WO2021164239A1 - 压缩机 - Google Patents

压缩机 Download PDF

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Publication number
WO2021164239A1
WO2021164239A1 PCT/CN2020/114449 CN2020114449W WO2021164239A1 WO 2021164239 A1 WO2021164239 A1 WO 2021164239A1 CN 2020114449 W CN2020114449 W CN 2020114449W WO 2021164239 A1 WO2021164239 A1 WO 2021164239A1
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WO
WIPO (PCT)
Prior art keywords
compressor
housing
oil
blocking member
fluid
Prior art date
Application number
PCT/CN2020/114449
Other languages
English (en)
French (fr)
Inventor
秦岩
周娟娟
陆俊
Original Assignee
艾默生环境优化技术(苏州)有限公司
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Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2021164239A1 publication Critical patent/WO2021164239A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present disclosure relates to a compressor, and more particularly, to a compressor that can effectively separate working fluid sucked into a casing from oil on the inner wall of the casing.
  • Compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems.
  • the scroll compressor includes a compression mechanism for compressing a working fluid (such as a refrigerant), and the compression mechanism further includes a movable scroll part and a fixed scroll part.
  • the compression mechanism is driven by a motor through a rotating shaft to compress the fluid.
  • sufficient lubricating oil is needed to realize the lubrication of the bearing, the sealing, lubrication and cooling of the movable scroll component and the fixed scroll component.
  • the oil circulation rate can be used to characterize the amount of lubricating oil carried by the working fluid. Excessive oil circulation rate will reduce the heat exchange efficiency of the system, and will also cause reliability problems such as compressor failure due to lack of oil.
  • the positive displacement oil pump of the scroll compressor will pump more oil under high-speed operation, and the centrifugal force generated at high-speed rotation will also be large, which will cause a large amount of oil to be thrown or splashed to the compressor shell
  • the oil thrown on the inner wall of the casing is mixed with the working fluid sucked into the casing via the fluid suction fitting, and is taken out of the compressor, thereby causing a large oil circulation rate.
  • some methods to reduce the oil circulation rate have been used to separate the oil on the inner wall of the housing and the working fluid sucked into the housing through the fluid suction fitting, but the separation effect is limited.
  • An object of the present disclosure is to provide a compressor that can effectively separate the working fluid sucked into the casing from the oil on the inner wall of the casing, thereby effectively reducing the oil circulation rate.
  • Another object of the present disclosure is to provide a compressor that can guide the working fluid to the upper member of the compressor while isolating the working fluid sucked into the casing from the oil on the inner wall of the casing to further reduce the oil circulation rate.
  • Another object of the present disclosure is to provide a compressor that can guide the working fluid to the lower member of the compressor while isolating the working fluid sucked into the casing from the oil on the inner wall of the casing to further reduce the temperature of the motor.
  • Another object of the present disclosure is to provide a compressor that has a simple structure and is easier to assemble and manufacture.
  • a compressor comprising: a casing having a suction port, an inner wall of the casing, and an outer wall of the casing; compression Mechanism, the compression mechanism is used to compress the working fluid; a drive mechanism, the drive mechanism is used to drive the compression mechanism; a fluid suction fitting, the fluid suction fitting is arranged at the suction port of the housing to The inside of the housing is in fluid communication.
  • the compressor is provided with an oil blocking member on the inner side of the casing for isolating the working fluid sucked into the casing through the fluid suction fitting from the oil on the inner wall of the casing.
  • the member includes an inward protrusion provided on the inner wall of the housing around the suction port, and/or, the fluid suction fitting includes an outer tube and an inner tube sleeved in the outer tube, the inner tube It includes an inner end extending beyond the suction port, and the oil blocking member is constituted by the inner end.
  • the inner end portion of the outer tube is connected to the outer wall of the housing, and/or, the outer tube An inner convex portion is provided, and the inner tube and the outer tube are connected to each other via the inner convex portion.
  • the inner end portion of the inner tube is a straight tube, curved upward in the axial direction of the compressor, or It is bent downward in the axial direction of the compressor.
  • the compressor in the case where the oil blocking member is constituted by the inner end, the compressor is further provided with a fitting that faces the inner end for opposing through the fluid suction A suction shield that guides the working fluid sucked into the housing.
  • the inward protrusion is a complete annular structure provided around the suction port or is provided only in the Part of the ring structure above the suction port.
  • the inward protrusion is: an annular cylinder connected to the inner wall of the housing, by making the housing An annular bulge formed by a portion of the body adjacent to the suction port protruding inward, or a folded portion formed by bending a portion of the housing that defines the suction port inward.
  • the positions of the suction port and the oil blocking member and the position of the fluid inlet of the compression mechanism are positioned to be staggered in the axial direction of the compressor.
  • the extension length of the oil blocking member in the housing is 1 mm to 10 mm.
  • the extension length of the oil blocking member in the housing is 5 mm to 6 mm.
  • the compressor is a low-pressure side scroll compressor.
  • the working fluid sucked in through the fluid suction fitting can flow through the oil blocking member when flowing into the casing, so that the compressor
  • the lubricating oil thrown out and splashed on the inner wall of the compressor housing during the operation of the compressor is effectively separated from the working fluid sucked into the housing through the fluid suction fitting, so the oil circulation rate can be effectively reduced to ensure the replacement of the system Thermal efficiency and eliminate reliability problems such as compressor failure due to lack of oil.
  • the oil blocking member in addition to effectively separating the oil on the inner wall of the housing from the sucked working fluid, it can also be The working fluid is directed to the upper part of the compressor such as the compression mechanism to further reduce the oil circulation rate, or to the lower part of the compressor such as the drive mechanism to lower the temperature of the motor, or to the upper and lower parts of the compressor In order to balance the distribution ratio of the upward and downward directions of the working fluid, the oil circulation rate and the motor temperature are reduced at the same time.
  • the oil blocking member on the casing, the structure of the fluid suction fitting of the compressor does not become complicated, and therefore it is easier to assemble and manufacture.
  • Fig. 1 shows a longitudinal sectional view of a compressor according to the related art.
  • Fig. 2 shows a schematic partial cross-sectional view of the compressor according to the first embodiment of the present disclosure, in which the oil blocking member is the inner end of the inner pipe of the fluid suction fitting.
  • Fig. 3 shows a schematic partial cross-sectional view of a compressor according to a second embodiment of the present disclosure, in which the oil blocking member is an inner end of a fluid suction pipe extending into the casing of the compressor.
  • FIG. 4 shows a schematic partial cross-sectional view of a compressor according to a modification of the second embodiment of the present disclosure, in which the oil blocking member is designed to be bent upward in the axial direction.
  • Fig. 5 shows a schematic partial cross-sectional view of a compressor according to another modification of the second embodiment of the present disclosure, in which the oil blocking member is designed to be axially bent downward.
  • Fig. 6 shows a schematic partial cross-sectional view of the cooperation of the oil blocking member and the suction blocking member of the compressor according to the second embodiment of the present disclosure.
  • Fig. 7 shows a schematic partial cross-sectional view of a compressor according to a third embodiment of the present disclosure, in which the oil blocking member is an annular cylinder connected to the inner wall of the housing.
