoid forming a large pressure gradient that may deflect and damage the movable scroll 14.

[0097] As described above, the orbiting scroll may experience wobble. To account for this possible wobble and the different thrust loads across the base plate 26, one embodiment of the aerostatic thrust bearing may include a gas distribution structure having a separation portion 167, such as Figure 5 In one embodiment, the gas distribution structure may include a gas distribution portion 167 positioned around the periphery of the bearing seat 158, such as Figure 5 In one embodiment, each gas distribution portion 167 may have a Figure 4 The shape of a portion of a full annular gas distribution structure 64 is shown. However, an embodiment may have a different shape of the gas distribution portion 167 than shown.

[0098] like Figure 5 As shown, each gas distribution portion 167 includes an inlet 174. The inlet may be similar to Figure 3A and 4Inlet 74 is shown and described. Since pressurized gas is supplied to each gas distribution portion 167 separately, a single gas distribution portion 167 can utilize pressurized gas alone. This configuration allows each gas distribution portion 167 to distribute pressurized gas without being affected by the way other gas distribution portions 167 distribute pressurized gas.

[0099] Figure 5 The embodiment shown in FIG. 1 shows a gas distribution structure having a gas distribution portion 167. However, the gas distribution structure in the embodiment may include two or more gas distribution portions 167. The embodiment of the gas distribution structure may include four or more gas distribution portions to solve the problem of the possible swinging ( Figure 2 ) caused by possible different thrust loads, axial distances 39, and / or local movements around the base plate 28 ( Figure 2 shown).

[0100] For example, the oscillation of the orbiting scroll may cause the axial distance between the orbiting scroll 14 and the bearing seat 58 (e.g., Figure 3A The axial distance 39 shown in FIG. 1 is larger at some locations around the circumference of the orbiting scroll member 14. The larger axial distance can allow excessive leakage of high-pressure gas. In embodiments of the gas distribution structure 64 without the gas distribution portion 176 (e.g., Figure 5 In the embodiment shown in the figure, excessive leakage may affect the performance of the entire gas distribution structure 64 (e.g., reduce load capacity). In contrast, the gas distribution section 167 independently supplies pressurized gas, so that excessive leakage of pressurized gas is less likely to affect or minimize the impact on the performance of other gas distribution sections 167.

[0101] like Figure 6 As shown, the gas distribution structure 264 in one embodiment includes an upper surface 272 that is inclined relative to the axial surface 266 of the bearing seat 258. The gas distribution structure 264 may include Figure 3A and Figure 3B The gas distribution structure 64 shown in FIG. 1 has similar features, except that the upper surface 272 has a sloped surface 277. Figure 2-5 Similar to the gas distribution structure shown in FIG. 1 , the gas distribution structure 264 distributes the compressed gas between the rear surface 228 of the base plate of the movable scroll member 214 and the axial surface 266 of the bearing seat 258. Figures 2 to 5 Similarly described, compressed gas is supplied to the gas distribution structure 264 via passage 268 .

[0102] The slope 277 of the upper surface 272 allows the pressurized gas to Figure 3A272. The gas distribution structure 264 shown in FIG. 27 can be configured to flow out of the gas distribution structure 264 in different ways. For example, the bevel 277 of the upper surface 272 can affect the direction of the gas flowing out of the gas distribution structure 264. Because the upper surface 272 in one embodiment is oriented in the direction of arrow F, the gas flowing out of the gas distribution structure 264 flows in the direction of arrow F. In addition, the pressurized gas flowing out of the inclined upper surface 272 can affect the manner in which the pressurized gas flows out of the gas distribution structure 264.

[0103] Depending on the internal structure (e.g., permeability) of the gas distribution structure 264 in one embodiment, the non-constant thickness 273 of the gas distribution structure 264 can also affect the flow rate of the gas flowing out of the upper surface 272. For example, the pressurized gas can flow out of the gas distribution structure 264 at different rates along its upper surface 272. However, the gas distribution structure 64, 164, 264 in one embodiment may not always have a constant internal structure. For example, the gas distribution structure 264 can have a non-constant internal structure to ensure a more uniform distribution of the pressurized gas along the upper surface 272 from a central source of pressurized gas (e.g., inlet 274).

[0104] Alternatively, the gas distribution structure in one embodiment (e.g., Figure 3A and Figure 3B The gas distribution structure 64 shown in FIG. 2 may be embedded at an angle into the axial surface 266 of the bearing seat 258. In such an embodiment, the gas distribution structure may have a uniform thickness 273 while still having an upper surface 272 with a bevel 277 (relative to the axial surface 266).

[0105] For the upper surface 272, embodiments may have Figure 6 277. The slope 277 may be different to, for example, change the direction of the pressurized gas flowing out of the gas distribution structure 264 and / or the rate of the pressurized gas flowing out of the gas distribution structure 264. In the illustrated embodiment, the gas distribution structure 264 becomes thicker toward the inner side 281. However, in one embodiment, the gas distribution structure 264 may be thicker toward the outer side 279 rather than the inner side 281.

[0106] The inclined surface 277 of the upper surface 272 can be configured to ensure that the outer radial end (e.g., the outer periphery) of the base plate of the movable scroll member 214 is fully supported (e.g., in the direction of arrow C). The inclined upper surface 277 can support the radial end of the base plate of the movable scroll member 214 by guiding the flow of the distribution gas. For example, in one embodiment, the configuration of the inclined surface 277 of the upper surface 272 can provide a larger amount of pressurized gas in direction E than in direction D. In such an embodiment, a larger gas flow in the outer radial direction (e.g., direction E) of the base plate of the movable scroll member 214 can better support the radial end of the base plate.

[0107] In one embodiment, the upper surface 72, 272 of the gas distribution structure 64, 264 may be inclined in a circumferential direction (e.g., along the circumference of the base plate 26, along the circumference of the base plate of the movable scroll member 214). In one embodiment, the slope of the upper surface 72, 264 in the circumferential direction may not be constant. For example, the upper surface 72, 272 may include a downwardly inclined portion and an upwardly inclined portion to form grooves in the upper surface 72, 272. In one embodiment, these grooves in the upper surface 27, 272 may be in a radial direction.

[0108] The friction between the rear surface 228 and the flowing pressurized gas can push the pressurized gas along the orbital direction of the orbiting scroll 14. In one embodiment, the upper surface 272 of the gas distribution structure 264 can use the pressurized gas pushed by the orbiting scroll 14 to form areas with higher relative pressure. For example, these areas of high relative pressure can be referred to as pressurized gas wedges. The inclined surface of the upper surface 272 can be located in the circumferential direction and / or the radial direction (such as Figure 6 272) to form a pressurized gas wedge at a specific location. The slope of the upper surface 72, 272 may not be as constant as the orbit of the orbiting scroll 14. These gas areas with higher relative pressure can increase the amount of support provided by the aerostatic thrust bearing.

[0109] The gas distribution structure 64, 264 is shown as being completely below the axial surface 66, 266 of the bearing adapter 58, 258. However, in one embodiment, the gas distribution structure 64, 264 can protrude above the axial surface 66 or be completely located (e.g., positioned) above the axial surface 66, 266 of the bearing adapter 58, 258.

[0110] like Figure 7 As shown, in one embodiment, a scroll compressor 310 has an aerostatic thrust bearing that includes a gas distribution structure 364 located on the rear surface 328 of the orbiting scroll member 314. Figure 2Similar to the scroll compressor 10 shown in FIG. 1 , the scroll compressor 310 further includes a fixed scroll 312 having a spiral wrap 318. The orbiting scroll 314 further includes a spiral wrap 320. The fixed scroll 312 and the orbiting scroll 314 and their respective spiral wraps are similar to those of FIG. Figure 2 The compressors 10 shown and described above are meshed with each other. For ease of understanding, Figure 7 The coupling device (eg, Oldham coupling 30) is omitted from the illustrated view.

[0111] In one embodiment, the aerostatic thrust bearing includes a rear surface 328 of the orbiting scroll 314, an axial surface 366 of the bearing seat 358, and a gas distribution structure 364. The gas distribution structure 364 of the aerostatic thrust bearing is located on the rear surface 328 of the base plate 326 of the orbiting scroll 314. In addition to as described herein, the scroll compressor 310 may have the same Figure 2 In one embodiment, the gas distribution structure 364 may include features similar to those of the scroll compressor 10 shown in FIG. Figures 2 to 6 The gas distribution structure 364 may have similar features to the gas distribution structures 64, 164, 264 shown in FIG. For example, the gas distribution structure 364 may have separate portions and / or a sloped upper surface.

[0112] Similar to Figure 2-6 In the manner of the gas distribution structures 64, 164, 264 shown in the figure, the gas distribution structure 364 distributes the pressurized gas between the rear surface 328 of the movable scroll 314 and the axial surface 366 of the bearing seat 358. Similar to the above, the distributed pressurized gas then flows into the lower space 334B of the scroll compressor 310. A flowing distributed pressurized gas layer is formed between the movable scroll 314 and the bearing seat 358 by the surface of the aerostatic thrust bearing. As described above, this layer supports the movable scroll 314 in the axial direction. In this way, the aerostatic thrust bearing can support the movable scroll 314 and its thrust load so that the movable scroll 314 will not move out of its correct meshing position with the movable scroll 312 in the axial direction.

