WO2019242721A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2019242721A1
WO2019242721A1 PCT/CN2019/092245 CN2019092245W WO2019242721A1 WO 2019242721 A1 WO2019242721 A1 WO 2019242721A1 CN 2019092245 W CN2019092245 W CN 2019092245W WO 2019242721 A1 WO2019242721 A1 WO 2019242721A1
Authority
WO
WIPO (PCT)
Prior art keywords
muffler
scroll
partition plate
scroll compressor
assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2019/092245
Other languages
English (en)
French (fr)
Inventor
魏圆圆
杨涛
江超
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Copeland Suzhou Co Ltd
Original Assignee
Emerson Climate Technologies Suzhou Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Emerson Climate Technologies Suzhou Co Ltd filed Critical Emerson Climate Technologies Suzhou Co Ltd
Priority to US17/254,835 priority Critical patent/US11846288B2/en
Priority to EP19822567.4A priority patent/EP3812590A4/en
Publication of WO2019242721A1 publication Critical patent/WO2019242721A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C29/06—Silencing
    • 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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • 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
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type

Definitions

  • the present disclosure relates to scroll equipment, and in particular to a scroll compressor with a muffler.
  • Compressor is a kind of fluid machinery that promotes low pressure gas to high pressure gas. It is the core equipment in refrigeration system.
  • Scroll compressor is a typical positive displacement compressor.
  • the main part of a scroll compressor is a scroll assembly, which is used to compress a fluid.
  • Scroll assemblies typically include fixed and orbiting vortexes that are nested on top of each other and, for example, cross slip rings that are coupled to the orbiting and orbiting vortexes respectively to prevent the orbiting vortex from spinning.
  • the fixed vortex and the movable vortex of the scroll assembly cooperate with each other in a stacked manner, wherein the movable vortex is eccentrically installed opposite to the fixed vortex.
  • the motor in the scroll compressor drives the crankshaft so that the orbiting scroll moves along a predetermined trajectory with respect to the fixed scroll, and a series of crescent-shaped compression spaces are formed between the orbiting scroll and the vortex profile of the fixed scroll.
  • the noise mainly comes from the noise of the compressed gas of the scroll assembly, the exhaust noise at the exhaust port of the scroll assembly, and the noise at the exhaust port of the scroll assembly. Vibration and flapping noise of reed valves.
  • Various methods have been proposed for isolating or reducing the working noise of the compressor, for example, improving the structural design of the compressor body, equipping the compressor with a soundproof cover, and arranging a muffler at the source of the noise.
  • a known way is to install a muffler on the scroll assembly, which can be used to eliminate exhaust noise and the like at the exhaust port of the scroll assembly.
  • a scroll compressor with a muffler is known.
  • the muffler used therein is generally a cup-shaped structure, and a plurality of muffler holes are formed in a side wall of the cup-shaped structure.
  • the muffler is fixedly installed on the inner part of the fixed scroll and located above the exhaust port of the fixed scroll, thereby reducing exhaust noise at the exhaust port.
  • the muffler used in the existing compressor is directly installed to the inner cymbal portion of the fixed scroll. Based on this structure, a more suitable way to fix the muffler is to use a screw connection.
  • the threaded connection requires that threads be formed on the circumferential wall of the inner condyle of the fixed scroll, so the inner condyle needs to have sufficient wall thickness to meet the requirements of the screw connection and structural strength at the same time. Therefore, it is difficult to apply such a muffler to a compressor having a thin inner wall portion of a fixed scroll.
  • the present disclosure looks forward to proposing a solution to this problem.
  • An object of the present disclosure is to provide a scroll compressor having an improved muffler device which is flexible in arrangement and has increased versatility and is applicable to various types of scroll assemblies.
  • Another object of the present disclosure is to provide a scroll compressor having an improved muffler device, which has a simplified structure, is easy to assemble, and has a dual function of muffling and isolating the high and low pressure chambers of the compressor.
  • a scroll compressor including: a scroll assembly having a movable scroll and a fixed scroll, each of which includes a movable scroll profile and Vortex lines are fixed and cooperate with each other to form a series of compression chambers, the scroll assembly defines an exhaust port; and a muffler, which is arranged above the scroll assembly and includes a partition plate and a muffler, and the partition plate is used for
  • the internal space of the scroll compressor is divided into a high pressure cavity and a low pressure cavity.
  • the partition plate has a central through hole, and the muffler is arranged above the exhaust port. The muffler is fixed to the central through hole and is independent of the scroll assembly.
  • the muffler is fixed to the partition plate instead of the scroll assembly, and is independent of the scroll assembly, so it does not affect the structure of the scroll assembly, and can be applied to various types of scroll assemblies; At the same time, the muffler is not only used to eliminate noise, but also uses the annular flange to seal and separate the high pressure chamber and the low pressure chamber of the compressor together with the partition plate.
  • the muffler is fixed to the central through hole and fixed to the partition plate by welding, interference fit or screw connection; or the partition plate further has a central flange portion extending upward from the periphery of the central through hole, and the muffler is It is fixed to the central through hole and the central flange by welding, interference fit or screw connection, and is fixed to the partition plate. In this way, the muffler is allowed to be easily and securely fixed to the partition plate.
  • the bottom of the muffler is formed with an external thread on the outside and a corresponding internal thread is formed on the inner side of the central through hole of the partition plate; or, in the case where the partition plate has a central flange portion, the bottom of the muffler is on the inside An internal thread is formed, and a corresponding external thread is formed outside the central flange portion of the partition plate. In this way, the muffler is further conveniently and firmly fixed to the partition plate.
  • the muffler includes a cylindrical body, and one or more muffler holes are formed in a top and / or a side wall of the cylindrical body.
  • the muffler further includes an annular flange extending radially outward along the bottom end of the cylindrical body.
  • the annular flange abuts the bottom wall surface or the top wall surface of the partition plate. In this way, the silencer is allowed to be positioned more precisely with respect to the partition plate and fixed to the partition plate more reliably by means of the annular flange.
  • the annular flange abuts the bottom wall surface of the partition plate, so that the annular flange functions as a sealing plate adapted to be engaged with a corresponding sealing member to seal and isolate the high-pressure cavity from the low-pressure cavity.
  • the use of an additional sealing member such as a sealing plate attached to the partition plate is eliminated, so that the muffler can perform the function of sealing and partitioning in addition to the muffler function.
  • the top of the cylindrical body includes a plurality of muffler holes arranged in a ring shape, and / or the side wall of the cylindrical body includes a plurality of muffler holes arranged in a circumferential direction.
  • the cylindrical body has a height ranging from 20 mm to 40 mm, and / or the cylindrical body has a radial dimension ranging from 20 mm to 80 mm.
  • the processing of the muffler is easier and the noise reduction effect is good (especially the noise reduction effect is good for a specific frequency).
  • the scroll compressor further includes a reed valve arranged at the exhaust port, and the muffler is arranged to be aligned with the exhaust port to perform noise reduction on the working noise of the reed valve.
  • the muffler can effectively and accurately reduce the noise of the working noise of the reed valve.
  • the scroll assembly includes a recess provided on a side of the fixed scroll facing away from the movable scroll, and the scroll compressor further includes a floating seal ring assembly, and the floating seal is arranged in the recess to define a back pressure cavity.
  • the floating seal ring assembly has a sealing tip, and the sealing tip abuts the annular flange of the muffler to seal and isolate the high-pressure cavity from the low-pressure cavity.
  • the annular flange of the muffler By engaging the annular flange of the muffler with the sealing tip of the floating seal assembly, in the case where a floating seal assembly for defining a back pressure cavity is provided, the annular flange of the muffler is advantageously used to simply realize the high-pressure cavity. Sealed from the low-pressure chamber.
  • the floating seal ring assembly has a flange extending radially inward from the sealing tip, and the scroll compressor further includes a check valve plate arranged on the flange to cover the air flow passage inside the flange.
  • the scroll compressor further includes a limiting member housed inside the muffler for limiting an upward movement range of the check valve disc.