  • Fig. 8 shows a schematic partial cross-sectional view of a compressor according to a modification of the third embodiment of the present disclosure, in which the oil blocking member is an annular bulge formed on the housing.
  • FIG. 9 shows a schematic partial cross-sectional view of a compressor according to another modification of the third embodiment of the present disclosure, in which the oil blocking member is formed by bending inwardly the portion of the casing defining the suction port Fold.
  • FIG. 1 is a longitudinal sectional view of the compressor according to the related art.
  • the compressor 10' (herein taking the low-pressure side scroll compressor as an example) includes a housing 20', a driving mechanism 30', a compression mechanism 40', a main bearing seat 50', and a fluid suction pipe ( Fluid suction fitting) 60' and fluid discharge pipe 70', etc.
  • the housing 20' can accommodate the driving mechanism 30', the compression mechanism 40' and the main bearing housing 50'.
  • the fluid suction pipe 60' is provided on the low pressure side of the casing 20' for sucking in working fluid (such as refrigerant), and the fluid discharge pipe 70' is provided on the high pressure side of the casing 20' for discharging the compressed fluid.
  • the fluid suction pipe 60' may be attached to the housing 20' through a mounting flange 62' at the suction port 22' of the housing 20' and be in fluid communication with the inside of the housing 20'.
  • the fluid suction pipe 60' also has a nozzle 64' opening at the suction port 22' of the casing 20', and the sucked working fluid flows through the nozzle 64' and enters the casing 20'.
  • the nozzle 64' of the fluid suction pipe 60' and the suction port 22' of the housing 20' have substantially the same central axis.
  • the driving mechanism 30' includes a motor and a rotating shaft 32'.
  • the motor may include a stator 33' and a rotor 34'.
  • the stator 33' may be fixed to the housing 20'.
  • the rotor 34' may be press-fitted to the rotating shaft 32', and the rotating shaft 32' may be rotatably driven by the rotor 34' to drive the compression mechanism 40'.
  • the compression mechanism 40' is provided in the housing 20' to compress the working fluid sucked in from the fluid suction pipe 60' and then discharge the compressed fluid from the fluid discharge pipe 70' to the compressor 10'.
  • the compression mechanism 40' generally includes a fixed scroll member 42' and a movable scroll member 44'.
  • the driving mechanism 30' drives the movable scroll member 44' via the rotating shaft 32' so that the movable scroll member 44' performs translational rotation with respect to the fixed scroll member 42'.
  • a series of compression chambers formed by the helical blades (not shown) of the movable scroll member 44' and the helical blades (not shown) of the fixed scroll member 42' are joined to each other from the radially outer side to the radially inner side.
  • the compressor 10' also includes an oil sump 80'.
  • the oil sump 80' may be provided at the lower end of the housing 20' and may be used to provide lubricating oil to the moving parts of the compressor 10', such as the compression mechanism 40', drive bearing, thrust surface, and main bearing.
  • the lubricating oil supplied to the relevant movable parts of the compressor 10' such as the drive bearing, thrust surface, and main bearing, is thrown out and splashed onto the compressor casing 20'.
  • the lubricating oil on the inner wall of the housing will often mix with the working fluid (e.g.
  • some methods are also used to reduce oil circulation.
  • One of the methods is to integrally install a suction shield on the main bearing housing of the compressor, leaving a gap between the suction shield and the inner wall of the housing.
  • the suction shield can guide the flow direction of the working fluid sucked into the compressor housing from the fluid suction pipe to avoid mixing with lubricating oil at other positions in the housing.
  • the working fluid sucked into the compressor housing through the fluid suction pipe will easily The effect of mixing with the oil thrown out to the inner wall of the casing, thereby being able to separate the oil is limited.
  • Another way is to weld the suction shield to the housing by adding new stamping parts and additional welding processes.
  • the suction shield can guide the flow direction of the working fluid sucked into the compressor housing from the fluid suction pipe to avoid mixing with lubricating oil at other locations in the housing.
  • the working fluid sucked into the compressor housing will easily interact with the working fluid in the compressor housing.
  • the oil on the inner wall of the shell is mixed, thereby the effect of separating the oil is also limited, and new parts and additional processes are introduced, which complicates the installation and manufacturing. Separating the oil and the sucked working fluid through these two methods will cause a large amount of oil to mix with the working fluid and eventually be taken out of the compressor, which will degrade the performance of the system and may also cause the compressor to fail due to lack of oil.
  • the method according to the present disclosure in order to effectively separate the lubricating oil thrown out and splashed onto the inner wall of the compressor housing during the operation of the compressor from the working fluid sucked into the housing via the fluid suction pipe, the method according to the present disclosure
  • the compressor is also provided with an oil blocking member which will be described later.
  • FIGS. 2 to 9 the oil blocking member of the compressor according to various embodiments of the present disclosure will be described with reference to FIGS. 2 to 9. It should be noted here that in FIGS. 2 to 9 and related descriptions, only the device structure closely related to the technical solution of the present disclosure is described and shown, and the technical content of the present disclosure is omitted. And other details known to those skilled in the art.
  • the compressor according to the present disclosure is provided inside the casing 20 with an oil blocking member for isolating the fluid sucked into the inside of the casing via the fluid suction fitting from the oil on the inner wall of the casing.
  • the casing 20 of the compressor has a suction port 22, an outer wall 26 of the casing, and an inner wall 27 of the casing.
  • the fluid suction fitting has an outer tube 60 and an inner tube 160 sheathed in the outer tube 60.
  • the inner end 65 of the outer tube 60 close to the housing 20 is connected to the outer wall 26 of the housing.
  • the outer tube 60 has a mounting flange 62 formed thereon and a nozzle 64 opening at the suction port 22 of the housing 20.
  • the inner end 65 of the outer tube 60 is mounted on the outer wall 26 of the housing 20 at the nozzle 64 through the mounting flange 62.
  • the inner tube 160 is a separate tube installed in the outer tube 60, and the separate tube extends from the outer tube 60 through the nozzle 64.
  • the inner tube 160 is installed into the outer tube 60 by interference fit.
  • the inner tube 160 is installed into the outer tube 60 by welding, threaded connection, or other suitable methods.
  • one end of the inner tube 160 that is, the outer end, extends in the outer tube 60, and the other end of the inner tube 160 that is opposite to the one end, that is, the inner end, extends beyond the shell.
  • the suction port 22 enters the housing 20, whereby the inner end 166 of the inner tube 160 that extends inwardly beyond the suction port 22 can be used as an oil blocking member.
  • the outer tube 60 is further provided with an inner convex portion 63 and the middle portion 162 of the inner tube 160 located between the outer end portion and the inner end portion is connected to the inner convex portion 63.
  • the inner tube 160 and the outer tube 60 are connected to each other via the inner convex portion 63.
  • the inner end 166 has a straight tube shape.
  • the oil blocking member according to this embodiment is installed at the inner end of the inner tube in the outer tube of the fluid suction fitting by interference fit. This configuration simplifies the manufacture of the compressor and can be unchanged or only slightly changed.