[0113] In one embodiment, the gas distribution structure 364 is supplied with pressurized gas from the exhaust volume 340 of the spiral wraps 318 , 320 . Figure 7 The exhaust volume 340 shown in FIG. 3 may have the same Figure 2 The discharge volume 340 is similarly structured as described above, except that the discharge volume 340 also includes an auxiliary outlet 365. A passage 368 in the base plate 326 of the orbiting scroll 314 fluidly connects the discharge volume 340 to the gas distribution structure 364 via the auxiliary outlet 365. In this manner, pressurized gas is supplied from the discharge volume 340 through the base plate 326 of the orbiting scroll 314 to the aerostatic thrust bearing.

[0114] In one embodiment, the inlet for the channel 368 (e.g., the secondary outlet 365) can be located at different radial positions of the substrate 326. In such an embodiment, the channel 365 can fluidly connect the gas distribution structure 364 to the intermediate volume (e.g., the retentate volume 316, the retentate volume 317). Therefore, the exhaust volume 340 in such an embodiment may or may not have the secondary outlet 365.

[0115] In one embodiment, the inlet for the passage 368 may be located on the outer radial surface of the base plate 326. In such an embodiment, pressurized gas from an internal source (e.g., the upper volume 334A) or an external source (e.g., a pressurizer, not shown) may supply pressurized gas to the gas distribution structure 364 via the outer radial surface of the base plate 326 rather than the exhaust volume 340.

[0116] In one embodiment, the pressure drop across the aerostatic thrust bearing can control the amount of pressurized gas flowing through the aerostatic thrust bearing. However, the passage 368 in an embodiment can include one or more flow control mechanisms (e.g., narrowing of the passage 368, a flow control valve (e.g., flow control valve 71)) to prevent more than a desired amount of pressurized gas from flowing through the aerostatic thrust bearing.

[0117] In one embodiment, the passage 368 can include multiple portions, and each portion can fluidly connect the passage 368 to a different location along the circumference of the gas distribution structure 364. Alternatively or additionally, the passage 368 can be fluidly connected to a groove (e.g., a groove similar to groove 78) that fluidly connects one or more inlets of the gas distribution structure 364 (e.g., similar to inlets 74, 174, 274). As described above, the gas distribution structure 364 in one embodiment can be a continuous ring (e.g., gas distribution structure 64), or it can have separate segments or portions (e.g., gas distribution portion 167). In one embodiment, the upper surface of the gas distribution structure 364 (e.g., the surface of the gas distribution structure 364 that faces the bearing seat 358) can be oriented relative to the rear surface 328 of the orbiting scroll member 314 to be aligned with the bearing seat 358. Figure 6 The gas distribution structure 264 is inclined in a similar manner.

[0118] During normal operation, the gas distribution structure 364 distributes pressurized gas between the bearing seat 358 and the movable scroll 314. As described above, the distributed pressurized gas flows from between the movable scroll 314 and the bearing seat 358 into the lower volume 334B of the scroll compressor 310. The distributed pressurized gas is squeezed between the axial surface 366 and the rear surface 328, so that it forms a flowing pressurized gas layer between the bearing seat 358 and the movable scroll 314. The flowing pressurized gas layer supports the movable scroll 314 and the thrust load generated by the scrolls 312, 314 in the axial direction. In this way, the aerostatic thrust bearing supports the movable scroll 314 and its thrust load. During normal operation, the aerostatic thrust bearing ensures that the movable scroll 314 maintains its correct meshing position with the fixed scroll 312 in the axial direction.

[0119] In one embodiment, a pressurizer (e.g., Figure 2 The pressurizer 70 in the aerostatic thrust bearing can be used to supply pressurized gas to the aerostatic thrust bearing. The pressurizer can be a secondary source of pressurized gas for the aerostatic thrust bearing. For example, the pressurizer can provide pressurized gas when the pressurized gas is insufficient to support the thrust load (e.g., during compressor startup, during compressor shutdown). In one embodiment, the pressurizer can be fluidly connected to the gas distribution structure 364 via, for example, the discharge volume 340, the radial surface of the base plate 326, the upper volume 334A, and / or the discharge outlet 338.

[0120] In one embodiment, the scroll compressor may be Figure 8 An oil-free scroll compressor 400 is shown. Figure 8 The illustrated scroll compressor 400 is a vertical, single-stage scroll compressor. Figure 8 4 is a cross-sectional view of an oil-free scroll compressor 400. The oil-free scroll compressor 400 includes an aerostatic thrust bearing and an aerostatic radial bearing. Pressurized gas is supplied to the aerostatic bearing. In one embodiment, the pressurized gas may be a refrigerant that has been compressed by the scroll compressor 400. For ease of understanding, Fig.11 The coupling device (e.g., the Oldham coupling 30) is omitted from the illustrated view. However, in one embodiment, it should be understood that additional aerostatic bearings or gas distribution structures may be provided for coupling devices that require lubrication in embodiments of the oil-free scroll compressor 400. The gas distribution structure for the coupling device may be located in the orbiting scroll 414 and / or the bearing seat 458.

[0121] In an embodiment of the oil-free scroll compressor 400, the orbiting scroll 414 and its thrust load may be supported in the axial direction by an aerostatic thrust bearing. The aerostatic thrust bearing includes a gas distribution structure 464. Similar to Figure 7In the scroll compressor 310 shown in FIG. 1 and described above, the gas distribution structure 464 is located on the orbiting scroll 414 and supplies pressurized gas from the interior volume 442 of the scrolls 412, 414 through the passage 468. In one embodiment, the secondary inlet 465 for the passage 468 can be located at another radial position of the orbiting scroll 414, as described above for Figure 7 In one embodiment, the aerostatic thrust bearing may have a gas distribution structure 464 on the axial surface 466 of the bearing seat 458, similar to Figures 2 to 6 The gas distribution structures 64, 164, 264 shown in FIG.

[0122] For example, in a scroll compressor 400, an electric motor 444 (similar to the above embodiment for Figure 2 The motor 44 is configured to rotate the crankshaft 424. The scroll compressor 400 includes an aerostatic radial bearing for supporting the crankshaft 424 in a radial direction and a crankshaft aerostatic thrust bearing for supporting the crankshaft 424 in an axial direction. The scroll compressor 400 also includes an aerostatic radial bearing located between an end portion (e.g., an eccentric end 456) of the crankshaft 424 and the orbiting scroll 414. In one embodiment, each aerostatic bearing along the crankshaft includes a gas distribution structure 448, 450, 452, 454 located on the crankshaft 424.

[0123] The first radial bearing and the second radial bearing support the crankshaft 424 in the radial direction when the crankshaft rotates. The first aerostatic radial bearing includes a radial surface of the crankshaft 424, a radial surface of the bearing seat 458 (e.g., a surface of the bearing seat that faces the radial surface of the crankshaft 424), and the gas distribution structure 450. Fig. 9 The first radial bearing is described in more detail. Figure 8 As shown, the second aerostatic radial bearing includes a radial surface of crankshaft 424 , a radial surface of lower bearing seat 459 (eg, surface 459 of lower bearing seat that faces the radial surface of crankshaft 424 ), and gas distribution structure 452 .

[0124] The crankshaft aerostatic thrust bearing supports the crankshaft 424 axially during rotation. The crankshaft aerostatic thrust bearing is located at an axial surface of the end of the crankshaft 424 opposite the eccentric end 456. The crankshaft aerostatic thrust bearing includes an axial surface of the end of the crankshaft 424, an axial surface 459 of the lower bearing seat, and the gas distribution structure 454. Fig. 10A The crankshaft thrust bearing is described in more detail.

[0125] The scroll compressor 400 also includes an aerostatic radial bearing for the eccentric end 456 of the crankshaft 424, which meshes with the orbiting scroll 414. In one embodiment, the aerostatic radial bearing for the eccentric end 456, together with the connection means, allows the eccentric end 456 to transmit its radial motion without transmitting its rotation to the orbiting scroll 414. The aerostatic radial bearing for the eccentric end 456 includes a radial surface of the eccentric end 456 of the crankshaft 424, a surface of the orbiting scroll 414 (e.g., an orbiting scroll 414 whose surface faces the radial surface of the eccentric end 456), and a gas distribution structure 448 located on the surface of the eccentric end 456.