  • the check valve disc By installing a check valve disc on the floating seal assembly and a limiting member inside the muffler, in the case that only a check valve disc is provided without a reed valve, the check valve disc can be simply used to prevent high pressure The gas flows back while the muffler does not interfere with the check valve disc and the stop member.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure
  • FIGS. 2 and 3 respectively show a top view and a cross-sectional view of a scroll assembly according to an embodiment of the present disclosure
  • FIG. 4 and 5 illustrate a top view and a cross-sectional view, respectively, of another scroll assembly according to an embodiment of the present disclosure
  • FIG. 6 and 7 illustrate an assembled state diagram and an exploded state diagram, respectively, of a muffler device according to an embodiment of the present disclosure
  • FIG. 8 shows a bottom view of the noise reduction device in FIG. 6
  • 9A to 9C are cross-sectional views of the muffler taken along line A-A in FIG. 8, showing three different fixing modes of the muffler;
  • FIG. 10 illustrates a schematic diagram of a muffler and a floating seal assembly in a scroll compressor according to an embodiment of the present disclosure
  • FIG. 11 shows a bottom view of the muffler and the floating seal assembly of FIG. 10 in a mounted state
  • FIG. 12 shows a cross-sectional view taken along line A-A of FIG. 11;
  • FIG. 13 and 14 illustrate a bottom view and a cross-sectional view of a partition plate of a muffler device according to an embodiment of the present disclosure
  • 15A, 15B, and 15C respectively show a perspective view, a top view, and a cross-sectional view taken along line A-A of the muffler of the muffler device according to an embodiment of the present disclosure
  • 16A, 16B, and 16C show a perspective view, a top view, and a cross-sectional view taken along line A-A of the top view, respectively, of a muffler according to still another embodiment of the present disclosure
  • 17A, 17B, and 17C show a perspective view, a top view, and a cross-sectional view taken along line A-A of the top view, respectively, of a muffler according to another embodiment of the present disclosure
  • FIG. 18 is a cross-sectional view of a muffler adopting a screw connection according to an embodiment of the present disclosure, in which an enlarged screw connection is shown;
  • FIG. 19 illustrates a simulation calculation curve of a sound energy transmission loss of a muffler device according to an embodiment of the present disclosure.
  • 20A and 20B are diagrams illustrating test results of an actual noise reduction effect of the noise reduction device according to an embodiment of the present disclosure.
  • FIG. 1 first illustrates one example of a scroll compressor 100 according to the present disclosure.
  • the scroll compressor 100 employs an improved muffler 120 and a scroll assembly 110 improved thereby.
  • the compressor 100 mainly includes a compressor casing composed of a top cover 101, a casing body 102, and a base 103.
  • the space inside the compressor casing is divided into a high-pressure cavity 104 and a low-pressure cavity 105.
  • the scroll assembly 110 is located in the low-pressure cavity 105, is arranged on the thrust bearing 130, and is driven by the main shaft 106 to compress the gas.
  • the scroll assembly 110 mainly includes an orbiting scroll 111 and a fixed scroll 112 arranged above the orbiting scroll 111 in an opposing manner.
  • the gas entering the low-pressure chamber 105 through the air inlet port 108 is compressed by the suction cavity between the movable scroll 111 and the fixed scroll 112 through the air inlet of the outer peripheral wall of the fixed scroll 112, and is then discharged through the exhaust port 110a.
  • the gas compression cavity is constituted by the vortex-type line 111 a of the movable vortex 111 and the vortex-type line 112 a of the fixed vortex 112.
  • FIGS. 2 to 5 show schematic diagrams of two exemplary scroll assemblies 110.
  • the scroll assembly 110 shown in FIGS. 2 and 3 is provided with a reed valve (HVE valve) 115 and a floating seal assembly 113 without a check valve disc 117, and the scroll assembly 110 shown in FIGS. 4 and 5 is provided.
  • the scroll assembly 110 in FIGS. 2 and 3 is the same as the scroll assembly used in the compressor 100 of FIG. 1.
  • the exhaust port 110a is provided in the center of the end plate of the fixed scroll 112.
  • the inner cymbal portion 112b of the fixed scroll 112 is formed to extend upwardly around the exhaust port 110a.
  • the air port 110a is directly above.
  • the floating seal assembly 113 is arranged in a recessed portion of the fixed scroll 112 on the side facing away from the movable scroll 111, and is installed so as to be sleeved on the outside of the inner ridge portion 112b of the fixed scroll 112, thereby defining the back pressure cavity 112c .
  • the compressed gas ejected through the exhaust port 110a opens the reed valve 115 through the upper center opening of the floating seal assembly 113 above the fixed scroll 112 and is discharged, as shown in FIG. 3.
  • the reed valve 115 is mainly used to stabilize the pressure of the gas discharged from the exhaust port 110a, and to ensure that the discharged gas has a required sufficient pressure.
  • the floating seal ring assembly 113 is mainly used to form a back pressure cavity 112 c above the fixed scroll 112 to always press the fixed scroll 112 toward the movable scroll 111.
  • FIG. 4 and 5 illustrate a scroll assembly 110 according to another embodiment.
  • the scroll assembly 110 is not provided with a reed valve 115, but at a flange 114a extending radially inward from a sealing tip 114 of the floating seal assembly 113
  • a check valve disc 117 is provided, and the check valve disc 117 opens or closes in response to a pressure difference between the inside and the outside thereof.
  • the compressed gas discharged from the exhaust port 110a enters the floating seal ring assembly 113 and then pushes open the check valve 117 on the top to discharge, as shown in FIG. 5.
  • a non-return valve disc limiting stud 118 penetrating through the non-return valve disc 117 of the floating seal ring assembly 113 is also provided.
  • the check valve limit stud 118 has a rod portion 118b serving as a guide section and an outwardly extending stop portion 118a formed on the upper portion.
  • the scroll assembly 110 of FIG. 5 may be used in conjunction with the muffler 120 according to the present disclosure without interfering with each other.
  • a floating seal assembly with a check valve cannot be used because the muffler will prevent the floating seal assembly from being installed on the floating seal assembly.
  • Check valve disc since the muffler in the existing muffler device is directly installed to the inner part of the fixed scroll, a floating seal assembly with a check valve cannot be used because the muffler will prevent the floating seal assembly from being installed on the floating seal assembly. Check valve disc.
  • the gas discharged from the scroll unit 110 enters the upper muffler 120 (in particular, the muffler 122 of the muffler 120), and performs noise reduction.
  • the noise-reduced gas leaves the muffler 120 and enters the high-pressure chamber 104, and is then discharged from the compressor 100 through the exhaust port 107.
  • the muffler 120 includes a partition plate 121 and a muffler 122. After the compressed gas enters the muffler 122, the noise is attenuated to achieve a noise reduction effect.
  • the partition plate 121 has an umbrella-like configuration similar to a "lid” and extends toward the outside to cover the entire scroll assembly 110 (as shown in FIG. 1).
  • the muffler 122 is fixed to the center of the partition plate 121 and is located above the exhaust port 110 a of the scroll assembly 110 (as shown in FIG. 1). After being installed in place, the muffler 120 is independent of the scroll assembly 110.
  • the muffler 122 is independent of the gas compression component or other additional components (such as the floating seal assembly 113) composed of the orbiting scroll 111 and the fixed scroll 112. . “Independent” here means that the muffler 122 may be in contact with the components of the scroll assembly 110 without being fixed by these components, or may be spatially isolated from the scroll assembly 110.
  • the muffler 122 of the muffler 120 can be installed more flexibly than the existing mufflers mentioned in the background, which can use welding connections, interference connections, threads, etc.
  • Various connection methods such as connection are used to fix to the partition plate 121.
  • the partition plate 121 has a central through hole 121 b for fixing the muffler 122, and the muffler 122 is then firmly fixed into the central through hole 121 b by welding, interference fit, or screw connection.
  • the fixed scroll and the movable scroll are usually made of cast iron, and the cast iron is not a base material suitable for welding connection, so the muffler is not suitable for welding and fixed to the movable scroll or fixed scroll. It is also difficult to use interference connections based on existing muffler arrangements.
  • the silencer needs to be fitted into the inner part of the fixed scroll with interference pressure, and if it has a reed valve, the silencer must be installed to accurately fix the reed valve.
  • the actual assembly process is difficult and requires complex press fitting. device.
  • additional structures may be required to compensate for part tolerances and accuracy errors, resulting in complex assembly structures and therefore not suitable for practical applications.
  • the muffler in the background can be fixed to the fixed scroll with a screw connection, this method is not suitable for a fixed scroll with a thin inner crotch, as explained in the background art.
  • the muffler 122 is not directly fixed to the fixed scroll 112, but is fixed to the partition plate 121. This arrangement allows the muffler 122 to be installed using the various connection methods described above. For the welding connection, by selecting a suitable material with good weldability to make the partition plate 121 and the muffler 122, a good welded joint can be obtained without changing the materials of the orbiting scroll and the fixed scroll.
  • the muffler 122 may be made of carbon steel, powder metallurgy material, or metal such as copper, and the partition plate 121 may be made of carbon steel.