  • the structure of the fluid suction fittings of the compressor is applied to existing compressors, which has unique adaptability.
  • the fluid suction pipe 60A of the fluid suction fitting has a mounting flange 62A formed thereon, and an outer end located outside the housing and an inner end located inside the housing.
  • the end of the fluid suction pipe 60A inside the housing directly extends into the housing 20 via the suction port 22 of the housing 20, so that the inner end 66A of the fluid suction pipe 60A extending into the housing 20 can be used as a stopper.
  • the inner end 66A has a straight tube shape.
  • the fluid suction pipe 60A is installed on the housing 20 by interference fit, welding, screw connection or other suitable methods after extending into the housing 20.
  • welding may be performed at the mounting flange 62A, while in the case of other methods, the mounting flange 62A may abut against the outer wall of the housing to play a role of positioning.
  • the inner end portions 166 and 66A may have any shape suitable for isolating the oil on the inner wall of the housing 20 and are not limited to the straight pipe shape shown in FIGS. 2 and 3.
  • the oil blocking member is a straight tube, in addition to effectively separating the oil on the inner wall of the housing from the sucked working fluid, the fluid supply and the cooling of the motor can also be realized at the same time.
  • the oil blocking member of the compressor according to a modification of the second embodiment of the present disclosure is described below with reference to FIG. 4. For clarity, only the differences from FIG. 3 are described, and similar components and features are described. The detailed description will not be given.
  • the end of the fluid suction pipe 60B of the fluid suction fitting of the compressor according to this modification example inside the casing passes through the suction port 22 of the casing 20 It extends directly into the casing 20, and the inner end 66B extending into the casing 20 is designed to be bent upward in the axial direction in the casing 20.
  • the inner end 66B has a curved upper half 661B and a curved lower half 662B that are bent upward in the axial direction.
  • the curved lower half 662B extends more inwardly than the curved upper half 661B, and the area of the curved lower half 662B is larger than the area of the curved upper half 661B.
  • the structure of the inner end portion 66B that is bent upward in the axial direction is not limited to this, as long as the structure of the inner end portion 66B is suitable for effectively isolating the oil on the inner wall of the housing from the working fluid sucked into the housing and can effectively isolate the working fluid. Just guide upwards.
  • the design of the oil retaining member that is bent upward in the axial direction can effectively separate the oil on the inner wall of the housing from the sucked working fluid, and it can also direct the working fluid to the upper part of the compressor, such as the compression mechanism. Avoid mixing the intake air with the oil flow at other locations in the housing, thereby further reducing the oil circulation rate.
  • the oil blocking member of the compressor according to another modification of the second embodiment of the present disclosure is described below with reference to FIG. 5. For clarity, only the differences from FIG. 3 are described, and similar components and The characteristics will not be described in detail.
  • the end of the fluid suction pipe 60C of the fluid suction fitting of the compressor according to this modification example inside the casing passes through the suction port 22 of the casing 20 It extends directly into the housing 20, and the inner end 66C extending into the housing 20 is designed to be axially bent downward in the housing 20.
  • the inner end 66C has a curved upper half 661C and a curved lower half 662C that are axially bent downward.
  • the curved upper half 661C extends more inwardly than the curved lower half 662C, and the area of the curved upper half 661C is larger than the area of the curved lower half 662C.
  • the structure of the inner end 66C that is bent downward in the axial direction is not limited to this, as long as the structure of the inner end 66C is suitable for effectively isolating the oil on the inner wall of the housing from the working fluid sucked into the housing and can effectively isolate the working fluid. The fluid can be directed downwards.
  • the design of the oil baffle member that is bent downward in the axial direction can effectively separate the oil on the inner wall of the housing from the sucked working fluid, and it can also direct the working fluid to the lower part of the compressor, such as the drive mechanism (motor). Wait for further guidance, so as to further improve the cooling of the motor.
  • the axial upward/downward bending structure in the oil blocking member of the compressor according to the above-mentioned modification of the second embodiment can also be applied to the oil blocking member in the first embodiment, that is, inserting fluid
  • the inner end of the separate tube (inner tube) of the outer tube of the suction fitting that extends into the housing can also be bent upward/downward in the axial direction.
  • the term "bend axially upwards" means that the inner end of the inner tube faces the compressor in the axial direction of the compressor (up and down direction as shown in the figure) after extending into the inside of the casing.
  • the axial upward bending here does not limit the inner end of the inner tube must be bent upward so that its extending direction is parallel to the axial direction of the compressor.
  • the term "bend axially downward” means that the inner end portion is bent toward the bottom of the compressor in the axial direction of the compressor (up and down direction as shown in the figure) after extending into the inside of the casing.
  • the axial downward bending here does not limit the inner end of the inner tube to be bent downward so that its extending direction is parallel to the axial direction of the compressor.
  • the compressor according to this example also has, for example, provided in the main bearing housing 50 on the suction shield 120.
  • the suction shield 120 is installed to face the inner end for guiding the working fluid sucked into the housing via the fluid suction fitting.
  • the suction shield 120 is fixedly mounted on the main bearing housing 50. In other examples, the suction shield 120 is fixed to the housing 20 by welding.
  • the specific shape and structure of the suction shield 120 are designed so that as long as the working fluid sucked into the housing 20 via the fluid suction fitting can be effectively guided upward and/or downward, and can be suitable for installation to the compressor Parts can be.
  • the inner end 66A of the fluid suction pipe 60A extending into the housing 20 via the suction port of the housing 20 is used as an oil blocking member in cooperation with the suction shield 120 to guide the working fluid upward and downward.
  • the distribution ratio of the upward and downward directions of the working fluid can be balanced, so that the working fluid can be guided to the upper part of the compressor, such as the compression mechanism, and the working fluid can be guided to the lower part of the compressor, such as the motor, at the same time. Control oil circulation rate and motor temperature.
  • the oil blocking member cooperates with the suction shield to direct the working fluid only upward or downward.
  • the oil blocking member may also have other configurations suitable for mating with the suction shield 120, such as the inner end of a separate tube (inner tube) inserted into the outer tube of the fluid suction fitting and extending into the housing. Department.
  • the oil blocking member itself is not a straight tube but is slightly curved, it can also be used in conjunction with the suction shield 120.
  • the oil blocking member of the compressor is an inward protrusion provided at a portion of the inner wall of the housing around the suction port of the housing.
  • the inward protrusion is a complete ring structure provided around the suction port or a partial ring structure provided only above the suction port.
  • the inwardly protruding portion in a completely annular structure is more conducive to isolating the oil on the inner wall of the housing and the incoming fluid, while the inwardly protruding portion in a partially annular structure has a simpler structure and is due to the inner wall of the housing.
  • the upper oil mainly flows from top to bottom, so this structure can still effectively control the contact and mixing of the fluid with the oil on the inner wall of the housing.
  • annular cylinder 201 (serving as an oil blocking member according to the present disclosure) is provided around the suction port 22 on the inner wall of the housing 20, and the annular cylinder 201 is provided at the edge of the suction port 22.
  • the annular cylinder 201 and the suction port 22 of the housing 20 have substantially the same central axis.