[0126] Similar to Figure 2 and Figure 7 In the scroll compressor 10, 310 shown in FIG. 4, the lower volume 434B of the scroll compressor 400 is separated from the upper volume 434A by fluid, and the inlet 441 of the meshing scroll members 412, 414 is located in the lower volume 434B. In this way, the gas in the lower volume 434B is supplied to the scroll members 412, 414 for compression. The inlet gas is supplied to the lower volume 434B through the suction port 436. Figure 8 As shown, the aerostatic bearings of the scroll compressor 400 (and its corresponding gas distribution structures 448, 450, 452, 454, 464) are located within the lower volume 434B of the scroll compressor 400. Therefore, the pressurized gas distributed by the gas distribution structures 448, 450, 452, 454, 464 flows into the lower volume 434B and can mix with the inlet gas in the lower volume 434B. In this way, the pressurized gas used by the aerostatic bearings is recompressed. Because the pressurized gas and the inlet gas are the same type of gas (e.g., refrigerant) in one embodiment, the pressurized gas distributed by the gas distribution structures 448, 450, 452, 454, 464 does not have to be separated from the inlet gas. As described above, in one embodiment, the lower volume 334B can be partitioned so that the gas used by the aerostatic bearings and the inlet gas do not mix.

[0127] like Figure 8 As shown, the crankshaft 424 has an internal passage 462 that passes through most of the length of the crankshaft 424. The gas distribution structures 448, 450, 452, 454 located along the crankshaft 424 are fluidly connected to the internal passage 462 of the crankshaft 424. In one embodiment, a connecting passage 469 fluidly connects the internal passage 462 to the upper volume 434A of the scroll compressor 400. As described above with respect to Figure 2-7As described, similarly, the upper volume 434A in one embodiment is fluidly connected to the discharge volume 440 of the scroll members 412, 414. Thus, the pressurized gas supplied to the gas distribution structures 448, 450, 452, 454 along the crankshaft 424 is the gas compressed by the scroll compressor 400.

[0128] exist Figure 8 In the illustrated embodiment, the connecting passage 469 is located entirely within the outer housing 422 of the scroll compressor 400. However, embodiments may have the connecting passage 469 passing through the outer housing 422. In such embodiments, the pressurized gas for the aerostatic bearings on the crankshaft 424 may be a source external to the scroll compressor 400 (e.g., a separate compressor, a pressurizer) or the exhaust outlet 438. In one embodiment, the connecting passage 469 may include a flow control device (e.g., Figure 2 A flow control device 71 is shown in FIG. 7 to control and / or stop the flow of gas to the gas distribution structures 448 , 450 , 452 , 454 .

[0129] In one embodiment, the scroll compressor can be a multi-stage scroll compressor having a movable scroll member 414 located at both ends of the crankshaft 424. In such an embodiment, for example, the connecting passage 469 can be connected to the internal passage 462, for example, through the radial surface of the crankshaft 424 rather than the end fluid of the crankshaft 424. In addition, the scroll compressor can include a pressurizer (e.g., pressurizer 70) as described herein. In one embodiment, the pressurizer can be outside or inside the scroll compressor 400. In one embodiment, the pressurizer can be the main source of pressurized gas as described above. In addition, the pressurizer in one embodiment can be the main source of pressurized gas for one or more aerostatic bearings in the oil-free scroll compressor 400.

[0130] Fig. 9 Is from Figure 8 A partial cross-sectional view of one of the aerostatic radial bearings of the scroll compressor 400 is shown along line 9 - 9 . The aerostatic radial bearing includes an outer surface 451 of the crankshaft 424 , a radial surface 463 of the bearing seat 458 , and a gas distribution structure 450 .

[0131] like Fig. 9 As shown, the gas distribution structure 450 forms the entire outer surface 451 of the crankshaft 424 near the bearing seat 458. Therefore, the crankshaft 424 and the gas distribution structure 450 have the same outer surface 451. However, in one embodiment, the gas distribution structure 450 may not form the entire outer surface of the crankshaft 424. For example, in one embodiment, when the gas distribution structure 450 is disposed in the axial direction (e.g., Fig. 9When viewed in the view shown in FIG. 4 ), the gas distribution structure 450 may have a portion along the circumference of the crankshaft 424 (e.g., along the direction G), and the portions of the gas distribution structure 450 may not contact each other. In one embodiment, the gas distribution structure 450 may have a plurality of portions along the axial direction of the crankshaft 424, along the circumference of the crankshaft 424, or along the axial direction of the crankshaft 424 and along the circumference of the crankshaft 424.

[0132] like Fig. 9 As shown, passage 429 fluidly connects the internal passage 462 of crankshaft 424 to gas distribution structure 450. In this way, pressurized gas is supplied from internal passage 462 to the aerostatic radial bearing. During normal operation of scroll compressor 400, gas distribution structure 450 distributes the supplied pressurized gas along its outer surface 451. The distributed pressurized gas is then squeezed between the surfaces of the aerostatic radial bearing, so that a layer of flowing pressurized gas is formed in space 461 between crankshaft 424 and bearing seat 458. In one embodiment, this layer of flowing pressurized gas supports crankshaft 424 when crankshaft 424 rotates, which prevents crankshaft 424 from contacting bearing seat 458 when crankshaft 424 rotates.

[0133] In the illustrated embodiment, the crankshaft 424 has two passages 429. However, an embodiment may include one or more passages 429, which may be adapted to adequately supply sufficient pressurized gas to the gas distribution structure 450 so that the aerostatic radial bearings may support the crankshaft 424 as the crankshaft 424 rotates. In embodiments of the gas distribution structure 450 having multiple sections (not shown), a passage 429 may be provided for each section.

[0134] Crankshaft 424 and / or aerostatic radial bearing 450 may include one or more grooves (not shown) in their surfaces. In one embodiment, the one or more grooves may be located along the radial surface and through an inner portion 427 of the inner radial surface of crankshaft 424 that faces the aerostatic radial bearing. The one or more grooves may run in an axial direction of crankshaft 424, in a circumferential direction of crankshaft 424 (e.g., in direction G), or in both an axial direction of crankshaft 424 and a circumferential direction of crankshaft 424. As described above with respect to Figure 2-6 As discussed similarly to the gas distribution structures 64, 164, 264 in FIG. 1 , the gas distribution structure 450 may have one or more inlets 421 or inlet surfaces. The grooves may allow pressurized gas to be supplied to one or more inlets 421 or inlet surfaces of the gas distribution structure 450 without requiring additional passages 429. In embodiments of the gas distribution structure 450 having multiple sections (not shown), the grooves may fluidly connect two or more inlets 421 and / or inlet surfaces of each section.

[0135] In the illustrated embodiment, the gas distribution structure 450 has a uniform thickness 449. However, the gas distribution structure 450 in an embodiment may have a non-uniform thickness 449. In an embodiment, other aerostatic radial bearings along the crankshaft, which may each include a gas distribution structure 448, 452, may have a thickness similar to Fig. 9 The structure of the first aerostatic radial bearing shown in . In one embodiment, other aerostatic radial bearings may include different surfaces (eg, an axial surface of lower bearing seat 459, a surface of movable scroll 414) facing the radial surface of the crankshaft.

[0136] Fig. 10A Shows Fig. 9 FIG. 4 is a partial enlarged view of the crankshaft aerostatic thrust bearing of the oil-free scroll compressor 400 during its normal operation. The crankshaft aerostatic thrust bearing includes an axial surface 491 of the crankshaft 424, an axial surface 492 of the lower bearing seat 459, and the gas distribution structure 454. In one embodiment, two passages 493 in the crankshaft 424 fluidly connect the gas distribution structure to the internal passage 462. Figure 8 As shown, in one embodiment, passage 469 fluidly connects the upper volume 434A of the scroll compressor 400 to the internal passage 462. Thus, the gas distribution structure 454 is fluidly connected to the upper volume 434A of the scroll compressor 400.

[0137] During operation of the scroll compressor 400, pressurized gas from the upper volume 334A is supplied to the gas distribution structure 454. As described above, the gas distribution structure 454 has a construction and / or composition (e.g., material properties, internal structure) such that it distributes the supplied pressurized gas along its outer surface 455. Therefore, the gas distribution structure 454 more evenly distributes the supplied pressurized gas to the space 495 between the axial surface 491 of the crankshaft 424 and the axial surface 492 of the lower bearing seat 459. The distribution of the pressurized gas allows the crankshaft aerostatic thrust bearing to form a flowing pressurized gas layer in the space 495. The flowing pressurized gas layer supports the crankshaft 424 in the axial direction when the crankshaft 424 rotates.

[0138] like Fig. 10A As shown, a dynamic seal 494A is disposed between an axial surface 491 of the crankshaft 424 and an axial surface 492 of the bearing seat 459. The dynamic seal 494A can guide the pressurized gas flowing from the passage 469 to the internal passage 462. In one embodiment, the dynamic seal 494A prevents the pressurized gas provided by the passage 469 from bypassing the internal passage 462. The dynamic seal 494A can be made of a material that allows it to easily contract and expand. This allows the dynamic seal 494A to provide a seal between the axial surfaces 491, 492, even if the crankshaft 424 and the lower bearing seat 459 are displaced relative to each other in the axial direction.