  • the process of press-fitting the muffler 122 into the partition plate 121 is relatively simple, can be performed independently, and the press-fitting equipment is simple.
  • the screw connection portion may be formed on the partition plate 121 and the muffler 122 correspondingly.
  • the inner flange portion 112b of the fixed scroll 112 does not need to have a large thickness to form the screw connection portion, so that a thin-walled inner portion can be used.
  • the fixed vortex 112 of the crotch 112b In the case of press-fit installation and threaded installation, the partition plate 121 and the muffler 122 can also be made of cast iron material. Although the welding performance is not high, the cast iron material has excellent castability, processability, wear resistance and shock absorption. , Can provide good mechanical properties for the partition plate 121 and the muffler 122.
  • the "independent" arrangement of the muffler 122 also allows the position and size of the muffler 120 to be flexibly adjusted, allowing additional components to be added to the scroll assembly 110 without interfering with the muffler 120, thereby the vortex
  • the design of the component 110 is also more flexible.
  • FIG. 9A shows a press-fit installation method
  • FIG. 9B shows a welding installation method
  • FIG. 9C shows a screw connection installation method.
  • the muffler 122 and the partition plate 121 are connected to each other at the joint 120a, respectively.
  • Fig. 9B shows the welded joint at the joint 120a
  • Fig. 9C shows the threaded connection at the joint 120a.
  • an external thread 122 e is formed on the outside of the muffler 122, and the external thread 122 e is located at a joint portion 120 a of the muffler 122 and the central through hole 121 b of the partition plate 121.
  • a corresponding internal thread 121i (shown in FIG. 14) is formed inside the central through hole 121b of the partition plate 121 so as to be engaged with the external thread 122e of the muffler 122.
  • the partition plate 121 may adopt other configurations.
  • a flange portion extending upward may be formed at the periphery of the central through hole 121b of the partition plate 121, and the muffler 122 may be fixedly connected to the outside of the flange portion.
  • the muffler 122 is located on the outside (upper side) of the partition plate 121 as a whole instead of being “embedded” in the partition plate 121.
  • the muffler 122 may also be arranged to be inserted only inside the flange portion or sleeved on the flange portion.
  • the outside, or the muffler 122 may also be arranged to be inserted into both the inside of the flange portion and the inside of the central through hole.
  • FIG. 10 to 12 illustrate diagrams in which a muffler 120 and a floating seal ring assembly 113 are installed together according to an embodiment of the present disclosure.
  • the muffler 122 abuts the sealing top 114 of the floating seal ring assembly 113 to isolate the high pressure chamber 104 and the low pressure chamber 105 of the scroll compressor 100 from each other.
  • the bottom of the muffler 122 abuts against the sealing tip 114 of the floating seal assembly 113 and partially covers the inner region of the sealing tip 114.
  • the lateral dimension of the check valve disc 117 will be smaller than the uncovered area inside the seal top 114.
  • a check valve may be provided
  • the slice limiting stud 118 has an upwardly extending portion accommodated inside the muffler 122.
  • the height of the muffler 122 is designed to provide sufficient space for accommodating the limit stud 118 inside, and the specific height range will be described below.
  • the muffler 122 may be arranged to directly abut the inner cymbal portion 112b of the fixed scroll 112.
  • the muffler A flexible seal ring is provided between the annular flange 122b of the 122 (as shown in FIG. 15A) and the inner cymbal portion 112b of the fixed scroll 112 to achieve a seal on the one hand to ensure that the gas discharged from the exhaust port 110a smoothly enters the muffler 122
  • FIG. 13 and 14 illustrate schematic diagrams of a partition plate 121 according to an embodiment of the present disclosure.
  • the structure of the partition plate 121 of the muffler 120 according to the present disclosure is designed to facilitate the installation of the muffler 122, and at the same time, it can accommodate and cover other components of the scroll assembly below.
  • the partition plate 121 mainly includes an umbrella-shaped body 121d, a cylindrical portion 121c, and an annular attachment portion 121e.
  • a central through hole 121b for mounting the muffler 122 is formed in the center of the umbrella-shaped body 121d, and extends outward from the central through hole 121b so as to cover the lower scroll assembly 110.
  • the umbrella-shaped body 121d is composed of a horizontal section 121h extending from the central through hole 121b and an inclined section 121f extending from the horizontal section 121h, and a protruding arc may be provided between the horizontal section 121h and the inclined section 121f.
  • the shape portion 121g increases the structural strength of the umbrella-shaped body 121d.
  • the "umbrella-like" structure of the umbrella-shaped body 121d can provide a more stable installation platform for the muffler 122, while leaving enough accommodation space for the upper high-pressure cavity 104 to accommodate additional components.
  • the cylindrical portion 121c extends substantially vertically downward from the periphery of the umbrella-shaped body 121d to form a joint area for engaging an external structure (for example, a compressor housing), and the cylindrical portion 121c can be compressed with The inner wall of the casing is fitted.
  • an external structure for example, a compressor housing
  • the annular attachment portion 121e is formed to extend radially outward around the cylindrical portion 121c, and may be formed, for example, as an annular flange for engaging the compressor housing.
  • the partition plate 121 is attached to the joint position of the top cover 101 and the housing body 102 via the annular attachment portion 121e, and is further fixed by welding or the like.
  • Providing the cylindrical portion 121c and the ring-shaped attachment portion 121e helps the partition plate 121 to be more securely mounted to external components (the improved structural strength of the partition plate 121 itself and the stable installation of the partition plate 121 with external components also makes When the muffler is installed on the partition plate, it still avoids the partition plate and thus avoids excessive vibration of the compressor casing), and provides a better sealing effect, but its specific structure is not limited to the form shown in the figure, any suitable Any structure for fixing the partition plate 121 is feasible.
  • the partition plate 121 is not only used for mounting the muffler 122, but also can be used to seal and separate the high-pressure chamber 104 and the low-pressure chamber 105 together with the muffler 122 (by means of the ring flange of the muffler 122 serving as a sealing plate). .
  • the muffler cover (dividing plate) of the existing muffler must be combined with an additional specially designed sealing seat member to achieve the effect of sealing and separating the high-pressure cavity and the low-pressure cavity.
  • the partition plate 121 further includes a boss portion 121 a formed on the umbrella-shaped body 121 d.
  • the boss portion 121 a provides an additional accommodation space inside the umbrella-shaped body 121 d for receiving additional devices on the scroll assembly 110. , Such as the additional jet port 109 shown in FIG. 1.
  • the form of the boss portion 121a is not limited to the "stepped" structure shown in the figure, and can be adjusted according to the shape of the additional device accommodated in actual needs.
  • FIGS. 15A to 17C show various embodiments of the muffler 122 according to the present disclosure.
  • the figure shows that the configuration of the muffler 122 is basically the same except that the positions and numbers of the muffler holes 122 a of the muffler 122 are different. And aperture and height and radial dimensions of the muffler body part.
  • the muffler 122 includes a cylindrical body 122c and an annular flange 122b formed around the bottom of the cylindrical body 122c.
  • a plurality of silencing holes 122a are formed in the top and / or the side wall of the cylindrical body 122c, and noise is significantly reduced when the compressed gas is discharged through the silencing holes 122a.
  • the cylindrical body 122c of the muffler 120 protrudes into the high-pressure cavity 104, and discharges compressed gas into the high-pressure cavity 104 while reducing noise.
  • the annular flange 122b is used to define the installation position of the muffler 122 relative to the partition plate 121. In the installed state, the annular flange 122b is arranged to abut the bottom wall surface of the partition plate 121, as shown clearly in FIGS. 9A to 9C. Out. Thus, the annular flange 122b can serve as a sealing surface for sealing the peripheral gap of the central through hole 121b of the partition plate 121 (used as a sealing plate suitable for engagement with a corresponding sealing member, such as a sealing tip of a floating seal assembly). Thus, the high-pressure cavity 104 and the low-pressure cavity 105 are sealed and separated together with the partition plate 121.
  • the muffler 122 has both a muffler function and a function of sealingly separating the high-pressure cavity 104 and the low-pressure cavity 105.
  • the sealed partition function also ensures that the acoustic energy of the gas discharged from the exhaust port 110a is transmitted to the muffler 122 without being transmitted to the partition plate 121 and the compressor housing.
  • the top edge of the cylindrical body 122c of the muffler 122 is formed with a chamfer or a rounded corner to eliminate a sharp edge.
  • the height and radial size of the cylindrical body 122c, the number, aperture and position of the muffler holes 122a different muffler effects can be obtained.
