WO2014198215A1 - Compresseur à spirale, élément à spirale fixe et élément spiro-orbital - Google Patents

Compresseur à spirale, élément à spirale fixe et élément spiro-orbital Download PDF

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Publication number
WO2014198215A1
WO2014198215A1 PCT/CN2014/079588 CN2014079588W WO2014198215A1 WO 2014198215 A1 WO2014198215 A1 WO 2014198215A1 CN 2014079588 W CN2014079588 W CN 2014079588W WO 2014198215 A1 WO2014198215 A1 WO 2014198215A1
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WO
WIPO (PCT)
Prior art keywords
scroll
compression chamber
communication
end plate
fixed scroll
Prior art date
Application number
PCT/CN2014/079588
Other languages
English (en)
Chinese (zh)
Inventor
崔永华
范忆文
韩艳春
Original Assignee
艾默生环境优化技术(苏州)有限公司
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
Priority claimed from CN201310237705.0A external-priority patent/CN104235016B/zh
Priority claimed from CN2013203437694U external-priority patent/CN203321824U/zh
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 WO2014198215A1 publication Critical patent/WO2014198215A1/fr

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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
    • 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • 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
    • 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
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the present invention relates to a scroll compressor and a fixed scroll member and an orbiting scroll member, and more particularly to a scroll compressor having an improvement in pressure fluctuation of a central compression chamber.
  • a scroll compressor includes a compression mechanism composed of a fixed scroll member and an orbiting scroll member.
  • the fixed scroll member includes a substantially spiral constant scroll extending from the end plate thereof
  • the movable scroll member includes a substantially spiral movable scroll extending from the end plate thereof.
  • the spiral fixed scroll and the helical moving scroll are engaged to define a plurality of closed crescent compression chambers therebetween.
  • the orbiting scroll member is driven by, for example, an electric motor to perform translational rotation with respect to the fixed scroll member (that is, the axis of the orbiting scroll member revolves with respect to the axis of the fixed scroll member, but the orbiting scroll member and the fixed scroll member
  • the scroll members themselves do not rotate about their respective axes, thereby causing the volume of the compression chamber defined by the spiral fixed scroll and the helical orbiting scroll to gradually move from the radially outer side to the radially inner side. From big to small.
  • the pressure in the compression chamber is also gradually increased, so that the refrigerant in the compression chamber is compressed and finally discharged from the exhaust port located at the center of the fixed scroll member, thereby achieving the suction, compression, and discharge of the refrigerant. cycle.
  • a compression chamber (also referred to as central compression) at the center of the scroll member that communicates with the exhaust port and is capable of communicating with a discharge space (high pressure chamber) defined between the muffler plate and the front end cover
  • the chamber or high pressure compression chamber has the highest pressure
  • the pair of compression chambers also referred to as secondary high pressure compression chambers located radially outward of the central compression chamber and adjacent to the central compression chamber have a second highest pressure.
  • the central compression chamber With the translational rotation of the orbiting scroll member, the central compression chamber is connected to the secondary high pressure compression chamber at a certain rotation angle of the orbiting scroll member (corresponding to the scroll separation point where the fixed scroll and the movable scroll are separated) A new central compression chamber is formed, and the compression chamber, which is originally located on the radially outer side of the secondary high pressure compression chamber, becomes a new secondary high pressure compression chamber. [ ⁇ 5] When the higher pressure central compression chamber communicates with the lower pressure secondary high pressure compression chamber, the pressure in the central compression chamber drops sharply. This pressure drop in the central compression chamber and large pressure fluctuations can cause problems. First of all, especially for small-sized air conditioner scroll compressors, such large pressure fluctuations cause high noise problems.
  • the elastic flap of the exhaust valve may strongly impinge on, for example, the valve seat due to such large fluctuations in pressure, causing abnormal noise.
  • HVE exhaust valve
  • the compressor is in a low compression ratio condition, such large pressure fluctuations may deteriorate the energy efficiency ratio and working stability of the compressor, thereby adversely affecting the energy efficiency ratio and working stability of the entire refrigeration system.
  • a muffler ⁇ may be provided at the exhaust port (as shown in Fig. 14, wherein Fig. 14 is a perspective view showing the muffler according to the related art).
  • noise e.g., high frequency noise
  • a pressure drop is also caused to adversely affect the performance of the compressor and the entire refrigeration system.