[0139] like Fig. 10B As shown, in place of the axial dynamic seal 494A or in addition to the axial dynamic seal 494A, a radial dynamic seal 494B can be provided in an embodiment. A rigid member 496 such as a tube can be provided with a radial dynamic seal 494B. In one embodiment, the rigid member 496 fluidly connects the connecting passage 469 and the internal passage 462. The end 497 of the rigid member 496 is pressed into the hole forming the internal passage 462. The end 497 is assembled into the internal passage 462 so that the rigid member 496 is in a fixed position relative to the crankshaft 424. Therefore, the rigid member 496 rotates with the crankshaft 424. The radial dynamic seal 494B is positioned around the connecting passage 469. In one embodiment, the radial dynamic seal 494B forms the last part of the connecting passage 469. The opposite end 498 of the rigid tube 494 is assembled into the radial dynamic seal 494B. The radial dynamic seal 494B provides a seal between the outer radial surface of the lower bearing seat 459 and the opposite end 498 of the rigid member 496. The radial dynamic seal 494B provides a seal so that the pressurized gas flowing through the connecting passage 469 flows through the rigid member and enters the internal passage 462. Fig. 10B As shown, the radial dynamic seal 494B may also include a spring 499. The spring 499 may bias the radial dynamic seal 494B against the outer surface of the rigid member 496 to improve sealing.

[0140] In the illustrated embodiment, the crankshaft 424 includes two passages 493 for the gas distribution structure 454 to distribute the pressurized gas into the space 495. However, in one embodiment, the crankshaft 424 may include one or more passages 493 for supplying pressurized fluid to the gas distribution structure 454. It should be understood that the gas distribution structure 454 may have a plurality of passages 493 and a plurality of passages 493 for supplying pressurized fluid to the gas distribution structure 454. Figure 3A-6 The gas distribution structure 454 may have similar features to the gas distribution structures 64, 164, 264 discussed in the foregoing. For example, the gas distribution structure 454 may have separate portions and / or an outer surface 455 that is inclined relative to the axial surface 491 of the crankshaft 424. Fig. 10A As shown, the gas distribution structure 454 is embedded in the crankshaft 424 so that the outer surface 455 of the gas distribution structure 454 and the axial surface 491 of the crankshaft 424 form a flat surface. However, the gas distribution structure 454 in an embodiment may protrude from the axial surface 491. In one embodiment, the entire gas distribution structure 454 may be above the axial surface 491.

[0141] Fig.11 A cross-sectional view of a vertical oil-free scroll compressor 500 is shown in FIG. In addition to the description herein, the scroll compressor 500 may have the same Figure 8-10 and described above. Scroll compressor 500 includes radial aerostatic bearings to support crankshaft 524 as crankshaft 524 rotates. Scroll compressor 500 also includes an aerostatic thrust bearing that axially supports orbiting scroll 514 as it orbits. Scroll compressor 500 also includes an aerostatic radial bearing on the eccentric end 556 of crankshaft 524.

[0142] Each aerostatic bearing along the crankshaft includes a corresponding gas distribution structure 548, 550, 552, 554. Figure 7 Similarly discussed, the scroll compressor 500 includes an aerostatic thrust bearing that supports the orbiting scroll 514 in an axial direction. The aerostatic thrust bearing includes a gas distribution structure 564 located on the orbiting scroll 514. Figure 2-6 As described above, the gas distribution structure 564 in the embodiment may be located on the surface of the bearing seat 558. For ease of understanding, Fig.11 The coupling device (eg, Oldham coupling 30) is omitted from the illustrated view.

[0143] The first radial bearing for supporting the crankshaft 524 includes a gas distribution structure 550 located on a radial surface of a bearing seat 558. The second radial bearing for supporting the crankshaft 524 includes a gas distribution structure 552 located on a radial surface of a lower bearing seat 559. The radial surface of the lower bearing seat 559 is a surface of the lower bearing seat 559 that faces the radial surface of the crankshaft 524. The crankshaft aerostatic thrust bearing, which is used to support the crankshaft 524 in the axial direction when the crankshaft rotates, includes a gas distribution structure 554 located on an axial surface of the lower bearing seat 559. The axial surface 554 is a surface of the end of the lower bearing seat 559 that faces the crankshaft 524.

[0144] The passage 569 fluidly connects the gas distribution structures 550, 552, 554 in the bearing housing 558 and the lower bearing housing 559 to the upper volume 534A of the scroll compressor 500. Thus, pressurized gas is supplied from the upper volume 534A to the aerostatic bearings supporting the crankshaft 524. Alternatively, the connecting passage 569 in an embodiment can fluidly connect the gas distribution structures 550, 552, 554 for supporting the crankshaft 524 to an external source of pressurized gas (e.g., a pressurizer, a compressor, etc.).

[0145] The orbiting scroll 514 includes passages 565, 568 that fluidly connect the discharge volumes 540 of the intermeshing fixed scroll 512 and the orbiting scroll 514 to gas distribution structures 548, 564 located on the surface of the orbiting scroll 514. The passage 568 provides pressurized gas from the discharge volume 540 to the static thrust bearing that axially supports the orbiting scroll 514. The passage 565 provides pressurized gas to the aerostatic radial bearing of the eccentric end 556 of the crankshaft 524. In one embodiment, the inlet 541 of the passage 565, 568 for one or both of the passages 565, 568 in one embodiment can be located at a different radial position, such as providing pressurized gas from an intermediately formed volume (e.g., trapped volume 516, trapped volume 517) rather than the discharge volume 640.

[0146] As described above, a pressurizer (e.g., Figure 2 A pressurizer 70 is shown as a secondary source of pressurized gas for one or more aerostatic bearings. In one embodiment, the pressurizer may be the primary source of pressurized gas that provides all of the pressurized gas to the aerostatic bearings. In one embodiment, the pressurizer may be the primary source of pressurized gas for one or more aerostatic bearings.

[0147] One aspect of the distribution structures 550, 552 located in the bearing seat 558 and the lower bearing seat 559 is that they do not rotate with the crankshaft 546. Because they do not rotate, the gas distribution structures 550, 552 are not affected by centrifugal forces. This may be advantageous because the gas distribution structures 550, 552 may not have to be firmly attached to the bearing seat 558 and the lower bearing seat 559, respectively, to account for centrifugal forces.

[0148] If the gas distribution structure is fixed to a rotating member (e.g., crankshaft 524), the flow of pressurized gas through and out of the gas distribution structure may be affected by the centrifugal forces caused by their rotation. In one embodiment, the gas distribution structure can be designed to offset possible flow issues caused by centrifugal forces. However, the gas distribution structures 550, 552 can be advantageous because they do not have to consider centrifugal forces because they are located in the bearing seat 558 and the lower bearing seat 559.

[0149] For example, this may be advantageous in a horizontal scroll compressor. In one embodiment of a horizontal scroll compressor, the gas distribution structures 550, 552 may have a configuration (e.g., internal and / or external structure, material properties) that allows the outer surface of the gas distribution structure to have a greater flow rate in an upward direction (e.g., in a direction opposite to the direction of gravity, vertically upward). In one embodiment of a horizontal scroll compressor, the radial bearings may be configured to account for (e.g., offset) the weight of the crankshaft 524. A larger gas flow in the upward direction may account for the weight of the crankshaft 524. As an example, in one embodiment of a horizontal scroll compressor, even if the bottom surface is not constant due to the rotation of the crankshaft 524, an aerostatic radial bearing or multiple bearings along the crankshaft 524 may provide greater support for the bottom of the crankshaft 524 to offset the weight of the crankshaft 524.

[0150] In one embodiment of the oil-free scroll compressor 600, pressurized gas is supplied via the orbiting scroll 614 to an aerostatic bearing supporting a crankshaft 624. The scroll compressor 600 is a vertical, single-stage scroll compressor. Fig.12 is a cross-sectional view of the scroll compressor 600. Fig.12 The view shown in omits the coupling device (e.g., Oldham coupling 30). In addition to what is shown and described herein, the scroll compressor 600 may have a Figure 8-1 0 and similar features to the scroll compressor 400 described above.

[0151] In an embodiment of the scroll compressor 600, the base plate 626 of the orbiting scroll 614 may include a passage 627 that fluidly connects the discharge volume 640 of the meshing scrolls 612, 614 to the clearance volume 625. The clearance volume 625 is the volume between one end of the crankshaft 624 (e.g., one end of the eccentric end 656) and the base plate 626 of the orbiting scroll 614. The internal passage 662 is also fluidly connected to the gas distribution structure 650, 652, 654 of the aerostatic bearing supporting the crankshaft 624. Therefore, compressed gas is supplied from the gas discharge volume 640 to the gas distribution structure 650, 652, 654 through the passage 627 in the base plate 628.

[0152] In one embodiment, a dynamic seal 690 is disposed between the eccentric end 656 of the crankshaft 624 and the base plate 628 of the movable scroll 614. The dynamic seal 690 can provide a seal between the axial surface of the eccentric end 656 of the crankshaft 624 and the axial surface of the base plate 628. The dynamic seal 690 ensures that the pressurized gas flows from the passage 627 to the internal passage 662. During operation, the movable scroll 614 can move in an axial direction relative to the crankshaft 624. Since the scroll compressor 600 includes an aerostatic thrust bearing for axially supporting the movable scroll 614, the offset may be small. However, the dynamic seal 690 is made of a material that allows it to expand and contract to take into account possible axial displacement. In this way, even if the axial distance between the crankshaft 624 and the base plate 626 changes, the dynamic seal 690 provides a seal between the base plate 626 and the crankshaft 624.

