EP3015709B1 - Scroll-type compressor - Google Patents
Scroll-type compressor Download PDFInfo
- Publication number
- EP3015709B1 EP3015709B1 EP14816917.0A EP14816917A EP3015709B1 EP 3015709 B1 EP3015709 B1 EP 3015709B1 EP 14816917 A EP14816917 A EP 14816917A EP 3015709 B1 EP3015709 B1 EP 3015709B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- scroll
- partitioning wall
- port section
- refrigerant
- type compressor
- 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.)
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- 238000000638 solvent extraction Methods 0.000 claims description 93
- 239000003507 refrigerant Substances 0.000 claims description 42
- 238000011144 upstream manufacturing Methods 0.000 claims description 19
- 230000006835 compression Effects 0.000 claims description 15
- 238000007906 compression Methods 0.000 claims description 15
- 230000009467 reduction Effects 0.000 description 20
- 230000000694 effects Effects 0.000 description 12
- 230000007246 mechanism Effects 0.000 description 5
- 230000006872 improvement Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 238000005266 casting Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000037361 pathway Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
-
- 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
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Definitions
- the present invention relates to a scroll-type compressor configuring an air conditioning device for indoor use, for example.
- a scroll-type compressor used in a refrigerating cycle of an air conditioning device, a refrigerating device, and the like is provided with a stationary scroll and a revolving scroll.
- the stationary scroll and the revolving scroll are each formed by a spiral-shaped wrap wall being integrally formed with one surface of an end plate having a round shape.
- Such a stationary scroll and revolving scroll are made to face each other with the wrap walls mutually engaged, and the revolving scroll is revolved with respect to the stationary scroll by an electric motor or the like. Then, a compression chamber formed between the two wrap walls is displaced from an outer circumferential side to an inner circumferential side while decreasing in volume. As such, a refrigerant gas within the compression chamber is compressed.
- the refrigerant gas compressed in the compression chamber passes through to an ejection port formed in the end plate of the stationary scroll, flows into a high-pressure chamber between a discharge cover and a housing, and is further ejected from an ejection pipe provided in the housing toward a refrigerant circuit.
- the ejection port formed in the stationary scroll has an influence on the performance or noise of the scroll-type compressor. As such, various ejection ports have been proposed.
- Patent Document 1 in order to suppress vibrations and noise due to ejection of fluid compressed by the revolving motion of the scroll, fitting a collar having a hollow tube shape to the ejection port is proposed. Providing such a collar enables the vibration force of pressure pulses within the tube to be reduced, and an increase in compressor noise to be suppressed.
- Patent document 2 discloses a scroll compressor muffling according to the preamble of claim 1 of the present invention.
- the present invention has been made in view of this technological problem, and thus an object thereof is to provide a scroll-type compressor enabling reduction in the noise of a desired frequency band produced by the scroll-type compressor.
- the resonance frequency in the ejection port may be changed by changing the length and volume (hereinafter termed specifications) of the ejection port.
- specifications the specifications of the ejection port cannot be largely changed. As such, the resonance frequency cannot be changed either.
- the ejection port provided in the stationary scroll is partitioned into an upstream port section and a downstream port section and the volume of the downstream port section is increased, thereby the ejection port functioning as a muffler.
- the downstream port section is partitioned in order to have a plurality of compartments, thereby realizing a different resonance frequency than is obtained with a non-partitioned downstream port section. As such, noise reduction of a desired frequency band is made possible.
- the plurality of partitioned compartments to function as a passage for the refrigerant in order for the refrigerant to pass through the downstream port section without waste.
- the scroll-type compressor of the present invention is provided with a revolving scroll rotatably connected to an eccentric shaft portion of a main shaft, a stationary scroll facing the revolving scroll to form a compression chamber compressing a refrigerant, and having an ejection port on an end plate, the ejection port ejecting the compressed refrigerant toward a high-pressure chamber, and a discharge cover covering the ejection port.
- the scroll-type compressor of the present invention has the ejection port formed by an upstream port section provided on an upstream side in an inflow direction of the refrigerant, and a downstream port section provided on a downstream side in the inflow direction of the refrigerant, the downstream port section having a greater volume than the upstream port section.
- the downstream port section is provided with partitioning wall(s) partitioning the interior of the downstream port section into a plurality of areas, and with a refrigerant passage passing the refrigerant through the plurality of areas.
- the partitioning wall is provided in the downstream port section of the ejection port, and the specifications of the partitioning wall, such as the length and height, can be set as desired. That is, tuning of the partitioning wall is made possible. As a result, sound reduction in a desired frequency band is enabled by tuning the partitioning wall in correspondence with the target scroll-type compressor.
- the ejection port including the downstream port section has a round internal space (cavity) formed therein.
- the partitioning wall preferably has a horizontal cross-section in an arc shape. This serves to minimize turbulence in the flow of refrigerant passing through the downstream port section.
- the arc-shaped partitioning wall may be provided in one of singularity and plurality along the circumferential direction of the downstream port section. In a case where the partitioning wall is provided in plurality, symmetrically positioning the partitioning walls is preferable in order to minimize the turbulence in the flow of the refrigerant.
- any means may be used to provide the partitioning wall.
- forming the partitioning wall integrally with the discharge cover is preferable.
- the discharge cover is manufactured by casting, similarly to the revolving scroll and the stationary scroll.
- integrally forming the partitioning wall by casting reduces the number of manufacturing processes in comparison to fixing a separately manufactured partitioning wall.
- the partitioning wall with a rib is preferably formed integrally with the discharge cover in order to increase the rigidity.
- a partitioning wall is provided in a downstream port section of a scroll-type compressor and tuning is applied to the partitioning wall. This produces sound reduction in a desired frequency band and suppresses noise.