  • the left end of the annular cylinder 201 is attached to the housing 20, and the right end extends into the housing 20.
  • the annular cylinder 201 is welded to the inner surface (inner wall) of the housing 20. Welding the annular cylinder 201 to the inner surface of the housing 20 will not increase the investment cost of assembly.
  • annular cylinder 201 is not limited to a straight tubular shape.
  • the annular cylinder may also have other shapes and structures suitable for isolating the oil on the inner wall of the housing.
  • the annular cylinder may be axially bent upward or axially downward. .
  • the inner wall of the housing 20 is provided with an annular bulge 202 formed by protruding a portion of the housing 22 adjacent to the suction port 22 inwardly (used to be used according to the present disclosure) around the suction port 22
  • the oil retaining member Preferably, the annular bulge 202 is protruded inwardly by stamping.
  • the annular protruding portion 202 may protrude inward to a length suitable for isolating the oil on the inner wall of the housing.
  • the method of forming a bulge on the inner wall of the casing to be used as an oil blocking member does not increase the assembly line welding station, and makes the structure of the compressor simpler and easier to manufacture.
  • a portion of the casing 20 located around the suction port 22 is provided with a folded portion 203 (with As an oil retaining member according to the present disclosure).
  • the part defining the suction port 22 is bent inward to form a folded portion to be used as an oil blocking member without increasing the number of parts or increasing the cost of the compressor and is easy to manufacture (for example, because the suction port can be formed together with the folded portion. Folded part, so easy to manufacture).
  • the folded portion 203 is not limited to a structure extending perpendicular to the housing, and the folded portion 203 may also have other shapes and structures suitable for isolating the oil on the inner wall of the housing.
  • the folded portion may be connected to the housing.
  • the inner surface is bent upwards or downwards at an angle.
  • the oil blocking member in the above-mentioned embodiment described in FIGS. 7 to 9 can make the structure of the fluid suction fitting not become complicated compared with the oil blocking member described in the first embodiment and the second embodiment, and therefore It is easier to assemble and manufacture.
  • the oil blocking member shown in FIGS. 2 to 9 is positioned close to the main bearing seat, it should be understood that it depends on the needs of the location of the fluid suction fittings in the compressor in different applications, according to The oil blocking member of the compressor of the present disclosure may be located at any position on the casing of the compressor, in other words, the oil blocking member is in the axial direction of the compressor (up and down directions as shown in FIGS. 1 to 9) and The position in the radial direction (the left-right direction as shown in FIGS. 1 to 9) is not limited.
  • the position of the suction port and the oil blocking member of the housing and the position of the fluid inlet of the compression mechanism are positioned to be offset in the axial direction.
  • the housing The suction port of the body and the oil blocking member are positioned downward in the axial direction (for example, near the main bearing seat). This configuration can facilitate both controlling the oil circulation rate and controlling the motor temperature.