[0153] Alternatively, in one embodiment, the dynamic seal 690 may be a radial seal rather than an axial seal. A radial dynamic seal (not shown) in one embodiment may be located between the radial outer surface of the eccentric end 656 of the crankshaft 624 and the surface of the orbiting scroll 614 facing the radial outer surface of the eccentric end 656. In such an embodiment, the radial dynamic seal would be located between the gas distribution structure 650 and the interstitial volume 625. In one embodiment, the passage 627 through the base plate 626 and the internal passage 662 may be fluidly connected by a rigid member (e.g., a tube) and a radial dynamic seal in a manner similar to the internal passage 462 and the connecting passage 469, such as Fig. 10B described.

[0154] like Fig.12 As shown, the scroll compressor 600 also includes an aerostatic thrust bearing that axially supports the orbiting scroll member 614. In one embodiment, the aerostatic thrust bearing can be similar to the above-mentioned Figure 7 The orbiting scroll 614 also includes a gas distribution structure 648 for an aerostatic radial bearing for the eccentric end 656 of the crankshaft 624. In one embodiment, the aerostatic radial bearing for the eccentric end 656 can be similar to the aerostatic radial bearing for the eccentric end 656. Fig.11 The aerostatic radial bearing of the eccentric end 565 shown and described. Fig.12As shown, two passages 665, 668 fluidly connect the gas distribution structure 648, 664 located on the movable scroll member 614 to the passage 627 through the base plate 626. In the illustrated embodiment, the passages 665, 668 are shown as being fluidly connected to each other. However, the passages 665, 668 in the embodiment can be separated, so that each passage 665, 668 supplies the pressurized fluid from the passage 627 to its corresponding gas distribution structure 648, 664 through the base plate 626. In one embodiment, each passage 665, 668 can include multiple passages, so that each passage 665, 668 includes multiple passages that supply pressurized gas to the corresponding gas distribution structure 648, 664. Therefore, the pressurized fluid from the discharge volume 640 is supplied to the aerostatic bearing 614 located on the movable scroll member.

[0155] Alternatively, in one embodiment, the inlet 641 to the passage 627 can be located at a different radial position so that pressurized gas is provided from the intermediate volume (e.g., the trapped volume 616, the trapped volume 617) rather than the discharge volume 640. In the illustrated embodiment, the gas distribution structure 648 for the eccentric end 656 of the crankshaft 624 is located on the surface of the orbiting scroll member 614. Alternatively, the gas distribution structure 648 in one embodiment can be located on the radial surface of the eccentric end of the crankshaft 624, such as Figure 8 shown.

[0156] In the above manner, pressurized gas is supplied from the discharge volume 640 to the gas distribution structures 648, 650, 652, 654, 664. Thus, the gas distribution structure 648 distributes the pressurized gas to form a flowing pressurized gas layer between the radial surface of the eccentric end 656 of the crankshaft 624 and the surface of the orbiting scroll 614.

[0157] The first and second aerostatic radial bearings can support the crankshaft 624 in the radial direction when the crankshaft rotates. The gas distribution structure 650 of the first aerostatic radial bearing distributes the pressurized gas so that a flowing pressurized gas layer is formed between the radial surface of the bearing seat 658 and the radial surface of the crankshaft 624. The flowing pressurized gas layer supports the crankshaft 624 in the radial direction.

[0158] The gas distribution structure 652 of the second aerostatic radial bearing distributes the pressurized gas so that a flowing pressurized gas layer is formed between the radial surface of the crankshaft 624 and the radial surface of the lower bearing seat 659. The flowing pressurized gas layer supports the crankshaft 624 in the radial direction.

[0159] When the crankshaft 624 rotates, the crankshaft aerostatic thrust bearing can support the crankshaft 624 in the axial direction. The gas distribution structure 654 of the crankshaft aerostatic thrust bearing distributes the pressurized gas so that a flowing pressurized gas layer is formed between the axial surface of the end of the crankshaft 624 and the axial surface of the lower bearing seat 659. The pressurized gas layer supports the crankshaft 624 in the axial direction.

[0160] The gas distribution structure 664 of the aerostatic thrust bearing distributes the pressurized gas so that a flowing pressurized gas layer is formed between the rear surface 626 of the orbiting scroll 614 and the axial surface 666 of the bearing seat 658. The aerostatic thrust bearing can support the orbiting scroll 614 and its axial thrust. The aerostatic thrust bearing supports the orbiting scroll 614 in the axial direction so that the thrust does not push the orbiting scroll 614 out of the correct meshing position with the fixed scroll 612 and / or does not push the orbiting scroll 614 to contact the bearing seat 658.

[0161] As previously described, the scroll compressor 600 may include a pressurizer (e.g., Figure 1 665, internal passage 662, passage 668) or volumes (e.g., exhaust volume 640, upper volume 334A) that supply pressurized gas to one or more aerostatic bearings.

[0162] It should be understood that although the drawings show Figure 2-12 The gas distribution structure in the embodiment is embedded in the surface of a specific component (e.g., movable scroll, bearing seat, crankshaft, lower bearing seat), but this article is about Figure 2-12 Any of the gas distribution structures described may in one embodiment be attached to an outer surface of the described component. In such an embodiment, the space between the opposing surfaces may be configured to allow for such configuration of an aerostatic bearing or bearings.

[0163] Fig.13 A cross-sectional view of an embodiment of a scroll compressor 700 is shown having an aerostatic thrust bearing for supporting an orbiting scroll member 714. In one embodiment, the aerostatic thrust bearing includes a gas distribution structure having an opening 764 located in a rear surface 728 of the orbiting scroll member 714, an inner radial seal 1710, and an outer radial seal 1720. The scroll compressor 700 also includes a fixed scroll member 712 having a spiral wrap 718. The orbiting scroll member 714 includes a base plate 726 and a spiral wrap 720, which protrudes from the base plate 726 in a direction toward the fixed scroll member 712. The fixed scroll member 712 and the orbiting scroll member 714 and their respective wraps 718, 720 are intermeshed and configured to be as shown. Figure 2The scroll compressor 10 shown and described above compresses gas (e.g., refrigerant) in a similar manner. For ease of understanding, Fig.13 The connection means (eg Figure 2 The Oldham coupling 30 shown).

[0164] Similar to Figure 2 As shown in the compressor 10 and described above, the scroll compressor 700 in one embodiment includes an outer shell 722 having an upper portion 732A and a lower portion 732B, wherein the upper portion 732A includes an upper volume 734A and the lower portion 732B includes a lower volume 734B. The gas in the lower volume 734B is sucked into the intermeshing scroll members 712, 714 and compressed by the intermeshing scroll members 712, 714, and then the compressed gas is discharged from the discharge volume 740 of the scroll members 712, 714 into the upper volume 734A. The gas to be compressed enters the outer shell 722 through the suction port 736 and the compressed gas leaves the outer shell 722 through the discharge port 738.

[0165] In one embodiment, the movable scroll member 714 is Figure 2 The orbiting scroll 714 is mounted on an eccentric end 756 of a crankshaft 724, which is rotated, for example, by an electric motor 744. The electric motor 744 in the embodiment has a Figure 2 And the same structure as described above for motor 44. For example, in one embodiment, crankshaft 724 can be rotated by a mechanism other than motor 744, such as an external motor, an internal combustion engine, or other such mechanism.

[0166] like Fig.13 As shown, the compressor 700 includes radial bearings 750, 752 and thrust bearings 754 to support the crankshaft 724 when the crankshaft rotates. The compressor 700 also includes a radial bearing 748 positioned on an eccentric end 756 of the crankshaft 724 to prevent rotational motion from being transmitted to the orbiting scroll member 714. A lubricant (e.g., oil) may be provided to the bearings 748, 750, 752, 754 along the crankshaft 724. In one embodiment, the radial bearings 750, 752, 754 may be provided to the bearings 748, 750, 752, 754. Figure 2 In a similar manner as described for compressor 10 in FIG. 1 , lubricating oil is provided from oil groove 733 to bearings 748, 750, 752, 754 through internal passage 762. Embodiments include three radial bearings 748, 750, 752 and thrust bearing 754 along crankshaft 724. However, an embodiment may include one or more bearings adapted to support crankshaft 724 and allow orbiting scroll 714 to properly rotate and / or orbit relative to fixed scroll 712.

[0167] like Fig.13 and14 As shown, the aerostatic thrust bearing in one embodiment includes a rear surface 728 of the orbiting scroll 714 , a surface 766 of the bearing support member 758 facing the rear surface 728 of the orbiting scroll 714 , and a gas distribution structure including an opening 764 , an outer radial seal 1720 and an inner radial seal 1710 . Fig.14 In one embodiment Fig.13 768 in the orbiting scroll 714 fluidly connects the intermediate volume 717 of the scrolls 712, 714 to the opening 764 in the rear surface 728 of the orbiting scroll 714. In one embodiment, the passage 768 has an opening 765 along the intermediate volume 717 of the scrolls 712, 714. The passage 768 allows compressed gas from the intermediate volume 717 to flow to the gas distribution structure.