  • the additional provision of the muffler can complicate the manufacturing process, increase the manufacturing cost, and require additional installation space for the muffler due to an increase in the number of components, and at the same time deteriorate the operational reliability of the compressor accordingly.
  • An object of the present invention is to provide a scroll compressor capable of reducing a pressure difference between a first/center compression chamber and a second/second pressure chamber during a wrap separation point.
  • Another object of the present invention is to provide a scroll compressor capable of making the pressure change of the center compression chamber more gentle without a sudden pressure drop at the wrap separation point.
  • Another object of the present invention is to provide a scroll compressor capable of suppressing high noise and abnormal noise.
  • Another object of the present invention is to provide a scroll compressor capable of suppressing noise on an entire frequency band including a high frequency range.
  • a scroll compressor capable of improving the energy efficiency ratio and operational stability of a compressor.
  • the scroll compressor includes: a compression mechanism including a fixed scroll member and an orbiting scroll member, the fixed scroll member including a fixed scroll end plate and a predetermined extension from the fixed scroll end plate a scroll, the orbiting scroll member including an orbiting scroll end plate and a movable scroll extending from the movable scroll end plate, the fixed scroll and the movable scroll being engaged with each other to be in the fixed scroll Defining a plurality of compression chambers between the orbiting scroll, the compression chamber including a first compression chamber at a substantially radial center of the compression mechanism and a radially outer side of the first compression chamber and a second compression chamber adjacent to the first compression chamber; an exhaust port disposed at a substantially radial center of the fixed scroll end plate and adapted to communicate with the first compression chamber; And
  • a fixed scroll member including a fixed scroll end plate and a fixed scroll end a fixed scroll extending from the plate, the fixed scroll and the movable scroll of the corresponding movable scroll member being engaged with each other to define a plurality of compression chambers between the fixed scroll and the movable scroll, the compression
  • the chamber includes a first compression chamber at a substantially radial center of the fixed scroll member and a second compression chamber located radially outward of the first compression chamber and adjacent to the first compression chamber, wherein
  • the fixed scroll member further includes a communication passage disposed at the fixed scroll end plate such that at least one of the second compression chambers and the first compression chamber can be before the scroll separation point Start to communicate.
  • an orbiting scroll member including an orbiting scroll end plate and the movable scroll end a movable scroll extending from the plate, the movable scroll being engaged with a fixed scroll of the corresponding fixed scroll member to define a plurality of compression chambers between the movable scroll and the fixed scroll, the compression
  • the chamber includes a first compression chamber at a substantially radial center of the orbiting scroll member and a second compression chamber located radially outward of the first compression chamber and adjacent to the first compression chamber, wherein
  • the movable scroll member further includes a communication passage disposed at the movable scroll end plate such that at least one of the second compression chambers and the first compression chamber can be before the scroll separation point Start to communicate.
  • the first/center pressure at which the wrap is separated can be made The pressure difference between the condensing chamber and the second/second high pressure compression chamber is reduced, so that the pressure change in the central compression chamber can be made gentler without a pressure dip at the vortex separation point.
  • the use of the silencer can be eliminated. Thereby, it is possible to avoid causing a pressure drop to adversely affect the performance of the compressor and the entire refrigeration system. Moreover, it is avoided to additionally provide a muffler to avoid complicated manufacturing processes, increased manufacturing costs, and additional installation space for the muffler due to an increase in the number of components, while ensuring the operational reliability of the compressor accordingly.
  • FIG. 1 is a perspective view showing a fixed scroll member of a compression mechanism according to a first embodiment of the present invention
  • FIG. 2 is a perspective view showing an orbiting scroll member of a compression mechanism according to a first embodiment of the present invention
  • Figure 3 is a longitudinal sectional perspective view showing a fixed scroll member according to a first embodiment of the present invention
  • Figure 4 is a longitudinal sectional perspective view showing a fixed scroll member according to a modification of the first embodiment of the present invention
  • Figure 5 is a schematic view showing a state in which the compression mechanism according to the first embodiment of the present invention is before the wrap separation point;
  • FIG. 6 is a schematic view showing a state in which the compression mechanism according to the first embodiment of the present invention is at a wrap separation point;
  • Figure 7 is a view showing a compression mechanism according to a first embodiment of the present invention at a wrap separation point Schematic diagram of the post state;
  • Figure 8 is a longitudinal sectional perspective view showing a fixed scroll member of a compression mechanism according to a second embodiment of the present invention.