  • different muffler hole arrangements can be designed for noise at a specific frequency. It enables the muffler according to the present disclosure to achieve a good noise reduction effect for a certain specific frequency (for example, a frequency related to noise caused by a reed valve).
  • the top of the cylindrical body 122c shown in FIGS. 15A to 15C is formed with 6 diameters 16A to 16C, the top of the cylindrical body 122c is formed with 24 diameters Hole.
  • a series of muffler holes 122a are formed around the side wall of the cylindrical body 122c of the muffler 122, which may be, for example, 24 diameters. Holes or 6 diameters Hole.
  • the size of the muffler holes 122a decreases correspondingly and the number of muffler holes 122a with multiple small apertures is better than a small amount.
  • the sound-absorbing effect of the large-diameter sound-absorbing hole 122a So in the above example, 24 diameters
  • the muffler hole 122a's muffler effect is better than 6 diameters Sound reduction effect of the sound reduction hole 122a.
  • excessive reduction in the size of the muffler hole will increase processing costs.
  • a muffler that is relatively easy to process and has a good noise reduction effect (especially a good noise reduction effect for a specific frequency) is designed.
  • the height and radial dimension of the muffler 122 also affect the muffler effect.
  • the cylindrical body 122c of the muffler 122 according to the present disclosure may have a height in a range of 20 mm to 40 mm, and a radial size (for example, a diameter of a cylinder) in a range of 20 mm to 80 mm.
  • the height and radial dimensions of the muffler 122 have a positive correlation with the muffler effect, that is, as the height and / or outer diameter size increases, the muffler effect is optimized.
  • the height and radial dimensions can be selected based on the displacement size of the scroll assembly 110, the size (height, outer diameter) of the partition plate 121, and the desired sound-absorbing effect (for example, sound-absorbing for a specific frequency band).
  • the muffler process of the muffler 122 follows the following formula for loss of sound energy transmission:
  • TL represents the transmission loss of acoustic energy
  • W represents the sound power
  • P represents the sound pressure
  • A represents the flow area
  • the infix suffix indicates the silencer inlet
  • the suffix out indicates the silencer outlet, namely the muffler hole.
  • FIG. 19 shows a simulation calculation curve of sound energy transmission loss obtained by the muffler according to the present disclosure based on this formula. It can be seen from the figure that the specially designed muffler 120 according to the present disclosure has a noise in the frequency band of 3000 Hz to 3500 Hz. Significant reduction effect.
  • 41F represents the saturated evaporation temperature of the compressor working medium (for example, refrigerant), and 131F represents the saturation condensation temperature of the compressor working medium.
  • the test results are shown in the graphs in Figure 20A (for Table 1) and Figure 20B (for Table 2).
  • the actual measurement results show that the overall operating noise of the compressor has decreased by about 4-5 dB (A) ("A” here means the noise test A-class weighting is used), especially in the expected noise reduction band around 3150Hz (the noise source in this band is mainly caused by reed valve flapping), there is about 10dB (A) noise reduction, the actual hearing sense Significant improvement.
  • the noise reduction device 120 can provide the following beneficial effects:
  • the muffler 122 of the muffler 120 is directly assembled to the partition plate 121 and is independent of the scroll assembly 110, so: the size design and arrangement are more flexible and can be adjusted according to the structure of the scroll assembly 110; the scroll assembly 110 is not restricted Structure, such as removing restrictions on the type of floating seal assembly and the wall thickness of the inner volute of the scroll; simplifying the assembly process.
  • the annular flange 122b of the muffler 122 is adapted to abut the partition plate 121, and at the same time is adapted to abut the sealing top 114 of, for example, the floating seal ring assembly 113 to seal and isolate the high pressure chamber from the low pressure chamber, which makes the discharge compressed