[0168] Fig.13 and 14 The gas distribution structure in includes two openings 764, and the movable scroll member 714 includes two passages 768. For example, Fig.14 A single opening 764 of the gas distribution structure is shown. In one embodiment, the gas distribution structure may include one or more openings 764 in the rear surface 728 of the orbiting scroll 714. In one embodiment, the gas distribution structure may include two or more openings 764 in the rear surface 728 of the orbiting scroll. For example, the gas distribution structure in one embodiment may include a gas distribution structure located adjacent to the rear surface 728 of the orbiting scroll. Figure 5 The five openings 764 in the rear surface 728 of the orbiting scroll member 714 are similarly located to the inlet 174 shown. In one embodiment, the orbiting scroll member 714 may include a passage 768 (e.g., such as Fig.13 In an embodiment having a plurality of openings 764, the orbiting scroll 714 may include one or more passages 786, and at least one passage 786 may be fluidly connected to the plurality of openings 764 of the gas distribution structure.

[0169] During operation of the compressor 700, the intermediate volume 717 has a higher pressure than the lower volume 734B of the compressor. Fig.13 As shown, the aerostatic thrust bearing is located in the lower volume 734B of the compressor 700. Therefore, the compressed gas flows from the intermediate volume 717 to the space 743 between the rear surface 728 of the movable scroll member 714 and the surface 766 of the bearing support member 758, and then flows from the space 743 to the lower volume 734B of the compressor 700. The compressed gas is discharged from the opening 764, as shown in FIG. Fig.14As shown by arrow B2 in , it then flows radially outward (e.g., along direction E2) or radially inward (e.g., along direction D2). When the gas flows through space 743, the thrust load of movable scroll 714 squeezes the flowing compressed gas between the rear surface 728 of movable scroll 714 and the surface 766 of bearing support member 758. Therefore, when flowing through space 743, a compressed gas layer is formed between the rear surface 728 of movable scroll 714 and the surface 766 of bearing support member 758. The compressed gas layer formed by the aerostatic thrust bearing provides support in direction C2 to support the thrust load of movable scroll 714.

[0170] The gas distribution structure in one embodiment also includes an inner radial seal 1710 and an outer radial seal 1720. In one embodiment, the radial seals 1710 and 1720 are located between the movable scroll 714 and the bearing support member 715. Each of the radial seals 1710 and 1720 extends along the circumference of the rear surface 728 of the movable scroll 714. In one embodiment, each radial seal 1710 and 1720 is annular. The inner radial seal 1710 is located radially inside the opening 764, and the outer radial seal 1720 is located radially outside the opening 764. In one embodiment, the inner radial seal 1710 can extend to the vicinity of the outer diameter of the base plate 726 of the movable scroll 714. The radial seals 1710 and 1720 are embedded in the surface 766 of the bearing support structure 758. However, in one embodiment, one or two of the radial seals 1710 and 1720 may be disposed on the surface 766 of the bearing support structure 758 without being embedded. In one embodiment, one or both of the radial seals 1710 , 1720 may be disposed on the rear surface 728 of the orbiting scroll 714 .

[0171] like Fig.14As shown, the inner radial seal 1710 has a thickness 1712 (e.g., a dimension in the axial direction), and the outer radial seal 1720 has a thickness 1722, which causes the radial seals 1710, 1720 to extend into the space 743. The inner radial seal 1710 forms a restriction 1714 for compressed gas flowing radially inward (e.g., in the direction D2), and the outer radial seal 1720 forms a restriction 1724 for compressed gas flowing radially outward (e.g., in the E2 direction). The axial length of each restriction 1714, 1724 is shorter than the axial length 739 of the space 743. In one embodiment, the radial seals 1710, 1720 allow a pressurized gas layer to be formed in the radial direction between the radial seals 1710, 1720, while also radially restricting compressed gas from between portions of the space 743 between the radial seals 1710, 1720. In one embodiment, radial seals 1710 , 1720 are advantageous because they limit the amount of pressurized gas that needs to be provided to space 743 to form a layer of pressurized gas that adequately supports orbiting scroll 714 in a radial direction.

[0172] Since the restricting portions 1714 and 1724 have an axial length in the axial direction of the space 743 that is smaller than the axial length 739, the compressed gas is forced to be severely compressed when passing through the restricting portions 1714 and 1724 in the radial direction (e.g., along the direction E2 or the direction D2). In addition, the orbit of the movable scroll 714 can cause the pressurized gas in the space 743 to flow radially outward due to friction. When the compressed gas is subjected to force in the radially outward direction, it is forced to pass through the restricting portions 1714 and 1724 and is further compressed. In this way, in addition to the Fig.13 and 14 In addition to the aerostatic support provided by the aerostatic thrust bearing, the aerostatic thrust bearing may also provide a portion of further compressed gas in restrictions 1714, 1724, which provides aerodynamic support for orbiting scroll member 714. In such an embodiment, the aerostatic thrust bearing may also be referred to as a hybrid aerostatic / aerodynamic thrust bearing.

[0173] In one embodiment, radial seals 1710, 1720, passages 768 and openings 764 are configured so that aerostatic thrust provides sufficient support for the orbiting scroll 714 in the axial direction while limiting the amount of compressed gas required to provide sufficient support. In one embodiment, radial seals 1710, 1720 may be configured to have specific lengths 1712, 1722 to provide a desired length in the axial direction for the restriction 1714, 1724. For example, in an embodiment, it may be desirable that the length of the restriction 1714, 1724 in the axial direction is small to minimize the flow of compressed gas from space 743. In one embodiment, passage 768 may be configured to connect to intermeshing scrolls of different volumes (e.g., intermediate volume 716, discharge volume 740) or having different sizes (e.g., cross-sectional area) to control the amount of gas flowing through one of the more openings 764 of the gas distribution structure. As described above, the gas distribution structure in one embodiment may have one or more openings 764 to allow the compressed gas to adequately flow into and be distributed around the circumference of the rear surface 728 of the orbiting scroll 714 .

[0174] In one embodiment, the opening 764 can be disposed on the bearing support member 758 instead of the surface 766 of the orbiting scroll 714. In such an embodiment, the compressor 700 can include a passage that extends partially through the bearing support member 758 to provide compressed gas. For example, the passage in such an embodiment can be similar to Figure 2 Passage 68 shown in and described above.

[0175] As previously described, the scroll compressor 700 may include a pressurizer (e.g., Figure 1 70 shown in FIG. 1 ). In one embodiment, the pressurizer may be fluidly connected to, for example, a passage (e.g., passage 768, passage 68) or volume (e.g., exhaust volume 740, upper volume 734A, intermediate volume 717) that supplies pressurized gas to the aerostatic thrust bearing. In one embodiment, the gas distribution structure may also include the above-described Figure 2 or Figure 7 The porous material in question.

[0176] exist Fig.15 A cross-sectional view of a vertical oil-free scroll compressor 800 is shown in FIG. In addition to what is described herein, the scroll compressor 800 may have the same Fig.14 The oil-free scroll compressor 800 includes an aerostatic thrust bearing to support the orbiting scroll member 814 in the axial direction, similar to the scroll compressor 700 shown in FIG. Fig.14 An aerostatic thrust bearing as shown in and described above. Fig.15As shown, the aerostatic thrust bearing in the embodiment includes the rear surface 828 of the orbiting scroll 814, the surface 866 of the bearing support member 858, the gas distribution structure having the opening 864, the outer radial seal 1820 and the inner radial seal 1810. The aerostatic thrust bearing in one embodiment may have the same Fig.14 A similar construction to the aerostatic thrust bearing shown in and described above.

[0177] Compressor 800 has aerostatic bearings along crankshaft 824 . Fig.15 The aerostatic bearings along the crankshaft 824 shown in FIG. 8 are similar to those shown in FIG. Fig.11 The aerostatic bearings along the crankshaft 524 are shown and described above. In one embodiment, Fig.15 The construction of the aerostatic bearing and the construction for providing compressed gas to the aerostatic bearing may be similar to that of Fig.11 Each aerostatic bearing along the crankshaft 824 includes a corresponding gas distribution structure 848, 850, 852, 854. Each gas distribution structure 848, 850, 852, 854 includes a porous material.

[0178] In one embodiment, passage 865 fluidly connects the exhaust volume 840 to the gas distribution structure 848. Thus, compressed gas is provided to the aerostatic radial bearing along the eccentric end 856 of the crankshaft. In one embodiment, passage 865 can be connected to different volumes (e.g., intermediate volume 816, intermediate volume 817). In one embodiment, passage 865 can be connected to passage 868 that provides compressed gas to the gas distribution structure 864. Passage 869 connects the gas distribution structures 850, 852, 854, 859 in the bearing seat 858 and the lower bearing seat 859 to the upper volume 834A of the scroll compressor 800. Thus, pressurized gas is supplied from the upper volume 834A to the aerostatic bearing along the crankshaft 824. Alternatively or additionally, the connecting passage 869 in one embodiment can fluidly connect the gas distribution structures 850, 852, 854 supporting the crankshaft 524 to an external pressurized gas source (e.g., a pressurizer, a compressor, etc.).