  • Figure 9 is a schematic view showing a state in which the compression mechanism according to the second embodiment of the present invention is before the wrap separation point;
  • Figure 10 is a schematic view showing a state in which a compression mechanism according to a second embodiment of the present invention is at a wrap separation point;
  • Figure 32 is a schematic view showing a state in which the compression mechanism according to the second embodiment of the present invention is after the wrap separation point;
  • Figure 23 is a graph showing an exemplary variation of the pressure of the central compression chamber and the secondary high pressure compression chamber according to the present invention and according to the related art as a function of the wrap angle;
  • FIG. 13 is an exploded perspective view showing an exhaust valve that can be applied to the compressor according to the present invention.
  • Fig. 14 is a perspective view showing a muffler according to the related art. detailed description
  • FIG. 1 is a view showing a fixed scroll of a compression mechanism according to a first embodiment of the present invention.
  • 2 is a perspective view showing a movable scroll member of a compression mechanism according to a first embodiment of the present invention
  • FIG. 3 is a longitudinal sectional perspective view showing a fixed scroll member according to a first embodiment of the present invention.
  • 4 is a longitudinal sectional perspective view showing a fixed scroll member according to a modification of the first embodiment of the present invention
  • FIG. 1 is a view showing a fixed scroll of a compression mechanism according to a first embodiment of the present invention.
  • 2 is a perspective view showing a movable scroll member of a compression mechanism according to a first embodiment of the present invention
  • FIG. 3 is a longitudinal sectional perspective view showing a fixed scroll member according to a first embodiment of the present invention.
  • 4 is a longitudinal sectional perspective view showing a fixed scroll member according to a modification of the first embodiment of the present invention
  • FIG. 1 is a view showing a fixed scroll
  • FIG. 5 is a schematic view showing a state before the compression mechanism according to the first embodiment of the present invention is in a state before the scroll separation point.
  • 6 is a schematic view showing a state in which the compression mechanism according to the first embodiment of the present invention is at the wrap separation point
  • FIG. 7 is a view showing a state in which the compression mechanism according to the first embodiment of the present invention is after the wrap separation point.
  • a scroll compressor includes a fixed scroll member 20 and a moving The compression mechanism 10 of the scroll member 30.
  • the fixed scroll member 20 includes a fixed scroll 24 extending from its end plate 22, for example, in a generally spiral shape
  • the orbiting scroll member 30 includes a movable scroll 34 extending from its end plate 32, for example, in a generally spiral shape.
  • the fixed scroll 24 and the movable scroll 34 are engaged with each other to define a plurality of closed crescent-shaped compression chambers C therebetween.
  • the orbiting scroll member 30 is driven by, for example, an electric motor (not shown) to perform translational rotation with respect to the fixed scroll member 20 (i.e., the axis of the orbiting scroll member 30 with respect to the axis of the fixed scroll member 20) Revolving, but both the orbiting scroll member 30 and the fixed scroll member 20 do not rotate about their respective axes, thereby causing the compression chamber C defined by the fixed scroll 24 and the orbiting scroll 34 to be radially outward. During the process of moving radially inward, the volume gradually decreases from large to small.
  • the pressure in the compression chamber C is also gradually increased, so that the working fluid (e.g., refrigerant) in the compression chamber C is compressed and finally from the exhaust port 40, for example, at the center of the end plate 22 of the fixed scroll member 20. Discharge, thereby achieving a working cycle of suction, compression and discharge of the working fluid.
  • the working fluid e.g., refrigerant
  • a compression chamber that is in communication with the exhaust port 40 and is capable of communicating with a discharge space (high pressure chamber) defined between the muffler plate and the front end cover at the center of the scroll member (also referred to as a compression chamber) a first compression chamber or a central compression chamber or a high pressure compression chamber, and used as the high pressure zone according to the present invention) C1 has the highest pressure, and a pair of compression chambers located radially outward of the central compression chamber C1 and adjacent to the central compression chamber C1 (Also referred to as a second compression chamber or a secondary high pressure compression chamber, and as a secondary high pressure region according to the present invention) C2 has a second highest pressure.