  • the gas is introduced into the muffler 122 to prevent the transmission of noise and sound energy to the partition plate 121 and the compressor casing. Therefore, the muffler 122 has both a muffler function and a function of isolating the high and low pressure chambers.

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Abstract

一种涡旋压缩机，包括：涡旋组件（110），涡旋组件（110）具有动涡旋（111）和定涡旋（112），动涡旋（111）和定涡旋（112）各自包括动涡旋型线（111a）和定涡旋型线（112a）并且彼此配合以形成一系列压缩腔，涡旋组件（110）限定有排气口（110a）；以及消音装置（120），消音装置（120）布置在涡旋组件（110）上方，消音装置（120）包括分隔板（121）和消音器（122），分隔板（121）用于将涡旋压缩机的内部空间分隔为高压腔和低压腔，分隔板（121）具有中央通孔（121b），消音器（122）布置在排气口（110a）上方，其中，消音器（122）固定至中央通孔（121b）而独立于涡旋组件（110）。该涡旋压缩机的消音装置具有消除噪音和密封分隔高低压腔的双重功能，并且布置方式灵活，不会与涡旋组件相互干涉。

Description

涡旋压缩机
本申请要求于2018年6月22日提交中国专利局、申请号为201820985551.1、名称为“涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本公开涉及涡旋设备，具体涉及带有消音装置的涡旋压缩机。
背景技术
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。
压缩机是一种将低压气体提升为高压气体的流体机械，是制冷系统中的核心设备。涡旋压缩机是一种典型的容积式压缩机。涡旋压缩机中的主要部分为涡旋组件，其用来压缩流体。涡旋组件通常包括彼此叠套在一起的定涡旋和动涡旋以及例如分别联接至定涡旋与动涡旋以防止动涡旋自转的十字滑环。
涡旋组件的定涡旋和动涡旋以叠套的方式互相配合在一起，其中动涡旋相对于定涡旋偏心对置安装。涡旋压缩机中的电机带动曲轴使得动涡旋相对于定涡旋沿预定轨迹运行，于是在动涡旋和定涡旋的涡旋型线之间形成一系列月牙形压缩空间。
在涡旋压缩机的工作过程中会产生显著的噪音，噪音主要来源于涡旋组件压缩气体的噪音、涡旋组件的排气口处的排气噪音、以及涡旋组件的排气口处的簧片阀的振动及拍击噪音等。目前已经提出用于隔离或减小压缩机工作噪音的多种方式，例如，改进压缩机的机体结构设计、在压缩机外配备隔音罩、在噪音发生源处布置消音器。对于布置消音器的方案，一种已知的方式为在涡旋组件上加装消音器，其可以用于消除涡旋组件排气口处的排气噪音等。
已知一种带消音器的涡旋压缩机，其中使用的消音器大体为杯型结构，杯型结构的侧壁中形成有多个消音孔。该消音器固定地安装在定涡旋的内榖部上并位于定涡旋的排气口上方，从而减小排气口处的排气噪音。
已有压缩机中采用的消音器直接安装至定涡旋的内榖部，基于这种结构， 较适用的固定消音器的方式是螺纹连接固定。螺纹连接要求在定涡旋的内榖部的圆周壁上形成螺纹，因此内榖部需要具有足够的壁厚以便同时满足螺纹连接以及结构强度方面的要求。由此，这种消音器难以适用于定涡旋的内榖部壁厚较薄的压缩机。
本公开期望提出针对此问题的解决方案。
发明内容
本公开的一个目的是提供一种涡旋压缩机，其具有改进的消音装置，该消音装置布置方式灵活，具有增加的通用性，适用于多种类型的涡旋组件。
本公开的另一个目的是提供一种涡旋压缩机，其具有改进的消音装置，该消音装置具有简化的结构，易于装配，具有消音和隔离压缩机高低压腔的双重功能。
针对上述目的，根据本公开的一个方面提供了一种涡旋压缩机，包括：涡旋组件，其具有动涡旋和定涡旋，动涡旋和定涡旋各自包括动涡旋型线和定涡旋型线并且彼此配合以形成一系列压缩腔，涡旋组件限定有排气口；以及消音装置，其布置在涡旋组件上方，包括分隔板和消音器，分隔板用于将所述涡旋压缩机的内部空间分隔为高压腔和低压腔，分隔板具有中央通孔，消音器布置在排气口上方，其中，消音器固定至中央通孔而独立于涡旋组件。
基于这种涡旋压缩机，消音器固定至分隔板而非涡旋组件，与涡旋组件为彼此独立，因此不会影响涡旋组件的结构，能够适用于多种类型的涡旋组件；同时，消音器不仅用于消除噪音，而且例如借助于其环形凸缘而与分隔板共同将压缩机的高压腔和低压腔密封分离，具有消音和分隔高低压腔的双重功能。
优选地，消音器以焊接、过盈配合或螺纹连接的方式固定至中央通孔而固定至分隔板；或者，分隔板还具有从中央通孔的周缘向上延伸的中央凸缘部，消音器以焊接、过盈配合或螺纹连接的方式固定至中央通孔和中央凸缘部而固定至分隔板。以此方式，允许消音器方便地且牢固地固定至分隔板。
优选地，消音器的底部在外侧形成有外螺纹，分隔板的中央通孔的内侧形成有对应的内螺纹；或者，在分隔板具有中央凸缘部的情况下，消音器的底部在内侧形成有内螺纹，分隔板的中央凸缘部的外侧形成有对应的外螺纹。以此方式，允许消音器进一步方便地且牢固地固定至分隔板。
优选地，消音器包括筒状本体，筒状本体的顶部和/或侧壁中形成有一个或多个消音孔。
优选地，消音器还包括沿筒状本体的底端径向向外延伸的环形凸缘，在消音器安装就位的状态下，环形凸缘抵靠分隔板的底壁面或顶壁面。以此方式，允许消音器借助于环形凸缘而更加精确地相对于分隔板定位并且更加可靠地固定至分隔板。
优选地，环形凸缘抵靠分隔板的底壁面，使得环形凸缘用作适于与对应密封构件接合的密封板，以将高压腔与低压腔密封隔离。以此方式，消除了使用额外的附接至分隔板的密封板等密封构件，使得消音器除了起到消音作用之外还能够起到密封分隔的功能。
优选地，筒状本体的顶部包括以环形形式排列的多个消音孔，并且/或者，筒状本体的侧壁包括沿周向方向排列的多个消音孔。
优选地，筒状本体的高度范围为20mm至40mm，并且/或者，筒状本体具有的径向尺寸的范围为20mm至80mm。
通过对消音孔的数量、尺寸和位置以及对筒状本体的尺寸的特别设计，使得消音器的加工较为容易同时减噪效果良好(尤其是针对某一特定频率减噪效果良好)。
优选地，涡旋压缩机还包括布置在排气口处的簧片阀，消音器布置成对准排气口以对簧片阀的工作噪音进行噪音消减。以此方式，使得消音器能够特别针对簧片阀的工作噪音进行有效地且精准地减噪。
优选地，涡旋组件包括设置在定涡旋的背离动涡旋一侧的凹部，涡旋压缩机还包括浮动密封圈组件，浮动密封件布置在凹部中以限定背压腔。
优选地，浮动密封圈组件具有密封顶端，密封顶端抵接消音器的环形凸缘，以将高压腔与低压腔密封隔离。
通过使消音器的环形凸缘与浮动密封圈组件的密封顶端接合，使得在设置有用于限定背压腔的浮动密封圈组件的情况下，有利地利用消音器的环形凸缘简单地实现高压腔与低压腔的密封隔离。
优选地，浮动密封圈组件具有从密封顶端径向向内延伸的突边，涡旋压缩机还包括布置在突边上的止回阀片，以覆盖突边内侧的气流通道。
优选地，涡旋压缩机还包括容置在消音器内部的用于限制止回阀片的向上 移动范围的限位构件。
通过在浮动密封圈组件上安装止回阀片以及在消音器内部设置限位构件，使得在不设置簧片阀而仅设置止回阀片的情况下，能够利用止回阀片简单地防止高压气体回流，同时消音器并不与止回阀片和限位构件相互干涉。
附图说明
图1是根据本公开实施方式的涡旋压缩机的纵向截面图；
图2和图3分别示出了根据本公开实施方式的涡旋组件的俯视图和截面图；
图4和图5分别示出了根据本公开实施方式的另一涡旋组件的俯视图和截面图；
图6和图7分别示出了根据本公开实施方式的消音装置的组装状态图和分解状态图；
图8示出了图6中的消音装置的仰视图；
图9A至图9C示出了沿图8中的线A-A截取的消音装置的截面图，其中示出了消音器的三种不同的固定方式；
图10示出了根据本公开实施方式的涡旋压缩机中的消音装置与浮动密封圈组件的示意图；
图11示出了图10中的消音装置和浮动密封圈组件安装就位状态下的仰视图；
图12示出了沿图11的线A-A截取的截面图；
图13和图14示出了根据本公开实施方式的消音装置的分隔板的仰视图和截面图；
图15A、图15B和图15C分别示出了根据本公开实施方式的消音装置的消音器的立体图、俯视图和沿俯视图中的线A-A截取的截面图；
图16A、图16B和图16C分别示出了根据本公开又一实施方式的消音器的立体图、俯视图和沿俯视图的线A-A截取的截面图；
图17A、图17B和图17C分别示出了根据本公开另一实施方式的消音器的立体图、俯视图和沿俯视图的线A-A截取的截面图；
图18是根据本公开实施方式的采用螺纹连接方式的消音器的截面图，其 中示出了放大的螺纹连接部；
图19示出了根据本公开实施方式的消音装置的声能传递损失模拟计算曲线；以及
图20A和图20B示出了根据本公开实施方式的消音装置的实际降噪效果的测试结果图。
具体实施方式
下面对优选实施方式的描述仅仅是示范性的，而绝不是对本公开及其应用或用法的限制。在各个附图中采用相同的附图标记来表示相同的部件，因此相同部件的构造将不再重复描述。
本文中使用的“上方”、“向上”、“顶”和“底”等方位术语针对立式涡旋压缩机的正常工作布置来描述。亦即，这些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。例如，在卧式压缩机的情况下，则“上方”可以对应于“左侧”或“右侧”。
下面将参照附图对根据本公开的涡旋压缩机及其改进部件的结构和工作方式进行说明。
图1首先示出了根据本公开的涡旋压缩机100的一个示例。该涡旋压缩机100采用了改进的消音装置120以及由此改进的涡旋组件110。
压缩机100主要包括由顶罩101、壳体本体102和基座103构成的压缩机壳体。压缩机壳体内的空间分成高压腔104和低压腔105。涡旋组件110位于低压腔105中，布置在止推轴承130上，经由主轴106驱动来压缩气体。
涡旋组件110主要包括动涡旋111和以对置方式布置在动涡旋111上方的定涡旋112。通过进气端口108进入低压腔105的气体经由定涡旋112外周壁的进气口被吸入动涡旋111与定涡旋112之间的压缩腔被压缩，进而通过排气口110a被排出。气体压缩腔通过动涡旋111的涡旋型线111a和定涡旋112的涡旋型线112a共同构成。