[0179] Fig.15 The compressor 800 shown in FIG. 8 has three aerostatic radial bearings and one aerostatic thrust bearing along the crankshaft 824. However, an embodiment may include one or more aerostatic bearings at any particular location along the crankshaft 24. The bearings may be included to suitably support the crankshaft 824 and allow the orbiting scroll 814 to properly rotate and / or orbit relative to the fixed scroll 812.

[0180] In one embodiment, one or more of the gas distribution structures 848, 850, 852, 854 may be disposed in the crankshaft 824 rather than in the bearing seats 858, 859 or the orbiting scroll 814. For example, in such an embodiment, Fig.15 The aerostatic bearing and the structure for providing compressed gas to the aerostatic bearing can be similar to the aerostatic bearing of Figure 8 The aerostatic bearing shown in and described above. For example, in such an embodiment, Fig.15 The construction of the aerostatic bearing and the construction for providing compressed gas to the aerostatic bearing may be similar to that described in Fig.12 An aerostatic bearing as shown in and described above.

[0181] aspect:

[0182] Any of aspects 1-16 may be combined with any of aspects 17-39, and any of aspects 17-21 may be combined with any of aspects 22-39.

[0183] Aspect 1. A scroll compressor, comprising:

[0184] a first scroll member having a base plate and a spiral wrap protruding from a surface of the base plate;

[0185] a second scroll member having a base plate and a spiral wrap protruding from a surface of the base plate;

[0186] an aerostatic thrust bearing supporting the second scroll member in an axial direction and comprising: a surface of the second scroll member, a surface of a fixed support member, and a gas distribution structure, wherein:

[0187] A pressurized gas source supplies pressurized gas to the gas distribution structure; and

[0188] The gas distribution structure forms a gas layer between a surface of the stationary support member and a surface of the second scroll member.

[0189] Aspect 2. The scroll compressor of aspect 1, wherein the pressurized gas comprises gas that has been compressed by the first scroll member and the second scroll member.

[0190] Aspect 3. The scroll compressor according to any one of aspects 1 or 2, wherein the gas distribution structure includes two or more parts, and each part is supplied with the pressurized gas.

[0191] Aspect 4. The scroll compressor according to any one of aspects 1 to 3, wherein an upper surface of the gas distribution structure is annular, so that the gas distribution structure distributes gas along the entire circumference of the surface of the second scroll member.

[0192] Aspect 5. The scroll compressor according to any one of aspects 1 to 4, wherein an upper surface of the gas distribution structure is inclined.

[0193] Aspect 6. The scroll compressor according to any one of aspects 1 to 5, wherein the gas distribution structure is located on the rear surface of the second scroll member.

[0194] Aspect 7. The scroll compressor according to any one of aspects 1 to 6, further comprising:

[0195] a passageway within the second scroll member, the passageway fluidly connecting a volume between the first scroll member and the second scroll member to the gas distribution structure, wherein:

[0196] The volume between the first scroll member and the second scroll member is a source of pressurized gas.

[0197] Aspect 8. The scroll compressor according to any one of aspects 1 to 5, wherein the gas distribution structure is located on a surface of the fixed support member.

[0198] Aspect 9. The scroll compressor according to any one of aspects 1-6 and 8, further comprising:

[0199] an upper volume into which gas compressed by the first and second scroll members is discharged; and

[0200] The upper volume fluid is connected to a connecting channel of the gas distribution structure, wherein

[0201] The source of the compressed gas is the upper volume.

[0202] Aspect 10. The scroll compressor according to any one of aspects 1-9, wherein the pressurized gas source comprises an external pressurized gas source.

[0203] Aspect 11. The scroll compressor according to any one of aspects 1 to 10, wherein the gas distribution structure comprises a porous material.

[0204] Aspect 12. A scroll compressor according to any one of aspects 1-11, wherein the gas distribution structure includes an inner radial seal and an outer radial seal, and the inner radial seal and the outer radial seal are located between the second scroll member and the fixed support member.

[0205] Aspect 13. A scroll compressor according to any one of Aspects 1-12, wherein the gas distribution structure also includes one or more openings located in the rear surface of the second scroll member or the surface of the fixed support member, and the one or more openings are located between the inner radial seal and the outer radial seal in the radial direction of the second scroll member.

[0206] Aspect 14. The scroll compressor according to any one of aspects 1 to 13, further comprising:

[0207] A flow control device controls the flow of pressurized gas supplied to the gas distribution structure.

[0208] Aspect 15. The scroll compressor according to any one of aspects 1 to 14, further comprising:

[0209] Inlet gas intake port;

[0210] a lower volume fluidly connected to the inlets of the first and second scroll members and fluidly connected to the suction port, wherein

[0211] The gas flowing into the inlets of the first and second scroll members includes gas exhausted from the gas distribution structure.

[0212] Aspect 16. The scroll compressor according to any one of aspects 1 to 15, further comprising:

[0213] A pressurizer provides a second source of pressurized gas to the gas distribution structure.

[0214] Aspect 17. A method of supporting an orbiting or moving scroll member in a scroll compressor, wherein a fixed support member is positioned within the scroll compressor such that a surface of the fixed support member faces a surface of the orbiting or moving scroll member, the method comprising:

[0215] providing a gas distribution structure on a surface of the fixed support member or a surface of the rotating or orbiting scroll member; supplying pressurized gas from a pressurized gas source to the gas distribution structure; and

[0216] The gas distribution structure forms a layer of gas between the orbiting or moving scroll member and the fixed support, which layer of gas supports the thrust load of the orbiting or moving scroll member.

[0217] Aspect 18. The method according to aspect 17, wherein the gas distribution structure comprises a porous material.

[0218] Aspect 19. The method according to aspect 17 or 18, wherein the gas distribution structure includes an inner radial seal and an outer radial seal, the inner radial seal and the outer radial seal are located between the rotating or orbiting scroll member and the fixed support member.

[0219] Aspect 20. The method according to any one of aspects 17-19, wherein the pressurized gas source comprises an internal pressurized gas source.

[0220] Aspect 21. The method according to any one of aspects 17-20, further comprising:

[0221] When the flow rate or pressure of the pressurized gas from the pressurized gas source is insufficient to support the thrust load, pressurized gas is supplied from the second pressurized gas source to the gas distribution structure.

[0222] Aspect 22. An oil-free scroll compressor, comprising:

[0223] a first scroll member having a base plate and a spiral wrap protruding from the base plate;

[0224] a second scroll member having a base plate and a spiral wrap protruding from the base plate;

[0225] an aerostatic thrust bearing supporting the second scroll member in an axial direction and comprising:

[0226] a rear surface of the base plate of the second scroll member,

[0227] The surface to which the support member is fixed, and

[0228] A gas distribution structure located on one of the rear surface of the second scroll member or the surface of the fixed support member, wherein

[0229] When supplied with pressurized gas, the gas distribution structure forms a pressurized gas layer between the rear surface of the base plate of the second scroll member and the surface of the fixed support member;

[0230] a crankshaft to rotate the second scroll member; and

[0231] An aerostatic radial bearing, the aerostatic radial bearing is used to support the crankshaft when the crankshaft rotates, and the aerostatic radial bearing includes:

[0232] The outer surface of the crankshaft,

[0233] a support surface facing the outer surface of the crankshaft, and

[0234] a second gas distribution structure located on one of an outer surface or a support surface of the crankshaft, wherein:

[0235] When supplied with pressurized gas, the gas distribution structure forms a gas layer between the outer surface of the crankshaft and the support surface facing the outer surface of the crankshaft.

[0236] Aspect 23. The oil-free scroll compressor of Aspect 22, wherein the gas distribution structure is located on the rear surface of the second scroll member.

[0237] Aspect 24. The oil-free scroll compressor according to any one of Aspects 22 or 23, further comprising:

[0238] A passageway is located within the second scroll member, the passageway fluidly connecting a volume between the first scroll member and the second scroll member to the gas distribution structure, the passageway being configured to supply the pressurized gas from the volume between the first scroll member and the second scroll member to the gas distribution structure.

[0239] Aspect 25. The oil-free scroll compressor of any one of Aspects 22-23, wherein the gas distribution structure is located on a surface of the fixed support member.

[0240] Aspect 26. The oil-free scroll compressor according to any one of Aspects 22 or 25, further comprising:

[0241] an upper volume, wherein gas compressed by the first scroll member and the second scroll member is discharged into the upper volume; and

[0242] The upper volume is fluidly connected to a connecting passage to a gas distribution structure, the connecting passage being configured to supply pressurized gas from the upper volume to the gas distribution structure.