  • a communication groove 50 (see Figs. 1 to 3) for connecting the central compression chamber C1 and the secondary high pressure compression chamber C2 is provided.
  • the communication groove 50 is disposed to advance the central compression chamber C1 and the secondary high pressure compression chamber C2 in advance before the scroll separation point.
  • the communication groove 50 is used as the communication passage (the pressure fluctuation restricting means for suppressing the pressure fluctuation of the center compression chamber) according to the present invention.
  • the dynamic scroll angle (also referred to as the separation point scroll angle) at a certain scroll separation point is assumed to be 0 degrees, and the dynamic scroll angle before the scroll separation point is assumed to be positive.
  • the central compression chamber C1 and the secondary high pressure compression chamber C2 may be brought into communication when the dynamic scroll angle is less than 360 degrees and greater than 0 degrees.
  • the communication slot 50 can The central compression chamber C1 and the secondary high pressure compression chamber C2 are brought into communication to be set such that the movable scroll angle is less than 180 degrees and greater than 20 degrees.
  • the communication groove 50 may be configured to initiate communication between the central compression chamber C1 and the secondary high pressure compression chamber C2 when the dynamic scroll angle is less than 150 degrees and greater than 30 degrees.
  • the communication groove 50 may be configured to initiate communication between the central compression chamber C1 and the secondary high pressure compression chamber C2 when the orbiting scroll angle is less than 120 degrees and greater than 40 degrees. In another example, the communication groove 50 may be disposed to initiate communication between the central compression chamber C1 and the secondary high pressure compression chamber C2 when the dynamic scroll angle is 80 degrees. By appropriately setting the dynamic scroll angle at the start of communication, it is possible to contribute to ensuring proper communication between the central compression chamber C1 and the secondary high pressure compression chamber C2.
  • Fig. 12 is a graph showing an exemplary variation of the pressure of the central compression chamber and the secondary high pressure compression chamber according to the present invention and according to the related art with the scroll angle.
  • the curve ABCDEF represents the pressure change of the central compression chamber of the compression mechanism according to the related art (i.e., the communication groove/communication path is not provided), and the curve A'-B'-C'-D represents the compression mechanism according to the related art.
  • the curve ABDEF represents the pressure change of the central compression chamber C1 of the compression mechanism 10 according to the present invention (i.e., the communication tank/communication passage 50 is provided), and the curve A'-B'-D represents The pressure of the secondary high pressure compression chamber C2 of the compression mechanism 10 of the present invention changes.
  • the curve ABDEF represents the pressure change of the central compression chamber C1 of the compression mechanism 10 according to the present invention (i.e., the communication tank/communication passage 50 is provided)
  • the curve A'-B'-D represents The pressure of the secondary high pressure compression chamber C2 of the compression mechanism 10 of the present invention changes.
  • the wrap angle corresponding to the C point and the C' point is the separation point wrap angle (X (the separation point wrap angle in the figure (assumed to be 53 degrees), and the B point and B'
  • the wrap angle corresponding to the point is a wrap angle (also referred to as a communication start wrap angle) in which the center compression chamber C1 and the sub-high pressure compression chamber C2 start to communicate with each other via the communication groove 50 in the case where the communication groove 50 is provided.
  • the connection start scroll angle ⁇ generally depends on the position at which the communication groove 50 is disposed, particularly the position of the communication groove 50 as to be described below as the outer end.
  • the communication start scroll angle ⁇ is 133 degrees, that is, the communication groove 50 is set to 80 degrees (i.e., 133 degrees - 53 degrees) before the wrap separation point to make the center compression chamber C1. It is in early communication with the secondary high pressure compression chamber C2.
  • the pressure change (curve ABDEF) of the central compression chamber C1 according to the present invention is gentler without a pressure dip as compared with the pressure change (curve ABCDEF) of the central compression chamber according to the related art. Case (as indicated by the section CD in the curve ABCDEF according to the related art).
  • the pressure change of the secondary high-pressure compression chamber C2 according to the present invention is more gradual without a sudden increase in pressure (as indicated by the section C'-D in the curve A'-B'-C'-D according to the related art).
  • the transition section T1 of the pressure drop of the central compression chamber C1 according to the present invention is more the transition section T2 according to the pressure drop of the central compression chamber according to the related art. The length is thereby able to release the pressure of the central compression chamber C1 to the secondary high pressure compression chamber C2 in advance to avoid a pressure dip in the scroll separation point (the separation point wrap angle (X).