图2至图5示出了两个示例性涡旋组件110的示意图。图2和图3示出的涡旋组件110设置有簧片阀(HVE阀)115和不带止回阀片117的浮动密封圈组件113，图4和图5示出的涡旋组件110设置有带止回阀片117的浮动密封圈组件113和额外的止回阀片限位螺柱118。由于采用了新设计的消音装置 120，因此根据本公开的涡旋组件110能够使用带止回阀片117的浮动密封圈组件113，使得可选用的浮动密封圈组件的类型不会受到消音装置120的影响。
图2和图3中的涡旋组件110与图1的压缩机100中使用的涡旋组件相同。排气口110a设置在定涡旋112的端板中央，定涡旋112的内榖部112b围绕排气口110a在端板向上延伸形成，簧片阀115布置在内榖部112b内侧并位于排气口110a正上方。浮动密封圈组件113布置在定涡旋112的背离动涡旋111的一侧的凹部中，并且以套设在定涡旋112的内榖部112b外侧的方式安装，由此限定背压腔112c。经由排气口110a排出的压缩气体顶开簧片阀115流过定涡旋112上方的浮动密封圈组件113的上中央开口而被排出，如图3所示。
在此，簧片阀115主要用于稳定从排气口110a排出的气体压力，确保排出的气体具有所需的足够压力。浮动密封圈组件113主要用于在定涡旋112上方形成背压腔112c，以始终将定涡旋112朝向动涡旋111按压。
图4和图5示出了另一实施方式的涡旋组件110。与图2和图3的实施方式的不同之处在于，该涡旋组件110没有设置簧片阀115，而是在浮动密封圈组件113的密封顶端114的径向向内延伸的突边114a处设置有止回阀片117，止回阀片117响应于其内外侧的压力差而开启或关闭。从排气口110a排出的压缩气体进入浮动密封圈组件113进而推开顶部的止回阀片117排出，如图5所示。同时还设置了贯穿浮动密封圈组件113的止回阀片117的止回阀片限位螺柱118。止回阀片限位螺柱118具有充当导引部段的杆部118b以及在上部形成的向外延伸的止挡部118a，当止回阀片117被下方的压力顶起时，止回阀片117可以沿着导引杆部118b移动，并且止挡部118a会防止止回阀片117因高压气体的过大排气压力而脱离。
图5的涡旋组件110可以与根据本公开的消音装置120共同使用，而不会彼此干扰。相对地，现有的消音装置中的消音器由于直接安装至定涡旋的内榖部，因此无法使用带止回阀片的浮动密封圈组件，因为消音器会阻碍在浮动密封圈组件上设置止回阀片。
从涡旋组件110排出的气体进入上方的消音装置120(特别地，进入消音装置120的消音器122)，进行噪音消减。经噪音消减的气体离开消音装置120后进入高压腔104，进而经由排气端口107排出压缩机100。
图6和图7示出了根据本公开一个实施方式的消音装置120。根据本实施 方式的消音装置120包括分隔板121和消音器122。压缩气体进入消音器122后噪声衰减，实现降噪效果。分隔板121具有类似“盖子”的伞状构型，朝向外侧伸展以覆盖整个涡旋组件110(如图1所示)。消音器122固定至分隔板121的中央并位于涡旋组件110的排气口110a的上方(如图1所示)。在安装就位后，消音装置120与涡旋组件110独立，具体地，消音器122与动涡旋111和定涡旋112构成的气体压缩部件或者其他附加部件(比如浮动密封圈组件113)独立。此处的“独立”表示消音器122可以与涡旋组件110的部件接触但不借助这些部件固定，或者可以在空间上与涡旋组件110隔离。
由于这种“独立”布置，因此与背景技术中提到的现有消音装置相比，根据本公开的消音装置120的消音器122的安装方式更灵活，可以使用焊接连接、过盈连接、螺纹连接等多种连接方式来固定至分隔板121。如图7所示，分隔板121具有用于固定消音器122的中央通孔121b，消音器122随后以焊接、过盈配合或螺纹连接的方式牢固地固定至该中央通孔121b中。
背景技术中的现有压缩机中，定涡旋和动涡旋通常以铸铁制成，铸铁不是适于焊接连接的母材，因此消音器不适于焊接固定至动涡旋或定涡旋。基于现有的消音器布置，也难以采用过盈连接。消音器需要过盈压配至定涡旋的内榖部内，并且在具有簧片阀的情况下还要使消音器安装成能够精确固定簧片阀，实际装配制程较困难，需要复杂的压装设备。此外，还可能需要额外的结构来补偿零件公差以及精度误差，导致装配结构复杂，因此并不适于实际应用。背景技术中的消音器虽然可以采用螺纹连接方式固定至定涡旋，但此种方式不适于内榖部厚度薄的定涡旋，如背景技术中说明的。
根据本公开的消音器122不直接固定至定涡旋112，而固定至分隔板121，这种布置允许采用上述的多种连接方式来安装消音器122。对于焊接连接而言，通过选择焊接性良好的合适材料制成分隔板121和消音器122，可以获得良好的焊接接头，并且无需改变动涡旋和定涡旋的材料。例如，消音器122可以由碳钢、粉末冶金材料、或铜等金属制成，分隔板121可以由碳钢制成。对于压配安装，将消音器122压配至分隔板121中的制程相对简单，可以独立进行，且压装设备简单。对于螺纹连接，螺纹连接部可以对应地形成在分隔板121和消音器122上，定涡旋112的内榖部112b不需具有大的厚度以形成螺纹连接部，从而可以使用具有薄壁内榖部112b的定涡旋112。在压配安装和 螺纹安装的情况下，分隔板121和消音器122也可以由铸铁材料制成，尽管焊接性能不高，但铸铁材料具有优良的铸造性、加工性和耐磨减震性，能够为分隔板121和消音器122提供良好的机械性能。
根据本公开的消音器122的“独立”的布置还允许灵活地调整消音装置120的位置和尺寸，允许为涡旋组件110增补额外的部件而不会与消音装置120相干涉，由此涡旋组件110的设计也更灵活。
图8和图9A至图9C具体示出了根据本公开的消音装置120的示例性连接方式。图9A示出了压配合的安装方式，图9B示出了焊接安装方式，图9C示出了螺纹连接的安装方式。在这三种连接方式中，消音器122和分隔板121分别在接合部位120a处连接至彼此。图9B示出了接合部位120a处的焊接接头，图9C示出了接合部位120a处的螺纹连接部。
具体地，如图18最佳示出的，消音器122的外侧形成有外螺纹122e，外螺纹122e位于消音器122与分隔板121的中央通孔121b的接合部位120a处。分隔板121的中央通孔121b的内侧形成有对应的内螺纹121i(图14中示出)，以便与消音器122的外螺纹122e接合。如本领域技术人员了解的，相对于焊接连接和压装连接，螺纹连接更易于部件的拆装和更换。然而，如果考虑气密性的要求，焊接连接和压装连接则更具优势。
此外，尽管图中未示出，分隔板121还可以采用其他的构型。例如，分隔板121的中央通孔121b的周缘处可以形成向上延伸的凸缘部，消音器122可以固定连接至该凸缘部的外侧。另外，可以考虑将消音器122直接焊接在分隔板121的中央通孔121b的周缘上而不设置凸缘部。在这种情况下，消音器122整体位于分隔板121的外侧(上侧)而并非“嵌入”分隔板121内。然而，也可以构想，在分隔板121设置有凸缘部的情况下，消音器122(不设有环形凸缘)也可以布置成仅插入凸缘部的内侧或套设在凸缘部的外侧，或者消音器122(设有环形凸缘或不设有环形凸缘)也可以布置成插入凸缘部的内侧以及中央通孔的内侧两者。
图10至图12示出了根据本公开实施方式的消音装置120与浮动密封圈组件113共同安装的图示。在消音装置120安装就位的状态下，消音器122抵接浮动密封圈组件113的密封顶端114，以将涡旋压缩机100的高压腔104和低压腔105相互隔离。
如图12中示出的，消音器122的底部抵靠浮动密封圈组件113的密封顶端114并且部分覆盖密封顶端114的内侧区域。一般地，止回阀片117的横向尺寸会小于密封顶端114内侧的未被覆盖的区域，则为了防止止回阀片117因脱离浮动密封圈组件113太远而不能复位，可以设置止回阀片限位螺柱118，其向上延伸的部分容置在消音器122内部。消音器122的高度设计为在其内部提供用于容置限位螺柱118的足够空间，具体地高度范围将在下文说明。
此外，基于本公开的原理，还可以考虑没有设置浮动密封圈组件113的简单实施方式，消音器122可以布置成直接抵接定涡旋112的内榖部112b，这种情况下需要在消音器122的环形凸缘122b(如图15A所示)与定涡旋112的内榖部112b之间设置柔性密封圈，以一方面实现密封而确保从排气口110a排出的气体顺利进入消音器122，而另一方面避免例如涡旋组件的振动传递至分隔板121和压缩机壳体。基于这种布置，消音装置120的整体高度也可以减小。
图13和图14示出了根据本公开实施方式的分隔板121的示意图。根据本公开的消音装置120的分隔板121的结构设计为便于安装消音器122，同时能够容置并覆盖下方的涡旋组件的其他部件。如图中所示，分隔板121主要包括伞状本体121d、筒状部121c和环状附接部121e。
伞状本体121d的中央形成了用于安装消音器122的中央通孔121b，并且从中央通孔121b向外扩展延伸以便覆盖下方的涡旋组件110。具体地，伞状本体121d由从中央通孔121b延伸的水平部段121h和从水平部段121h延伸的倾斜部段121f构成，并且，水平部段121h与倾斜部段121f之间还可以设置突起弧形部121g以提高伞状本体121d的结构强度。伞状本体121d的“伞状”结构能够为消音器122提供更稳定的安装平台，同时为上部的高压腔104留出足够的容置空间，以容纳附加部件。
筒状部121c从伞状本体121d的周缘基本竖直地向下延伸以形成用于接合外部结构(比如，压缩机壳体)的接合区域，在安装就位后该筒状部121c可以与压缩机壳体的内壁贴合。
环状附接部121e围绕筒状部121c径向向外地延伸形成，例如可以形成为环形突边，以用于接合压缩机壳体。分隔板121借助环状附接部121e附接至顶罩101与壳体本体102的接合位置，进而通过焊接等方式固定。提供筒状部121c和环形附接部121e有助于分隔板121更稳固地安装至外部部件(分隔板 121本身改进的结构强度以及分隔板121与外部部件的稳固安装也使得在将消音器安装至分隔板的情况下仍然避免分隔板进而避免压缩机壳体的过度振动)，并提供更好的密封效果，但其具体结构并不限于图中示出的形式，任何适于固定安装分隔板121的结构都是可行的。由此，分隔板121不仅用于安装消音器122，而且能够与消音器122(借助于消音器122的用作密封板的环形凸缘)一起将高压腔104与低压腔105密封分隔开。现有消音装置的消音罩(分隔板)必须结合额外的专门设计的密封座部构件才能实现密封分隔高压腔与低压腔的效果。