  • the extension length of the oil blocking member in the housing is about 1 mm to 10 mm. In a preferred example, the extension length of the oil blocking member in the housing is about 3 mm to 8 mm. In a further preferred example, the extension length of the oil blocking member in the housing is approximately 5 mm to 6 mm. The inventor found that when the extension length of the oil retaining member in the housing is within these ranges, on the one hand, the fluid can be effectively isolated from the oil on the inner wall of the housing, and on the other hand, the extension length will not be too long. This leads to inconvenience in processing and occupies too much space inside the housing.
  • the oil on the inner wall of the housing can be effectively separated from the working fluid sucked in from the fluid suction fitting by forming the oil blocking member inside the housing , Thereby effectively reducing the oil circulation rate, especially for scroll compressors with large scroll displacement, high motor speed, and more oil injection, which are likely to cause more oil to be thrown or splashed on the inner wall of the compressor shell In terms of.
  • the oil circulation rate when the compressor is equipped with an oil retaining member is significantly lower than that without an oil retaining member.
  • the oil circulation rate in the case of the component For example, the oil circulation rate in the case where the compressor is provided with the oil blocking member is 2.86%, and the oil circulation rate in the case where the oil blocking member is not provided is 4.01%.
  • the present disclosure is not limited to the embodiments described above, but allows various possible modifications.
  • the compressor shown in the figure is a low-pressure side scroll compressor, those skilled in the art should understand that the present disclosure can also be applied to other types of compressors.

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Abstract

一种压缩机，包括：壳体（20），该壳体（20）具有吸入口（22）、壳体内壁（27）和壳体外壁（26）；压缩机构，该压缩机构用于对工作流体进行压缩；驱动机构，该驱动机构用于驱动压缩机构；流体吸入配件，该流体吸入配件设置在壳体（20）的吸入口（22）处以与壳体内部流体连通；压缩机在壳体（20）的内侧设置有用于将经由流体吸入配件吸入壳体内部的工作流体与壳体内壁（27）上的油隔离开的挡油构件，该挡油构件包括设置在壳体内壁（27）的位于吸入口（22）周围的向内突起部，并且/或者，流体吸入配件包括外管（60）和套设在外管（60）内的内管（160），内管（160）包括延伸超出吸入口（22）的内端部（166），挡油构件由内端部（166）构成。通过设置挡油构件可以有效降低油循环率并消除压缩机因缺油而失效等可靠性问题。

Description

压缩机
本申请要求以下中国专利申请的优先权：于2020年2月21日提交中国专利局的申请号为202020196858.0、发明创造名称为“压缩机”的中国专利申请。该专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种压缩机，尤其涉及一种能够将吸入壳体的工作流体与壳体内壁上的油进行有效分离的压缩机。
背景技术
压缩机(比如涡旋压缩机)可以应用于例如制冷系统、空调系统和热泵系统中。涡旋压缩机包括用于压缩工作流体(比如制冷剂)的压缩机构，压缩机构进而包括动涡旋部件和定涡旋部件。压缩机构由马达通过旋转轴来驱动以进行对流体的压缩。涡旋压缩机在工作过程中，需要足够的润滑油来实现轴承的润滑、动涡旋部件和定涡旋部件的密封、润滑及冷却。通常，可以用油循环率来表征被工作流体携带的润滑油的多少。过大的油循环率会降低系统的换热效率，同时也会造成压缩机由于缺油而失效等可靠性问题。
涡旋压缩机的容积式油泵在高转速运行下会泵出更多的油，且在高速旋转下产生的离心力也会很大，这会使大量的油被甩到或飞溅到压缩机的壳体的内壁上，由此导致甩到壳体内壁上的油与经由流体吸入配件吸入到壳体中的工作流体混合，从而被带出压缩机，进而造成大的油循环率。传统上也采用了一些降低油循环率的方式来分离壳体内壁上的油和经由流体吸入配件吸入壳体中的工作流体，但分离效果有限。
因此，在本领域中，特别地在因大涡旋排量、高马达转速以及更多注油量而易于引起大油循环率的压缩机中，期望提供一种能够以更加简单且更低成本的方式来有效降低油循环率以及降低马达温度的技术。
这里，应当指出的是，本部分中所提供的技术内容旨在有助于本领域技术人员对本公开的理解，而不一定构成现有技术。
发明内容
在本部分中提供本公开的总概要，而不是本公开完全范围或本公开所有特征的全面公开。
本公开的一个目的是提供一种能够将吸入壳体的工作流体与壳体的内壁上的油进行有效分离进而有效地降低油循环率的压缩机。
本公开的另一目的是提供一种能够在将吸入壳体的工作流体与壳体的内壁上的油隔离的同时将工作流体向压缩机的上部构件引导以进一步降低油循环率的压缩机。
本公开的另一目的是提供一种能够在将吸入壳体的工作流体与壳体的内壁上的油隔离的同时将工作流体向压缩机的下部构件引导以进一步降低马达温度的压缩机。
本公开的另一目的是提供一种结构简单、更加易于组装以及制造的压缩机。