  • the communication groove 50 may be provided to the end plate 22 of the fixed scroll member 20 and/or the end plate 32 of the movable scroll member 30 (e.g., the mutually facing surfaces of the end plate 22 and the end plate 32). Specifically, in one example, the communication groove 50 is provided only to the end plate 22 of the fixed scroll member 20, and in another example, the communication groove 50 is provided only to the end plate 32 of the orbiting scroll member 30, and in another In the example, the communication groove 50 is provided at both the end plate 22 of the fixed scroll member 20 and the end plate 32 of the movable scroll member 30.
  • the communication groove 50 may be in the form of an elongated groove and has an inner end 51 and an outer end 52.
  • the inner end 51 is in fluid communication with the central compression chamber C1
  • the outer end 52 has It is in fluid communication with the secondary high pressure compression chamber C2.
  • the inner end 51 of the communication groove 50 at the fixed scroll member 20 can be connected to the exhaust port 40 (also used as the high pressure region according to the present invention).
  • the exhaust port 40 also used as the high pressure region according to the present invention.
  • the position at which the inner end 51 of the communication groove 50 at the fixed scroll member 20 is disposed is not limited thereto.
  • the communication groove 50 at the orbiting scroll member 30 may include an enlarged portion 53 at a substantially radial center of the end plate 32 of the orbiting scroll member 30.
  • the enlarged portion 53 facilitates an appropriate increase in the advance communication between the central compression chamber C1 and the secondary high pressure compression chamber C2 before the scroll separation point.
  • the enlarged portion 53 may be substantially circular (as viewed in the axial direction of the compressor) or may have other suitable shapes as shown.
  • the cross-sectional shape of the communication groove 50 may be substantially rectangular.
  • the cross-sectional shape of the communication groove 50 may be substantially semicircular.
  • the flow area of the communication groove 50 (for example, when the orbiting scroll member 30 is at the separation point wrap angle (the effective cross-sectional area of the communication groove 50 that connects the central compression chamber C1 and the secondary high pressure compression chamber C2, and
  • the flow area is generally related to the depth and width of the communication groove 50. It may be appropriately changed depending on the specific application (for example, the compressor model).
  • the flow area of the communication groove 50 may be l-15 mm 2 (square
  • the flow area of the communication groove 50 may be 2-10 mm 2 .
  • the communication groove The flow area of 50 can be 5mm 2
  • the position of the inner end 51 of the groove 50, the position of the outer end 52 of the communication groove 50, and the shape of the communication groove 50 (as seen when viewed in the axial direction of the compressor)
  • the shape), the cross-sectional shape of the communication groove 50 (the cross-sectional shape taken along the axial direction of the compressor), the flow area of the communication groove 50, and even the specific installation position of the communication groove 50 can be appropriately changed as long as the wrap separation point can be (Before the separation point wrap angle (X), at least one of the central compression chamber C1 and the second high pressure compression chamber C2 is prematurely communicated at an appropriate timing and the central compression chamber C1 and the secondary high pressure compression chamber C2 can be moderately connected (ie, avoided) Small communication or excessive communication - excessive communication causes leakage loss of the compressor), thereby ensuring that the pressure change of the central compression chamber C1 is more gentle without a sudden pressure drop.
  • the communication groove 50 may be arranged to advance the central compression chamber C1 in advance with each of the pair of two secondary high pressure compression chambers C2 prior to the scroll separation point.
  • an additional elongated communication groove may be additionally provided, which may be opposed to the elongated communication groove 50 from the exhaust port. That side extends radially and may extend to the outside of the innermost portion of the fixed scroll 24.
  • the additional communication groove may be symmetrical with respect to the center of the fixed scroll member 20 with respect to the communication groove 50 in shape, size, and arrangement position.
  • an exhaust valve V including a flap VR may be disposed at the exhaust port 40 (as shown in FIG. 13 , wherein FIG. 13 is a view showing an exhaust valve that can be applied to the compressor according to the present invention An exploded perspective view) to restrict the return of working fluid from the discharge space to the compression mechanism 10 via the exhaust port 40.
  • the pressure difference between the central compression chamber and the secondary high pressure compression chamber at the time of the scroll separation point can be reduced, and the pressure change of the central compression chamber can be made gentler. There is no pressure dip in the wrap separation point.