分隔板121还包括形成在伞状本体121d上的凸台部121a，该凸台部121a在伞状本体121d内部提供了额外的容置空间，用于容置涡旋组件110上的附加装置，例如图1中示出的附加喷气端口109。该凸台部121a的形式并不限于图中示出的“台阶状”结构，可以根据实际需要容置的附加装置的形状来调整。
图15A至图17C示出了根据本公开的消音器122的多个实施方式，图中示出了消音器122的构型基本相同，不同之处在于消音器122的消音孔122a的位置、数量和孔径以及消音器本体部分的高度和径向尺寸。
在图中示出的示例中，消音器122包括筒状本体122c以及围绕筒状本体122c的底部形成的环形凸缘122b。在筒状本体122c的顶部和/或侧壁中形成有多个消音孔122a，压缩气体经由消音孔122a排出时噪音会显著降低。在安装就位后，消音装置120的筒状本体122c突伸至高压腔104内，在消减噪音的同时将压缩气体排入高压腔104。
环形凸缘122b用于限定消音器122相对于分隔板121的安装位置，在安装状态下，环形凸缘122b布置成抵靠分隔板121的底壁面，如图9A至图9C中清楚示出的。由此，环形凸缘122b可以作为密封分隔板121的中央通孔121b的周边间隙的密封面(用作适于与对应密封构件——例如浮动密封圈组件的密封顶端——接合的密封板)，从而与分隔板121一起密封分隔高压腔104和低压腔105。由此，根据本公开的消音器122同时具备消音功能以及密封分隔高压腔104与低压腔105的功能。密封分隔功能也确保了从排气口110a排出的气体的声能传入消音器122，而不会向分隔板121和压缩机壳体传递。
有利地，消音器122的筒状本体122c的顶部边缘形成有倒角或圆角，以 消除锋利的边缘。
通过调整筒状本体122c的高度和径向尺寸、消音孔122a的数量和孔径及位置能够获得不同的消音效果，特别是能够针对某一特定频率的噪音设计不同的消音孔布置方式等，由此使得根据本公开的消音器能够针对某一特定频率(例如与簧片阀导致的噪音相关的频率)实现良好的减噪效果。
图15A至图15C示出的筒状本体122c的顶部形成有6个直径
Figure PCTCN2019092245-appb-000001
的孔，图16A至图16C示出的筒状本体122c的顶部形成有24个直径
Figure PCTCN2019092245-appb-000002
的孔。在图17A至图17C的示例中，围绕消音器122的筒状本体122c的侧壁形成有一系列消音孔122a，例如可以是24个直径
Figure PCTCN2019092245-appb-000003
的孔或6个直径
Figure PCTCN2019092245-appb-000004
的孔。
根据本公开的原理，在消音器122上的孔的总通道面积一定的情况下，消音孔122a的尺寸减小则相应地数量增加，多个小孔径的消音孔122a的消音效果要优于少量大孔径的消音孔122a的消音效果。因此，上述示例中，24个直径
Figure PCTCN2019092245-appb-000005
的消音孔122a的消音效果优于6个直径
Figure PCTCN2019092245-appb-000006
的消音孔122a的消音效果。同时，过多的尺寸减小的消音孔会造成加工成本增加。根据本公开，在综合考虑上述因素之后，设计出加工较为容易且减噪效果良好(尤其是针对某一特定频率减噪效果良好)的消音器。
消音器122的高度和径向尺寸同样会影响消音效果。根据本公开的消音器122的筒状本体122c可以具有20mm至40mm范围内的高度，以及20mm至80mm范围内的径向尺寸(比如，圆筒的直径)。消音器122的高度和径向尺寸与消音效果成正相关关系，即，高度和/或外径尺寸增加，则消音效果优化。高度和径向尺寸可以基于涡旋组件110的排量大小、分隔板121的尺寸(高度、外径)、以及期望的消音效果(例如，针对某一特定频段消音)来选择。
根据本公开的原理，消音器122的消音过程遵循以下的声能传递损失公式：
Figure PCTCN2019092245-appb-000007
其中，TL表示声能传输损失，W表示声功率，P表示声压，A表示流通面积，下缀in表示消音器入口，而下缀out表示消音器出口即消音孔。
图19中示出了根据本公开的消音装置基于此公式得到的声能传递损失模 拟计算曲线，由图中可以看出根据本公开的经过特别设计的消音装置120对3000Hz～3500Hz频段的噪音有显著的降低效果。
除了模拟降噪效果，本申请人还在多种压缩机机型上分别进行了实验性的装配及标定工况点噪音测试，以验证根据本公开的消音装置120的实际降噪效果。使用的测试条件如下面的表格1和表格2所示。
表格1
Figure PCTCN2019092245-appb-000008
表格2
Figure PCTCN2019092245-appb-000009
注：上述表格中的41F表示压缩机工质(比如，制冷剂)的饱和蒸发温度，131F表示压缩机工质的饱和冷凝温度。
测试结果如图20A(针对表格1)和图20B(针对表格2)的图表所示，实测结果表明压缩机的总体运行噪音下降了约4～5dB(A)(“A”在此表示噪声测试采用A级计权)，特别在期望的降噪频段3150Hz附近的降噪效果明显(该频段的噪音来源主要是簧片阀拍击导致)，有约10dB(A)的噪声下降，实际听感明显改善。
总体上，根据本公开的消音装置120能够提供如下的有益效果：
1.消音装置120的消音器122直接装配至分隔板121，与涡旋组件110独 立，因此：尺寸设计和布置更加灵活，可以根据涡旋组件110的结构来调整；不限制涡旋组件110的结构，比如消除了对浮动密封圈组件类型以及涡旋内榖部壁厚的限制；简化了装配过程。
2.消音器122的环形凸缘122b适于抵接分隔板121，同时适于抵接例如浮动密封圈组件113的密封顶端114，以将高压腔与低压腔密封隔离，这使得排出的压缩气体都引入消音器122中，避免噪声声能传递至分隔板121和压缩机壳体，由此，消音器122同时具备消音功能和隔离高低压腔的功能。
3.通过实验发现，消音装置120的实际降噪效果与模拟降噪效果正相关，这证明了消音器122通过改变消音孔和筒状本体的尺寸参数而能够针对某一特定频率实现精准且有效的降噪。
尽管在此已详细描述本公开的各种实施方式，但是应该理解本公开并不局限于这里详细描述和示出的具体实施方式，在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (13)

  1. 一种涡旋压缩机，包括：
    涡旋组件，所述涡旋组件具有动涡旋和定涡旋，所述动涡旋和所述定涡旋各自包括动涡旋型线和定涡旋型线并且彼此配合以形成一系列压缩腔，所述涡旋组件限定有排气口；以及
    消音装置，所述消音装置布置在所述涡旋组件上方，所述消音装置包括分隔板和消音器，所述分隔板用于将所述涡旋压缩机的内部空间分隔为高压腔和低压腔，所述分隔板具有中央通孔，所述消音器布置在所述排气口上方，
    其特征在于，所述消音器固定至所述中央通孔而独立于所述涡旋组件。
  2. 根据权利要求1所述的涡旋压缩机，其特征在于：
    所述消音器以焊接、过盈配合或螺纹连接的方式固定至所述中央通孔而固定至所述分隔板；或者
    所述分隔板还具有从所述中央通孔的周缘向上延伸的中央凸缘部，所述消音器以焊接、过盈配合或螺纹连接的方式固定至所述中央通孔和所述中央凸缘部而固定至所述分隔板。
  3. 根据权利要求2所述的涡旋压缩机，其特征在于：所述消音器的底部在外侧形成有外螺纹，所述分隔板的所述中央通孔的内侧形成有对应的内螺纹；或者，在所述分隔板具有所述中央凸缘部的情况下，所述消音器的底部在内侧形成有内螺纹，所述分隔板的所述中央凸缘部的外侧形成有对应的外螺纹。
  4. 根据权利要求1所述的涡旋压缩机，其特征在于：所述消音器包括筒状本体，所述筒状本体的顶部和/或侧壁中形成有一个或多个消音孔。
  5. 根据权利要求4所述的涡旋压缩机，其特征在于：所述消音器还包括沿所述筒状本体的底端径向向外延伸的环形凸缘，在所述消音器安装就位的状 态下，所述环形凸缘抵靠所述分隔板的底壁面或顶壁面。
  6. 根据权利要求5所述的涡旋压缩机，其特征在于：所述环形凸缘抵靠所述分隔板的底壁面，使得所述环形凸缘用作适于与对应密封构件接合的密封板，以将所述高压腔与所述低压腔密封隔离。
  7. 根据权利要求4所述的涡旋压缩机，其特征在于：所述筒状本体的顶部包括以环形形式排列的多个消音孔，并且/或者，所述筒状本体的侧壁包括沿周向方向排列的多个消音孔。
  8. 根据权利要求4所述的涡旋压缩机，其特征在于：所述筒状本体的高度范围为20mm至40mm，并且/或者，所述筒状本体的径向尺寸范围为20mm至80mm。
  9. 根据权利要求1至8中任一项所述的涡旋压缩机，其特征在于：所述涡旋压缩机还包括布置在所述排气口处的簧片阀，所述消音器布置成对准所述排气口以对所述簧片阀的工作噪音进行噪音消减。
  10. 根据权利要求1至8中任一项所述的涡旋压缩机，其特征在于：所述涡旋组件包括设置在所述定涡旋的背离所述动涡旋一侧的凹部，所述涡旋压缩机还包括浮动密封圈组件，所述浮动密封件布置在所述凹部中以限定背压腔。
  11. 根据权利要求10所述的涡旋压缩机，其特征在于：所述浮动密封圈组件具有密封顶端，所述密封顶端抵接所述消音器的环形凸缘，以将所述高压腔与所述低压腔密封隔离。
  12. 根据权利要求11所述的涡旋压缩机，其特征在于：所述浮动密封圈组件具有从所述密封顶端径向向内延伸的突边，所述涡旋压缩机还包括布置在所述突边上的止回阀片，以覆盖所述突边内侧的气流通道。
  13. 根据权利要求12所述的涡旋压缩机，其特征在于：所述涡旋压缩机还包括容置在所述消音器内部的用于限制所述止回阀片的向上移动范围的限位构件。
PCT/CN2019/092245 2018-06-22 2019-06-21 涡旋压缩机 Ceased WO2019242721A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114294222A (zh) * 2021-12-08 2022-04-08 松下压缩机(大连)有限公司 一种具有补气结构的涡旋压缩机

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN208651145U (zh) * 2018-06-22 2019-03-26 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