为了实现上述目的中的一个或多个，根据本公开的一个方面，提供一种压缩机，所述压缩机包括：壳体，所述壳体具有吸入口、壳体内壁和壳体外壁；压缩机构，所述压缩机构用于对工作流体进行压缩；驱动机构，所述驱动机构用于驱动所述压缩机构；流体吸入配件，所述流体吸入配件设置在所述壳体的吸入口处以与所述壳体内部流体连通。所述压缩机在所述壳体的内侧设置有用于将经由所述流体吸入配件吸入所述壳体内部的工作流体与所述壳体内壁上的油隔离开的挡油构件，所述挡油构件包括设置在所述壳体内壁的位于所述吸入口周围的向内突起部，并且/或者，所述流体吸入配件包括外管和套设在所述外管内的内管，所述内管包括延伸超出所述吸入口的内端部，所述挡油构件由所述内端部构成。
在根据本公开的压缩机中，在所述挡油构件由所述内端部构成的情况下，所述外管的内端部连接至所述壳体外壁，并且/或者，所述外管设置有内凸部并且所述内管与所述外管经由所述内凸部相互连接。
在根据本公开的压缩机中，在所述挡油构件由所述内端部构成的情况下，所述内管的内端部为直管状、沿所述压缩机的轴向方向向上弯曲或者沿所述压缩机的轴向方向向下弯曲。
在根据本公开的压缩机中，在所述挡油构件由所述内端部构成的情况下， 所述压缩机还设置有面对所述内端部的用于对经由所述流体吸入配件吸入所述壳体内部的工作流体进行引导的吸气遮挡件。
在根据本公开的压缩机中，在所述挡油构件包括所述向内突起部的情况下，所述向内突起部为围绕所述吸入口设置的完全环形结构或者为仅设置在所述吸入口的上方的部分环形结构。
在根据本公开的压缩机中，在所述挡油构件包括所述向内突起部的情况下，所述向内突起部为：连接至所述壳体内壁的环形筒、通过使所述壳体的邻近所述吸入口的部分向内突出而形成的环形隆起部、或通过使所述壳体的限定所述吸入口的部分向内弯折而形成的翻折部。
在根据本公开的压缩机中，所述吸入口和所述挡油构件的位置与所述压缩机构的流体入口的位置定位成在压缩机的轴向方向上错开。
在根据本公开的压缩机中，所述挡油构件在所述壳体中的延伸长度为1mm至10mm。
在根据本公开的压缩机中，所述挡油构件在所述壳体中的延伸长度为5mm至6mm。
在根据本公开的压缩机中，所述压缩机为低压侧涡旋压缩机。
根据本公开的一个或多个实施方式，通过在壳体的内侧设置有挡油构件，使得经由流体吸入配件吸入的工作流体能够在流入壳体内时流动经过挡油构件，从而能够将在压缩机的运转过程中甩出和飞溅到压缩机的壳体的内壁上的润滑油与经由流体吸入配件吸入到壳体中的工作流体有效地分离，因此可以有效地降低油循环率进而确保系统的换热效率并消除压缩机因缺油而失效等可靠性问题。另外，通过将挡油构件设计成轴向向上弯曲/轴向向下弯曲/与吸气遮挡件配合等构型，除了可以有效分离壳体内壁上的油与吸入的工作流体之外，还可以将工作流体向压缩机的上部构件比如压缩机构等引导以进一步降低油循环率、或者向压缩机的下部构件比如驱动机构等引导以降低马达的温度、或者向压缩机的上部构件和下部构件引导以平衡工作流体向上引导和向下引导的分配比例而同时降低油循环率和马达温度。另外，通过在壳体上形成挡油构件，使得压缩机的流体吸入配件的结构不会变得复杂化，因此更加易于组装以及制造。
附图说明
通过以下参照附图的描述，本公开的一个或多个实施方式的特征和优点将变得更加容易理解。在附图中：
图1示出了根据相关技术的压缩机的纵向剖视图。
图2示出了根据本公开的第一实施方式的压缩机的示意性局部剖视图，其中挡油构件为流体吸入配件的内管的内端部。
图3示出了根据本公开的第二实施方式的压缩机的示意性局部剖视图，其中挡油构件为流体吸入管延伸到压缩机的壳体中的内端部。
图4示出了根据本公开的第二实施方式的一个变型例的压缩机的示意性局部剖视图，其中挡油构件设计成轴向向上弯曲。
图5示出了根据本公开的第二实施方式的另一变型例的压缩机的示意性局部剖视图，其中挡油构件设计成轴向向下弯曲。
图6示出了根据本公开的第二实施方式的压缩机的挡油构件与吸气遮挡件配合的示意性局部剖视图。
图7示出了根据本公开的第三实施方式的压缩机的示意性局部剖视图，其中，挡油构件为连接至壳体内壁的环形筒。
图8示出了根据本公开的第三实施方式的一个变型例的压缩机的示意性局部剖视图，其中，挡油构件为形成在壳体上的环形隆起部。
图9示出了根据本公开的第三实施方式的另一变型例的压缩机的示意性局部剖视图，其中，挡油构件为由壳体的限定吸入口的部分向内弯折而形成的翻折部。
在附图中，相同的或对应的技术特征或部件采用相同或对应的附图标记来表示。
具体实施方式
下面参照附图、借助示例性实施方式对本公开进行详细描述。对本公开的以下详细描述仅仅是出于说明目的，而绝不是对本公开及其应用或用途的限制。
首先，将参照图1来描述根据相关技术的压缩机的总体构造和运行原理(图1是根据相关技术的压缩机的纵向剖视图)。
如图1所示，压缩机10’(在本文中以低压侧涡旋压缩机为示例)包括壳体20’、驱动机构30’、压缩机构40’、主轴承座50’、流体吸入管(流体吸入配件)60’以及流体排出管70’等。壳体20’可以容置驱动机构30’、压缩机构40’和主轴承座50’。流体吸入管60’设置在壳体20’的低压侧用于吸入工作流体(比如制冷剂)，而流体排出管70’设置在壳体20’的高压侧用于排出压缩后的流体。流体吸入管60’可以在壳体20’的吸入口22’处通过安装凸缘62’附接至壳体20’并与壳体20’的内部流体连通。流体吸入管60’还具有开口于壳体20’的吸入口22’处的管口64’，吸入的工作流体流动经过该管口64’进入壳体20’中。流体吸入管60’的管口64’与壳体20’的吸入口22’具有大致相同的中心轴线。
驱动机构30’包括马达和旋转轴32’。马达可以包括定子33’和转子34’。定子33’可以固定至壳体20’。转子34’可以压配合至旋转轴32’，旋转轴32’可以由转子34’可旋转地驱动以驱动压缩机构40’。
压缩机构40’设置在壳体20’内以对从流体吸入管60’吸入的工作流体进行压缩然后将压缩后的流体从流体排出管70’排出压缩机10’。压缩机构40’通常包括定涡旋部件42’和动涡旋部件44’。驱动机构30’经由旋转轴32’驱动动涡旋部件44’，使得动涡旋部件44’相对于定涡旋部件42’进行平动转动。由此，在由动涡旋部件44’的螺旋叶片(未标示)与定涡旋部件42’的螺旋叶片(未标示)彼此接合而形成的一系列压缩腔在从径向外侧向径向内侧移动而体积逐渐减小时，对压缩腔中的制冷剂进行压缩。
压缩机10’还包括油池80’。油池80’可以设置在壳体20’的下端部处并且可以用于向压缩机10’的运动部件，例如压缩机构40’、驱动轴承、止推表面和主轴承，提供润滑油。在压缩机10’的运转过程中，供给到压缩机10’中的相关活动部件比如驱动轴承、止推表面和主轴承等上的润滑油被甩出和飞溅到压缩机的壳体20’的内壁上，壳体内壁上的这些润滑油在往下流(例如沿着内壁往下流)回油池80’时往往会与从流体吸入管60’吸入的工作流体(例如制冷剂)混合，随后这些混合有润滑油的工作流体被吸入到定涡旋部件42’与动涡旋部件44’之间的压缩腔中并最终被带出压缩机，由此造成了大的油循环，从而导致系统性能下降并且由于缺油而导致压缩机失效。
在相关技术中也采用了一些方式来降低油循环，其中一种方式为在压缩机 的主轴承座上一体地安装吸气遮挡件，在吸气遮挡件与壳体内壁之间留有间隙。该吸气遮挡件能够引导由流体吸入管吸入压缩机壳体内的工作流体的流向而避免与壳体内其它位置处的润滑油混合，然而经由流体吸入管吸入压缩机壳体内的工作流体却会易于与甩出到壳体内壁上的油混合，由此能够分离油的效果有限。另一种方式为通过增加新的冲压零件以及额外的焊接工艺来将吸气遮挡件焊接在壳体上。同样地，该吸气遮挡件能够引导由流体吸入管吸入压缩机壳体内的工作流体的流向而避免与壳体内其它位置处的润滑油混合，然而吸入压缩机壳体内的工作流体却会易于与壳体内壁上的油混合，由此分离油的效果同样有限，而且还引入了新的零件和额外的工艺，使安装制造复杂化。通过这两种方式来分离油和吸入的工作流体，都会使得大量油与工作流体混合并最终被带出压缩机，从而使系统的性能下降，也可能会使压缩机由于缺油而失效。
在本公开中，为了将在压缩机的运转过程中甩出和飞溅到压缩机的壳体的内壁上的润滑油与经由流体吸入管吸入到壳体中的工作流体有效分离，根据本公开的压缩机还设置有将在下文中进行描述的挡油构件。