  • a high noise problem can be effectively suppressed.
  • the exhaust valve is provided at the exhaust port, it is possible to effectively suppress the valve flap of the exhaust valve from strongly striking, for example, the valve seat to cause an abnormal noise.
  • the use of the communication groove/communication path according to the present invention can reduce the noise by about 7 dBA.
  • the compression can be improved.
  • the energy efficiency ratio and working stability of the machine are beneficial to improve the energy efficiency ratio and working stability of the entire refrigeration system.
  • the communication groove/communication path according to the present invention can increase the energy efficiency ratio under low compression ratio conditions.
  • the use of the silencer can be eliminated. Thereby, it is possible to avoid causing a pressure drop to adversely affect the performance of the compressor and the entire refrigeration system. Moreover, it is avoided to additionally provide a muffler to avoid complicated manufacturing processes, increased manufacturing costs, and additional installation space for the muffler due to an increase in the number of components, while ensuring the operational reliability of the compressor accordingly.
  • FIG. 8 is a view showing a fixed scroll of a compression mechanism according to a second embodiment of the present invention.
  • a longitudinal sectional view of the component FIG. 9 is a schematic view showing a state before the compression mechanism according to the second embodiment of the present invention is at the wrap separation point
  • FIG. 10 is a view showing the compression mechanism according to the second embodiment of the present invention.
  • a schematic view of a state at the time of separating the dots FIG. 11 is a schematic view showing a state in which the compression mechanism according to the second embodiment of the present invention is after the wrap separation point.
  • a central compression chamber C1 serving as a high pressure region according to the present invention
  • a secondary high pressure compression chamber C2 serving as a secondary high pressure region according to the present invention
  • the communication hole 50A is disposed to advance the central compression chamber C1 and the secondary high pressure compression chamber C2 in advance before the scroll separation point.
  • the communication hole 50A serves as a communication passage (pressure fluctuation restricting means for suppressing pressure fluctuation of the center compression chamber) according to the present invention.
  • the communication hole 50A may be provided in the end plate 22 of the fixed scroll member 20 and/or the end plate 32 of the movable scroll member 30.
  • the communication hole 50A may have an inner opening 51A and an outer opening 52A.
  • X i.e., when the compression mechanism 10 is at the wrap separation point
  • the inner opening is in fluid communication with the central compression chamber C1
  • the outer opening 52A has been
  • the secondary high pressure compression chamber C2 is in communication.
  • the inner opening 51A of the communication hole 50A at the fixed scroll member 20 may be connected to the exhaust port 40 (i.e., open to the wall of the exhaust port 40) such that the communication hole 50A (at least in shape) At the section where the flow is effective, it is substantially L-shaped.
  • the installation position of the inner opening 51A of the communication hole 50A at the fixed scroll member 20 is not limited thereto, for example, the inner opening 51A of the communication hole 50A at the fixed scroll member 20 may not be connected to
  • the exhaust port 40 is such that the communication hole 50A (at least at the section where the effective flow is formed) is substantially U-shaped.
  • the cross-sectional shape of the communication hole 50A may be substantially circular.
  • the scroll compressor according to the second embodiment can provide substantially the same advantageous effects as those of the scroll compressor according to the first embodiment described above.
  • the scroll compressor according to the present invention can accommodate a variety of different variations.
  • one end (inner end) of the communication hole communicates with the central compression chamber or the exhaust port, and the other end (outer end) communicates with the secondary high pressure compression chamber, however, the communication
  • the one end of the hole may also extend to communicate with a discharge space/high pressure chamber (serving as a high pressure zone according to the present invention) defined between the muffler plate and the front end cover.
  • such a communication passage (serving as a pressure fluctuation restricting means for suppressing pressure fluctuation of the center compression chamber according to the present invention) may be provided, which may be extended axially through the end plate of the fixed scroll member
  • the axial through bore and the tubular member extending from the axial through bore to the discharge space are configured such that the discharge space communicates with the secondary high pressure compression chamber at an appropriate time prior to the scroll separation point.
  • the pressure in the secondary high pressure compression chamber can be additionally raised before the scroll separation point, so that the pressure difference between the central compression chamber and the secondary high pressure compression chamber at the time of the scroll separation point is reduced, thereby making the central compression chamber
  • the pressure changes are more gradual without a sudden drop in pressure at the point of separation of the scroll. According to this modification, it is also possible to provide substantially the same advantageous effects as those of the scroll compressor according to the first embodiment as described above.