CN110185615B (zh) * 2019-04-29 2024-05-10 苏州为山之环境技术有限公司 具有消音结构的密封组件且与横隔板固定的涡旋压缩机
CN110159536B (zh) * 2019-06-10 2020-11-24 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机、空调器和车辆
CN110410327B (zh) * 2019-08-29 2024-11-22 珠海格力节能环保制冷技术研究中心有限公司 法兰密封结构、压缩机、空调器
CN111765089B (zh) * 2020-07-06 2025-05-16 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机和空调器
CN114251261B (zh) * 2020-09-21 2025-08-08 谷轮环境科技（苏州）有限公司 涡旋压缩机
CN112576513B (zh) * 2020-12-03 2022-09-16 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机和空调器
CN114645835A (zh) * 2020-12-18 2022-06-21 丹佛斯（天津）有限公司 消音装置和具有该消音装置的压缩机
EP4015824B1 (en) * 2020-12-18 2024-07-10 Danfoss (Tianjin) Ltd. Muffler device and compressor having the same
CN114017346B (zh) * 2021-11-10 2024-01-23 广东美芝制冷设备有限公司 消音器、压缩机及其制冷设备
CN116792317A (zh) * 2022-03-16 2023-09-22 艾默生环境优化技术(苏州)有限公司 消音器、单向阀和涡旋压缩机
CN116816682B (zh) * 2022-03-22 2025-12-30 谷轮环境科技（苏州）有限公司 压缩机
US12259163B2 (en) 2022-06-01 2025-03-25 Copeland Lp Climate-control system with thermal storage
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub
US11965507B1 (en) 2022-12-15 2024-04-23 Copeland Lp Compressor and valve assembly
US12416308B2 (en) 2022-12-28 2025-09-16 Copeland Lp Compressor with shutdown assembly
US12173708B1 (en) 2023-12-07 2024-12-24 Copeland Lp Heat pump systems with capacity modulation
US12163523B1 (en) 2023-12-15 2024-12-10 Copeland Lp Compressor and valve assembly
CN119084313A (zh) * 2024-08-28 2024-12-06 珠海凌达压缩机有限公司 一种消音结构、应用其的压缩机及空调器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1280251A (zh) * 1999-07-07 2001-01-17 科普兰公司 涡卷压缩机排放消声器
US6352417B1 (en) * 2000-11-06 2002-03-05 Scroll Technologies Optimized radial compliance for a scroll compressor
US6390792B1 (en) * 2001-01-23 2002-05-21 Rechi Precision Co., Ltd. Venting passage for isolation block of scroll compressor and check valve for the same
CN101270751A (zh) * 2008-05-07 2008-09-24 美的集团有限公司 涡旋式压缩机
CN202228358U (zh) * 2011-09-08 2012-05-23 艾默生环境优化技术(苏州)研发有限公司 压缩机
CN202937456U (zh) * 2012-09-21 2013-05-15 珠海格力电器股份有限公司 具有消音功能的高低压分隔板及涡旋压缩机
CN208651145U (zh) * 2018-06-22 2019-03-26 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5649816A (en) * 1986-08-22 1997-07-22 Copeland Corporation Hermetic compressor with heat shield
US4767293A (en) * 1986-08-22 1988-08-30 Copeland Corporation Scroll-type machine with axially compliant mounting
US4877382A (en) * 1986-08-22 1989-10-31 Copeland Corporation Scroll-type machine with axially compliant mounting
US5591014A (en) * 1993-11-29 1997-01-07 Copeland Corporation Scroll machine with reverse rotation protection
US6017205A (en) * 1996-08-02 2000-01-25 Copeland Corporation Scroll compressor
US5800141A (en) * 1996-11-21 1998-09-01 Copeland Corporation Scroll machine with reverse rotation protection
US5921761A (en) * 1997-04-17 1999-07-13 Copeland Corporation Scroll machine with discharge duct
KR100286312B1 (ko) 1998-07-28 2001-05-02 구자홍 스크롤 압축기의 체크밸브 소음저감장치
KR100446214B1 (ko) * 2001-11-29 2004-08-30 주식회사 롤텍 스크롤 압축기의 소음 저감 구조
KR20040107093A (ko) * 2003-06-12 2004-12-20 엘지전자 주식회사 스크롤 압축기의 토출 소음 저감 장치
TWI235791B (en) * 2003-12-25 2005-07-11 Ind Tech Res Inst Scroll compressor with self-sealing structure
US7338265B2 (en) * 2005-03-04 2008-03-04 Emerson Climate Technologies, Inc. Scroll machine with single plate floating seal
US7429167B2 (en) * 2005-04-18 2008-09-30 Emerson Climate Technologies, Inc. Scroll machine having a discharge valve assembly
JP5436978B2 (ja) * 2009-08-26 2014-03-05 三洋電機株式会社 スクロール圧縮機
TWI461606B (zh) * 2010-12-09 2014-11-21 Ind Tech Res Inst 渦卷式壓縮機浮動裝置之改良

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1280251A (zh) * 1999-07-07 2001-01-17 科普兰公司 涡卷压缩机排放消声器
US6352417B1 (en) * 2000-11-06 2002-03-05 Scroll Technologies Optimized radial compliance for a scroll compressor
US6390792B1 (en) * 2001-01-23 2002-05-21 Rechi Precision Co., Ltd. Venting passage for isolation block of scroll compressor and check valve for the same
CN101270751A (zh) * 2008-05-07 2008-09-24 美的集团有限公司 涡旋式压缩机
CN202228358U (zh) * 2011-09-08 2012-05-23 艾默生环境优化技术(苏州)研发有限公司 压缩机
CN202937456U (zh) * 2012-09-21 2013-05-15 珠海格力电器股份有限公司 具有消音功能的高低压分隔板及涡旋压缩机
CN208651145U (zh) * 2018-06-22 2019-03-26 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3812590A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114294222A (zh) * 2021-12-08 2022-04-08 松下压缩机(大连)有限公司 一种具有补气结构的涡旋压缩机

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