下面将参照图2至图9来描述根据本公开的各实施方式的压缩机的挡油构件。此处需要说明的是，在图2至图9中和相关的说明中仅描述和示出了与本公开的技术方案密切相关的装置结构，而省略了与本公开的技术内容关系不大的且本领域技术人员已知的其他细节。根据本公开的压缩机在壳体20的内侧设置有用于将经由流体吸入配件吸入壳体的内部的流体与壳体内壁上的油隔离开的挡油构件。
首先，参照图2来描述根据本公开的第一实施方式的压缩机的挡油构件。如图2所示，压缩机的壳体20具有吸入口22、壳体外壁26和壳体内壁27。流体吸入配件具有外管60和套设在外管60内的内管160，外管60的靠近壳体20的内端部65连接至壳体外壁26。外管60具有形成在其上的安装凸缘62以及开口于壳体20的吸入口22处的管口64。外管60的内端部65在管口64处通过安装凸缘62安装到壳体20的壳体外壁26上。在该实施方式中，内管160为安装在外管60中的一根单独的管，该单独的管从外管60中延伸穿过管口64。在优选的示例中，内管160通过过盈配合安装到外管60中。在其他示例中，内管160通过焊接、螺纹连接、或其他合适的方式安装到外管60中。在该实施方式中，内管160的一个端部、即外端部在外管60中延伸，而内管 160的与所述一个端部相反的另一端部、即内端部延伸超出壳体的吸入口22进入到壳体20中，由此内管160的向内延伸超出吸入口22的内端部166可以用作挡油构件。在该实施方式中，外管60还设置有内凸部63并且内管160的位于外端部与内端部之间的中间部162连接至该内凸部63。也就是说，内管160与外管60经由内凸部63相互连接。在该实施方式中，内端部166为直管状。根据该实施方式的挡油构件是通过过盈配合安装在流体吸入配件的外管中的内管的内端部，该构型简化了压缩机的制造并且可以在不改变或者仅稍微改变现有压缩机的流体吸入配件的结构的情况下应用于现有压缩机，具有独特的适应性。
下面参照图3来描述根据本公开的第二实施方式的压缩机的挡油构件，为了清楚起见，其中仅对与图2的不同之处进行描述，而对类似的部件和特征将不再进行详细描述。如图3所示，在该实施方式中，流体吸入配件的流体吸入管60A具有形成在其上的安装凸缘62A以及位于壳体外侧的外端部和位于壳体内侧的内端部。流体吸入管60A的在壳体内侧的端部经由壳体20的吸入口22直接延伸到壳体20中，由此流体吸入管60A的延伸到壳体20中的内端部66A可以用作挡油构件。在该实施方式中，内端部66A为直管状。在优选的示例中，流体吸入管60A在延伸到壳体20中之后通过过盈配合、焊接、螺纹连接或其他合适的方式安装到壳体20上。在焊接的情况下，可以在安装凸缘62A处实施焊接，而在其他方式的情况下，安装凸缘62A可以抵接壳体外壁从而起到定位的作用。通过将流体吸入管60A的直接延伸到壳体20中的内端部作为挡油构件，无需引入新的部件来进行挡油，也无需增加额外的安装步骤，从而简化了压缩机的结构及其制造。
应当理解的是，内端部166和66A可以为适于隔离壳体20的内壁上的油的任何形状，而不限于图2和图3所示的直管形状。在挡油构件为直管状的情况下，除了可以有效分离壳体内壁上的油与吸入的工作流体之外，还可以同时实现流体的供应和马达的冷却。
下面参照图4来描述根据本公开的第二实施方式的一个变型例的压缩机的挡油构件，为了清楚起见，其中仅对与图3的不同之处进行描述，而对类似的部件和特征将不再进行详细描述。如图4所示，与在第二实施方式中所描述的一样，根据该变型例的压缩机的流体吸入配件的流体吸入管60B的在壳体 内侧的端部经由壳体20的吸入口22直接延伸到壳体20中，延伸到壳体20中的内端部66B在壳体20中设计为轴向向上弯曲。内端部66B具有轴向向上弯曲的弯曲上半部661B和弯曲下半部662B。在优选的示例中，弯曲下半部662B比弯曲上半部661B伸入得更向内，并且弯曲下半部662B的面积比弯曲上半部661B的面积更大。应当理解的是，轴向向上弯曲的内端部66B的结构不限于此，只要内端部66B的结构适于将壳体内壁上的油与吸入壳体的工作流体有效隔离且能够将工作流体向上引导即可。挡油构件的这种轴向向上弯曲的设计，除了可以有效分离壳体内壁上的油与吸入的工作流体之外，还可以将工作流体向压缩机的上部构件，比如压缩机构等进一步引导以避免进气与壳体内其它位置处的油流混合，从而进一步降低油循环率。
下面参照图5来描述根据本公开的第二实施方式的另一变型例的压缩机的挡油构件，为了清楚起见，其中仅对与图3的不同之处进行描述，而对类似的部件和特征将不再进行详细描述。如图5所示，与在第二实施方式中所描述的一样，根据该变型例的压缩机的流体吸入配件的流体吸入管60C的在壳体内侧的端部经由壳体20的吸入口22直接延伸到壳体20中，延伸到壳体20中的内端部66C在壳体20中设计为轴向向下弯曲。内端部66C具有轴向向下弯曲的弯曲上半部661C和弯曲下半部662C。在优选的示例中，弯曲上半部661C比弯曲下半部662C伸入得更向内，并且弯曲上半部661C的面积比弯曲下半部662C的面积更大。应当理解的是，轴向向下弯曲的内端部66C的结构不限于此，只要内端部66C的结构适于将壳体内壁上的油与吸入壳体的工作流体有效隔离且能够将工作流体向下引导即可。挡油构件的这种轴向向下弯曲的设计，除了可以有效分离壳体内壁上的油与吸入的工作流体之外，还可以将工作流体向压缩机的下部构件，比如驱动机构(马达)等进一步引导，从而进一步提高马达的冷却。
应当理解的是，根据第二实施方式的上述变型例的压缩机的挡油构件中的轴向向上/向下弯曲结构，也可以适用于第一实施方式中的挡油构件，即，插入流体吸入配件的外管中的单独的管(内管)的延伸到壳体中的内端部也可以轴向向上/向下弯曲。此处作如下补充解释，术语“轴向向上弯曲”指的是内管的内端部在伸入壳体内部后在压缩机的轴向方向(如图所示的上下方向)上朝向压缩机的顶部弯曲，这里的轴向向上弯曲并没有限定内管的内端部一定要 向上弯曲成其延伸方向与压缩机的轴向方向平行。术语“轴向向下弯曲”指的是内端部在伸入壳体内部后在压缩机的轴向方向(如图所示的上下方向)上朝向压缩机的底部弯曲。同理，这里的轴向向下弯曲并没有限定内管的内端部一定要向下弯曲成其延伸方向与压缩机的轴向方向平行。
当然，特别地，在挡油构件为直管状(如图2和图3所示)的情况下，也可以实现工作流体的向上及向下的引导。如图6所示(图6示出了根据第二实施方式的压缩机的挡油构件与吸气遮挡件配合的示意性局部剖视图)，根据该示例的压缩机还具有例如设置在主轴承座50上的吸气遮挡件120。吸气遮挡件120安装成面对内端部用于对经由流体吸入配件吸入壳体内部的工作流体进行引导。在一些示例中，吸气遮挡件120固定地安装在主轴承座50上。在其他示例中，吸气遮挡件120通过焊接固定在壳体20上。吸气遮挡件120的具体形状和结构设计成使得只要能够有效地将经由流体吸入配件吸入到壳体20内的工作流体向上引导和/或向下引导、并且能够适于安装至压缩机的相关部件即可。在该示例中，流体吸入管60A的经由壳体20的吸入口延伸到壳体20中的内端部66A作为挡油构件与吸气遮挡件120配合使用以将工作流体向上引导和向下引导，这样可以平衡工作流体向上引导和向下引导的分配比例，使得既能够将工作流体向压缩机的上部构件比如压缩机构引导又能够将工作流体向压缩机的下部构件比如马达引导，起到同时控制油循环率和马达温度的作用。在其他示例中，挡油构件与吸气遮挡件配合以将工作流体仅向上或仅向下引导。应当理解的是，挡油构件也可以具有适合与吸气遮挡件120配合的其他构型，比如插入流体吸入配件的外管中的单独的管(内管)的延伸到壳体中的内端部。另外，还可以构想的是，在挡油构件本身不是直管状而是稍微弯曲的情况下，也可以与吸气遮挡件120配合使用。
下面参照图7至图9来描述根据本公开的第三实施方式的压缩机的挡油构件及其各种变型，为了清楚起见，其中仅对与上述实施方式的不同之处进行描述，而对类似的部件和特征将不再进行详细描述。在图7至图9所示的实施方式中，挡油构件为设置在壳体内壁的位于壳体的吸入口周围的部分处的向内突起部。向内突起部为围绕吸入口设置的完全环形结构或者为仅设置在吸入口的上方的部分环形结构。应当理解的是，呈完全环形结构的向内突出部更有利于隔离壳体内壁上的油和进入的流体，而呈部分环形结构的向内突出部则具有更 简单的结构同时由于壳体内壁上的油主要从上往下流因此这种结构仍可以较为有效地控制流体与壳体内壁上的油的接触及混合。