  • an orbital angle of the orbiting scroll at the wrap separation point is defined as a separation point wrap angle, and the orbiting scroll passes through the communication path in the second compression chamber and the high pressure region
  • the orbiting angle at the start of communication is defined as a communication start scroll angle, and the communication passage is disposed such that the communication start scroll angle is advanced by 20 to 180 degrees from the separation point scroll angle.
  • the communication passage is disposed such that the communication start scroll angle is 30 degrees to 150 degrees ahead of the separation point scroll angle.
  • the communication passage is disposed such that the communication start wrap angle is larger than the separation point wrap angle The degree is advanced by 40 degrees to 120 degrees.
  • the communication passage is disposed such that the communication start scroll angle is advanced by 80 degrees from the separation point wrap angle.
  • the communication passage is provided in at least one of the fixed scroll end plate and the movable scroll end plate.
  • the communication passage is a communication groove formed on the surface of the scroll end plate adapted to cause the second compression chamber to communicate with the first compression chamber in advance.
  • the cross-sectional shape of the communication groove is substantially rectangular or substantially semi-circular.
  • the communication groove In the case where the communication groove is provided in the fixed scroll end plate, the communication groove extends to the exhaust port.
  • the communication passage includes an enlarged portion located at a substantially radial center of the movable scroll end plate.
  • the communication passage is a communication hole formed in the scroll end plate adapted to cause the second compression chamber to communicate with the first compression chamber in advance.
  • the communication passage is provided in the fixed scroll end plate, the communication passage is formed in the fixed vortex adapted to cause the second compression chamber to communicate with the exhaust port in advance Connect the turns in the end plate.
  • the communication passage is adapted to communicate the second compression chamber with the discharge space.
  • a tubular member extending to the discharge space to the discharge space is formed.
  • the communication passage has a flow area that enables a pressure dip in the first compression chamber to be avoided and a leakage loss in the scroll compressor to be avoided.
  • each of the second compression chambers is capable of starting communication with the high pressure zone before the scroll separation point, and the communication passages are symmetrically disposed about a central axis of the compression mechanism.
  • the scroll compressor further includes an exhaust valve disposed at the exhaust port, the exhaust valve including a valve flap.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur à spirale, un élément à spirale fixe et un élément spiro-orbital. Le compresseur selon l'invention comprend : un mécanisme de compression (10) pourvu d'un élément à spirale fixe (20) et d'un élément spiro-orbital (30), l'élément à spirale fixe (20) comprenant une plaque d'extrémité à spirale fixe (22) et une spirale fixe (24), l'élément spiro-orbital (30) comprenant une plaque d'extrémité spiro-orbiral (32) et une spirale orbitale (34), la spirale fixe (24) et la spirale orbitale (34) étant reliées entre elles pour définir une pluralité de chambres de compression (C) comprenant des premières chambres de compression (C1) et des deuxièmes chambres de compression (C2) ; un orifice d'échappement (40) conçu pour communiquer avec les premières chambres de compression (C1) ; et un espace d'émission conçu pour communiquer avec l'orifice d'échappement (40). Les premières chambres de compression (C1), l'orifice d'échappement (40) et l'espace d'émission forment une zone haute pression. Le compresseur selon l'invention comprend également un passage de communication (50,50A) formé de sorte qu'au moins une des deuxièmes chambres de compression (C2) et la zone haute pression puissent communiquer avant un point de séparation de spirale. La pression de la première chambre de compression/chambre de compression centrale du présent dispositif peut être modifiée progressivement, ce qui permet de supprimer efficacement les hauts niveaux de bruit et d'améliorer le rapport énergie-efficacité et la stabilité de fonctionnement du compresseur à spirale.