[0243] Aspect 27. The oil-free scroll compressor according to any one of aspects 22-26, wherein the pressurized gas is supplied to the gas distribution structure from an external pressurized gas source.

[0244] Aspect 28. The oil-free scroll compressor according to any one of aspects 22-27, wherein the gas distribution structure comprises a porous material.

[0245] Aspect 29. The oil-free scroll compressor according to any one of aspects 22-28, wherein the gas distribution structure includes an inner radial seal and an outer radial seal, and the inner radial seal and the outer radial seal are located between the second scroll member and the fixed support member.

[0246] Aspect 30. A scroll compressor according to any one of Aspects 22-29, wherein the gas distribution structure includes one or more openings on the rear surface of the second scroll member or the surface of the fixed support member, and the one or more openings are located between the inner radial seal and the outer radial seal in the radial direction of the second scroll member.

[0247] Aspect 31. The scroll compressor according to any one of aspects 22-30, further comprising:

[0248] Inlet gas intake port;

[0249] a lower volume fluidly connected to the inlets of the first and second scroll members and fluidly connected to the suction port, wherein:

[0250] The gas flowing into the inlets of the first and second scroll members includes gas distributed by the gas distribution structure.

[0251] Aspect 32. The oil-free scroll compressor according to any one of aspects 22-31, wherein the pressurized gas supplied to the gas distribution structure includes gas that has been compressed by the first scroll member and the second scroll member.

[0252] Aspect 33. The oil-free scroll compressor according to any one of aspects 22-32, wherein:

[0253] a second gas distribution structure located on an outer surface of the crankshaft; and

[0254] The crankshaft includes an internal passage fluidly connected to the second gas distribution structure, the internal passage being configured to supply pressurized gas to the second gas distribution structure.

[0255] Aspect 34. The oil-free scroll compressor according to any one of aspects 22-33, further comprising:

[0256] A passage in the second scroll member baseplate fluidly connects the volume between the first scroll member and the second scroll member to the internal passage of the crankshaft.

[0257] Aspect 35. The oil-free scroll compressor of Aspect 34, wherein a volume between the first scroll member and the second scroll member is a displacement volume of the first scroll member and the second scroll member.

[0258] Aspect 36. The oil-free scroll compressor according to Aspect 34, wherein the volume between the first scroll member and the second scroll member is an intermediate volume between the first scroll member and the second scroll member.

[0259] Aspect 37. The oil-free scroll compressor according to any one of aspects 22-32, wherein the second gas distribution structure is located on the support surface.

[0260] Aspect 38. The oil-free scroll compressor according to any one of aspects 22-37, wherein an internal pressurized gas source supplies pressurized gas to the second gas distribution structure.

[0261] Aspect 39. The oil-free scroll compressor according to any one of aspects 22-38, further comprising:

[0262] An aerostatic thrust bearing for supporting a crankshaft when the crankshaft rotates, the aerostatic thrust bearing comprising an axial surface of the crankshaft, a support surface facing the axial surface of the crankshaft, and a third gas distribution structure, wherein:

[0263] When supplied with pressurized gas, the gas distribution structure forms a gas layer between the axial surface of the crankshaft and the support surface facing the axial surface of the crankshaft.

[0264] The examples disclosed in this application are to be considered in all respects as illustrative and not restrictive. The scope of the invention is indicated by the appended claims rather than by the foregoing description, and all changes within the meaning and range of equivalency of the claims are intended to be embraced within the scope of this application.

Claims

1. A scroll compressor, characterized in that: include: a first scroll member having a base plate and a spiral wrap protruding from a surface of the base plate; a second scroll member having a base plate and a spiral wrap protruding from a surface of the base plate; An aerostatic thrust bearing, the aerostatic thrust bearing supports the second scroll member in an axial direction and includes a surface of the second scroll member, a surface of a fixed support member and a gas distribution structure, the gas distribution structure includes a radial seal disposed on one or more of the second scroll member and the fixed support member, the radial seal extending into a space between the surface of the fixed support member and the surface of the second scroll member, the radial seal extending into the space in the axial direction by a distance shorter than a length of the space in the axial direction, wherein A pressurized gas source supplies pressurized gas to the gas distribution structure; and The gas distribution structure forms a gas layer between a surface of the stationary support member and a surface of the second scroll member.

2. The scroll compressor according to claim 1, characterized in that: The pressurized gas includes gas that has been compressed by the first scroll member and the second scroll member.

3. The scroll compressor according to claim 1, characterized in that: The gas distribution structure is located on a rear surface of the second scroll member.

4. The scroll compressor according to claim 3, characterized in that: Also includes: a passageway within the second scroll member, the passageway fluidly connecting a volume between the first scroll member and the second scroll member to the gas distribution structure, wherein: The volume between the first and second scroll members is the source of the pressurized gas.

5. The scroll compressor according to claim 1, characterized in that: The gas distribution structure is located on a surface of the fixed support member.

6. The scroll compressor according to claim 5, characterized in that: Also includes: an upper volume into which gas compressed by the first scroll member and the second scroll member is discharged; as well as a connecting passage connecting the upper volume fluid to the gas distribution structure, wherein The source of the compressed gas is the upper volume.

7. The scroll compressor according to claim 1, characterized in that: The gas distribution structure includes a porous material.

8. The scroll compressor according to claim 1, characterized in that: The radial seals include inner and outer radial seals located between the second scroll member and the stationary support member.

9. The scroll compressor according to claim 8, characterized in that: The gas distribution structure further includes one or more openings in the rear surface of the second scroll member or the surface of the fixed support member, the one or more openings being located between the inner radial seal and the outer radial seal in a radial direction of the second scroll member.

10. The scroll compressor according to claim 9, characterized in that: The gas distribution structure includes two or more of the one or more openings.

11. The scroll compressor according to claim 8, characterized in that: Also includes: a crankshaft that causes the second scroll member to rotate or orbit; as well as An aerostatic radial bearing for supporting the crankshaft as the crankshaft rotates, the aerostatic radial bearing comprising: The outer surface of the crankshaft, a support surface facing the outer surface of the crankshaft, and a second gas distribution structure located on one of the outer surface or the support surface of the crankshaft, wherein When supplied with pressurized gas, the gas distribution structure forms a gas layer between the outer surface of the crankshaft and the support surface facing the outer surface of the crankshaft, Wherein, the scroll compressor is an oil-free scroll compressor.

12. The scroll compressor according to claim 11, characterized in that: the second gas distribution structure is located on the outer surface of the crankshaft, and The crankshaft includes an internal passage fluidly connected to the second gas distribution structure, the internal passage being configured to supply the pressurized gas to the second gas distribution structure.

13. The scroll compressor according to claim 12, characterized in that: Also includes: A passage in the base plate of the second scroll member fluidly connects the volume between the first scroll member and the second scroll member to the internal passage of the crankshaft.

14. The scroll compressor according to claim 1, characterized in that: Also includes: A pressurizer provides a second pressurized gas source to the gas distribution structure.

15. A method of supporting a rotating or orbiting scroll member in a scroll compressor, wherein a fixed support member is positioned within the scroll compressor so that a surface of the fixed support member faces a surface of the rotating or orbiting scroll member, characterized in that: The method comprises: providing a gas distribution structure on a surface of the fixed support member or a surface of the rotating or orbiting scroll member, the gas distribution structure comprising a radial seal provided on one or more of the rotating or orbiting scroll member and the fixed support member, the radial seal extending into a space between the surface of the fixed support member and the surface of the rotating or orbiting scroll member, the radial seal extending into the space by a distance in an axial direction shorter than a length of the space in the axial direction; supplying pressurized gas from a pressurized gas source to the gas distribution structure; and The gas distribution structure forms a gas layer between the orbiting or orbiting scroll member and the fixed support member, the gas layer supporting the thrust load of the orbiting or orbiting scroll member.

16. The method according to claim 15, characterized in that The gas distribution structure comprises a porous material, or The radial seals include inner and outer radial seals located between the orbiting or orbiting scroll member and the stationary support member.

17. The method according to claim 16, characterized in that The gas distribution structure includes the inner radial seal, the outer radial seal, and one or more openings on the surface of the rotating or orbiting scroll member or the surface of the fixed support member, the one or more openings being located between the inner radial seal and the outer radial seal in the radial direction of the rotating or orbiting scroll member, and The pressurized gas is supplied from the pressurized gas source to the gas distribution structure through one or more openings.

18. The method according to claim 15, characterized in that The orbiting or orbiting scroll member intermeshes with a fixed scroll member, and the volume between the orbiting or orbiting scroll member and the fixed scroll member is the source of pressurized gas.

19. The method according to claim 18, characterized in that The volume between the orbiting or orbiting scroll member and the fixed scroll member is an intermediate volume between the orbiting or orbiting scroll member and the fixed scroll member.

20. The method according to claim 15, characterized in that Also includes: When the flow rate or pressure of the pressurized gas from the pressurized gas source is insufficient to support the thrust load, pressurized gas is supplied from a second pressurized gas source to the gas distribution structure.

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