在图7所示的示例中，在壳体20的内壁上围绕吸入口22设置环形筒201(用作根据本公开的挡油构件)，环形筒201设置在吸入口22的边缘处。环形筒201与壳体20的吸入口22具有大致相同的中心轴线。环形筒201的左侧端部附接至壳体20，而右侧端部延伸到壳体20中。在优选的示例中，环形筒201焊接至壳体20的内表面(内壁)。将环形筒201焊接至壳体20的内表面将不会增加组装的投入成本。应当理解的是，环形筒201不限于直管状的，环形筒也可以是适于隔离壳体内壁上的油的其他形状及构造，例如，环形筒可以为轴向向上弯曲或轴向向下弯曲。
在图8所示的示例中，在壳体20的内壁上围绕吸入口22设置有通过使壳体22的邻近吸入口22的部分向内突出而形成的环形隆起部202(用作根据本公开的挡油构件)。优选地，环形隆起部202通过冲压而向内突出。环形隆起部202向内突出到适于隔离壳体内壁上的油的长度即可。在壳体内壁上形成隆起部而用作挡油构件的这种方式不会增加组装线焊接站，使得压缩机的结构更简单且更易于制造。
在图9所示的示例中，在壳体20的位于吸入口22的周围的部分处设置有通过使壳体20的限定吸入口22的部分向内弯折而形成的翻折部203(用作根据本公开的挡油构件)。将限定吸入口22的部分向内弯折形成翻折部来用作挡油构件不会增加部件数量也不会增加压缩机的成本并且易于制造(例如，由于可以在形成吸入口时一同形成翻折部，因此易于制造)。应当理解的是，翻折部203不限于垂直于壳体延伸的结构，翻折部203也可以是适于隔离壳体内壁上的油的其他形状及结构，例如，翻折部可以与壳体的内表面成一定角度向上或向下弯折。
在图7至图9中描述的上述实施方式中的挡油构件相比于第一实施方式和第二实施方式中描述的挡油构件能够使得流体吸入配件的结构不会变得复杂化，因此更加易于组装以及制造。
虽然在图2至图9中示出的挡油构件定位在靠近主轴承座的位置处，但应当理解的是，取决于压缩机中流体吸入配件在不同的应用中的设置位置的需要，根据本公开的压缩机的挡油构件可以位于压缩机的壳体上的任何位置处， 换句话说，挡油构件在压缩机的轴向方向(如图1至图9所示的上下方向)和径向方向(如图1至图9所示的左右方向)上的位置不受限制。挡油构件在壳体中的延伸长度也没有任何限制，只要能够将壳体内壁上的油与吸入的工作流体有效分离并且在尺寸上能够与压缩机内部的各部件适配即可。然而，在一些示例中，壳体的吸入口和挡油构件的位置与压缩机构的流体入口的位置定位成在轴向方向上错开，特别地，与压缩机构的流体入口的位置相比，壳体的吸入口和挡油构件的位置定位成在轴向方向上靠下(例如靠近主轴承座的位置处)，这种构型可以便于兼顾控制油循环率和控制马达温度。另外，在一些示例中，挡油构件在壳体中的延伸长度为大约1mm至10mm。在优选的示例中，挡油构件在壳体中的延伸长度为大约3mm至8mm。在进一步优选的示例中，挡油构件在壳体中的延伸长度大约为5mm至6mm。发明人发现，当挡油构件在壳体中的延伸长度处于上述这些范围时，一方面，可以有效地使流体与壳体内壁上的油隔离，另一方面，也不至于使延伸长度过长而导致加工不便和占据过多壳体内部的空间。
通过如上所述的挡油构件，在压缩机的操作期间，当壳体的内壁上的油往下流动经过挡油构件时，油围绕挡油构件的外表面顺着壳体内壁流回油池中，从而避免或减少了壳体内壁上的油与从流体吸入配件吸入的工作流体的混合。相比于根据相关技术的通过吸气遮挡件分离油与工作流体的方式，通过在壳体内侧形成挡油构件能够有效地将壳体内壁上的油与从流体吸入配件吸入的工作流体进行隔离，进而有效地降低油循环率，特别是对于大涡旋排量、高马达转速以及更多注油量而易于引起更多油被甩到或飞溅到压缩机的壳体内壁上的涡旋压缩机而言。
通过实验，对于某一型号的涡旋压缩机，在其他条件(比如工况、转速)相同的情况下，在压缩机设置有挡油构件的情况下的油循环率明显低于没有设置挡油构件的情况下的油循环率。例如，在压缩机设置有挡油构件的情况下的油循环率为2.86％，而在没有设置挡油构件的情况下的油循环率为4.01％。
本公开并不局限于如上所述的实施方式，而是容许各种可能的变型。例如，尽管图中所示的压缩机为低压侧涡旋压缩机，然而本领域技术人员应当理解本公开也可以应用于其它类型的压缩机。
在本申请文件中，术语“上”、“下”、“左”和“右”等方位术语的使用仅 仅出于便于描述的目的，而不应视为是限制性的。此外，虽然已经参照示例性实施方式对本公开进行了描述，但是应当理解，本公开并不局限于文中详细描述和示出的具体实施方式/示例，在不偏离权利要求书所限定的范围的情况下，本领域技术人员可以对示例性实施方式做出各种改变。

Claims (10)

  1. 一种压缩机，包括：
    壳体，所述壳体具有吸入口、壳体内壁和壳体外壁；
    压缩机构，所述压缩机构用于对工作流体进行压缩；
    驱动机构，所述驱动机构用于驱动所述压缩机构；
    流体吸入配件，所述流体吸入配件设置在所述壳体的吸入口处以与所述壳体内部流体连通，
    其特征在于，所述压缩机在所述壳体的内侧设置有用于将经由所述流体吸入配件吸入所述壳体内部的工作流体与所述壳体内壁上的油隔离开的挡油构件，
    所述挡油构件包括设置在所述壳体内壁的位于所述吸入口周围的向内突起部，并且/或者，所述流体吸入配件包括外管和套设在所述外管内的内管，所述内管包括延伸超出所述吸入口的内端部，所述挡油构件由所述内端部构成。
  2. 根据权利要求1所述的压缩机，其特征在于，在所述挡油构件由所述内端部构成的情况下，所述外管的内端部连接至所述壳体外壁，并且/或者，所述外管设置有内凸部并且所述内管与所述外管经由所述内凸部相互连接。
  3. 根据权利要求1所述的压缩机，其特征在于，在所述挡油构件由所述内端部构成的情况下，所述内管的内端部为直管状、沿所述压缩机的轴向方向向上弯曲或者沿所述压缩机的轴向方向向下弯曲。
  4. 根据权利要求1所述的压缩机，其特征在于，在所述挡油构件由所述内端部构成的情况下，所述压缩机还设置有面对所述内端部的用于对经由所述流体吸入配件吸入所述壳体内部的工作流体进行引导的吸气遮挡件。
  5. 根据权利要求1所述的压缩机，其特征在于，在所述挡油构件包括所述向内突起部的情况下，所述向内突起部为围绕所述吸入口设置的完全环形结 构或者为仅设置在所述吸入口的上方的部分环形结构。
  6. 根据权利要求1所述的压缩机，其特征在于，在所述挡油构件包括所述向内突起部的情况下，所述向内突起部为：连接至所述壳体内壁的环形筒、通过使所述壳体的邻近所述吸入口的部分向内突出而形成的环形隆起部、或通过使所述壳体的限定所述吸入口的部分向内弯折而形成的翻折部。
  7. 根据权利要求1至6中任一项所述的压缩机，其特征在于，所述吸入口和所述挡油构件的位置与所述压缩机构的工作流体入口的位置定位成在所述压缩机的轴向方向上错开。
  8. 根据权利要求1至6中任一项所述的压缩机，其特征在于，所述挡油构件在所述壳体中的延伸长度为1mm至10mm。
  9. 根据权利要求1至6中任一项所述的压缩机，其特征在于，所述挡油构件在所述壳体中的延伸长度为5mm至6mm。
  10. 根据权利要求1至6中任一项所述的压缩机，其特征在于，所述压缩机为低压侧涡旋压缩机。
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JP6083173B2 (ja) * 2012-09-27 2017-02-22 株式会社富士通ゼネラル 空気調和装置及びそれに用いられる圧縮機
JP2015017521A (ja) * 2013-07-10 2015-01-29 日立アプライアンス株式会社 容積形圧縮機
CN203548230U (zh) * 2013-09-02 2014-04-16 合肥凌达压缩机有限公司 具有螺旋油分离器的旋转式压缩机
CN105443377A (zh) * 2014-06-10 2016-03-30 丹佛斯（天津）有限公司 涡旋压缩机

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