PCT/CN2014/079588 2013-06-14 2014-06-10 Compresseur à spirale, élément à spirale fixe et élément spiro-orbital WO2014198215A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201320343769.4 2013-06-14
CN201310237705.0A CN104235016B (zh) 2013-06-14 2013-06-14 涡旋压缩机以及定涡旋部件和动涡旋部件
CN201310237705.0 2013-06-14
CN2013203437694U CN203321824U (zh) 2013-06-14 2013-06-14 涡旋压缩机以及定涡旋部件和动涡旋部件

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WO2014198215A1 true WO2014198215A1 (fr) 2014-12-18

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3418573A1 (fr) * 2017-06-23 2018-12-26 LG Electronics Inc. Compresseur à spirale présentant une meilleure performance de décharge
US10697455B2 (en) 2017-06-22 2020-06-30 Lg Electronics Inc. Compressor having lubrication structure for thrust surface
US10781817B2 (en) 2017-06-14 2020-09-22 Lg Electronics Inc. Compressor having centrifugation and differential pressure structure for oil supplying
US10816000B2 (en) 2017-07-24 2020-10-27 Lg Electronics Inc. Compressor having centrifugation structure for supplying oil
US10830237B2 (en) 2017-06-21 2020-11-10 Lg Electronics Inc. Compressor having integrated flow path structure
EP3636925A4 (fr) * 2017-07-07 2020-11-25 Daikin Industries, Ltd. Compresseur à spirale
US10851789B2 (en) 2017-07-10 2020-12-01 Lg Electronics Inc. Compressor having improved discharge structure including discharge inlets, communication hole, and discharge outlet
US11767844B2 (en) 2020-08-31 2023-09-26 Danfoss (Tianjin) Ltd. Fixed scroll disk and scroll compressor having the same

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JPS6275089A (ja) * 1985-09-27 1987-04-06 Toshiba Corp スクロ−ル形圧縮機
JPH10122167A (ja) * 1996-10-24 1998-05-12 Mitsubishi Electric Corp スクロール圧縮機
JPH10169574A (ja) * 1996-12-10 1998-06-23 Hitachi Ltd スクロール圧縮機
CN1673542A (zh) * 2004-03-22 2005-09-28 爱信精机株式会社 涡旋式压缩机
CN203321824U (zh) * 2013-06-14 2013-12-04 艾默生环境优化技术(苏州)有限公司 涡旋压缩机以及定涡旋部件和动涡旋部件

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JPS6275089A (ja) * 1985-09-27 1987-04-06 Toshiba Corp スクロ−ル形圧縮機
JPH10122167A (ja) * 1996-10-24 1998-05-12 Mitsubishi Electric Corp スクロール圧縮機
JPH10169574A (ja) * 1996-12-10 1998-06-23 Hitachi Ltd スクロール圧縮機
CN1673542A (zh) * 2004-03-22 2005-09-28 爱信精机株式会社 涡旋式压缩机
CN203321824U (zh) * 2013-06-14 2013-12-04 艾默生环境优化技术(苏州)有限公司 涡旋压缩机以及定涡旋部件和动涡旋部件

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10781817B2 (en) 2017-06-14 2020-09-22 Lg Electronics Inc. Compressor having centrifugation and differential pressure structure for oil supplying
US11248608B2 (en) 2017-06-14 2022-02-15 Lg Electronics Inc. Compressor having centrifugation and differential pressure structure for oil supplying
US10830237B2 (en) 2017-06-21 2020-11-10 Lg Electronics Inc. Compressor having integrated flow path structure
US10697455B2 (en) 2017-06-22 2020-06-30 Lg Electronics Inc. Compressor having lubrication structure for thrust surface
US11434908B2 (en) 2017-06-22 2022-09-06 Lg Electronics Inc. Compressor having lubrication structure for thrust surface
EP3418573A1 (fr) * 2017-06-23 2018-12-26 LG Electronics Inc. Compresseur à spirale présentant une meilleure performance de décharge
US10808698B2 (en) 2017-06-23 2020-10-20 Lg Electronics Inc. Scroll compressor having communication groove in orbiting end plate
EP3636925A4 (fr) * 2017-07-07 2020-11-25 Daikin Industries, Ltd. Compresseur à spirale
US10851789B2 (en) 2017-07-10 2020-12-01 Lg Electronics Inc. Compressor having improved discharge structure including discharge inlets, communication hole, and discharge outlet
US10816000B2 (en) 2017-07-24 2020-10-27 Lg Electronics Inc. Compressor having centrifugation structure for supplying oil
US11767844B2 (en) 2020-08-31 2023-09-26 Danfoss (Tianjin) Ltd. Fixed scroll disk and scroll compressor having the same

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