- a scroll-type compressor 1 of the present embodiment includes a housing 10 housing an electric motor 12 and a scroll-type compressor mechanism 2 driven by the electric motor 12.
- the scroll-type compressor 1 compresses a refrigerant such as R410C or R407C and, for example, supplies the refrigerant to a refrigerant circuit such as that of an air conditioning device or a refrigerator.
- a refrigerant such as R410C or R407C
- the housing 10 is provided with a housing body 101 shaped as a bottomed cylinder open at a top end, and a housing top 102 covering an opening at the top end of the housing body 101.
- An intake pipe 13 is provided on a side face of the housing body 101, introducing the refrigerant from an accumulator (not illustrated) into the housing body 101.
- An ejection pipe 14 is provided on the housing top 102, ejecting the refrigerant compressed by the scroll-type compressor mechanism 2.
- the interior of the housing 10 is partitioned by a discharge cover 25 into a low-pressure chamber 10A and a high-pressure chamber 10B.
- the electric motor 12 is provided with a stator 15 and a rotor 16.
- the stator 15 is provided with a coil generating a magnetic field upon being supplied with electric power from a power supply unit (not illustrated) that is affixed to the side face of the housing body 101.
- the rotor 16 is provided with a permanent magnet and a yoke as main components, and further joined integrally with a main shaft 17 at the center.
- An upper bearing 18 and a lower bearing 19 are provided at both ends of the main shaft 17 so as to interpose the electric motor 12, rotatably supporting the main shaft 17.
- An accommodating space 190 is formed in the upper bearing 18.
- An eccentric pin 17A provided on the top end of the main shaft 17 protrudes and is accommodated by the accommodating space 190.
- the scroll-type compressor mechanism 2 is provided with a stationary scroll 20 and a revolving scroll 30 configured to revolve with respect to the stationary scroll 20.
- the stationary scroll 20 is provided with a stationary end plate 21 and a wrap 22 having a spiral shape originating from one face of the stationary end plate 21.
- the stationary scroll 20 also includes an ejection port 23 provided on the stationary end plate 21.
- the ejection port 23 includes an upstream port section 23A and a downstream port section 23B that communicates with the upstream port section 23A and has a greater volume than the upstream port section 23A.
- Both the upstream port section 23A and the downstream port section 23B have round-shaped openings (cavities).
- the upstream port section 23A is disposed on an upstream side in a direction A of the flow of the refrigerant
- the downstream port section 23B is disposed on a downstream side thereof. Enlarging an opening surface area of the downstream port section 23B, positioned on the downstream side in the direction A, enables a reduction in pressure loss for the refrigerant in that section.
- FIG. 2B only illustrates the surrounding vicinity of the downstream port section 23B with the discharge cover 25 removed, relating to the stationary end plate 21. The same applies to FIGS. 3A to 3F , described later.
- the upstream side of the upstream port section 23A communicates with a compression chamber PR formed between the stationary scroll 20 and the revolving scroll 30.
- the downstream side of the downstream port section 23B communicates with an ejection port 27 of the discharge cover 25 covering the top of the stationary scroll 20.
- a partitioning wall 40 is provided in the downstream port section 23B.
- the partitioning wall 40 is formed of partitioning walls 40a, 40b having identical shapes and identical dimensions, each having a horizontal cross-section in an arc shape.
- the partitioning wall 40 partitions the downstream port section 23B into an outside area OA and an inside area IA, thus changing the natural frequency of the downstream port section 23B.
- the partitioning walls 40a, 40b are symmetrically disposed centered on the center C of the downstream port section 23B. Symmetrically disposing the partitioning wall 40 enables turbulence in the flow of the refrigerant in the downstream port section 23B to be minimized.
- a gap G is provided between end portions E, E of the partitioning walls 40a, 40b in the circumferential direction. This gap G is provided across the entirety of the partitioning walls 40a, 40b in the height direction, and makes the outside area OA communicate with the inside area IA in the radial direction.
- the refrigerant flowing into the downstream port section 23B passes through the refrigerant passage connecting the outside area OA, the gap G, and the inside area IA, and flows into the ejection port 27 of the discharge cover 25.
- the partitioning wall 40 is integrally formed with the discharge cover 25 and is provided so that a tip of the partitioning wall 40 is in contact with a surface of the stationary end plate 21.
- the revolving scroll 30 is likewise provided with a revolving end plate 31 having a round shape, and a wrap 32 having a spiral shape originating from one face of the revolving end plate 31.
- a boss 34 is provided on a back face of the revolving end plate 31 of the revolving scroll 30, and a drive bush 36 is assembled on the boss 34 through a bearing.
- the eccentric pin 17A is fit into the drive bush 36.
- the revolving scroll 30 is eccentrically joined to a shaft center of the main shaft 17. As such, upon rotation of the main shaft 17, the revolving scroll 30 rotates (revolves) with an eccentric distance from the shaft center of the main shaft 17 as a radius of revolution.
- an Oldham's ring (not illustrated) is provided between the revolving scroll 30 and the main shaft 17 in order to restrain the rotation of the revolving scroll 30 so that the revolving scroll 30 does not rotate upon itself while revolving.
- the wraps 22, 32 have a predetermined amount of eccentricity with respect to each other, engage with each other with a phase offset of 180°, and are in contact with each other at a plurality of positions according to a rotation angle of the revolving scroll 30. Then, the compression chamber PR is formed with point symmetry with respect to a central portion (innermost circumferential portion) of the spirals of the wraps 22, 32. Also, as the revolving scroll 30 revolves, the compression chamber is displaced gradually toward the inner circumferential side while decreasing in volume. Then, the refrigerant is maximally compressed at the central portion of the spirals.
- the compression chamber PR illustrated in FIG. 1 depicts this portion.
- the volume of the compression chamber PR formed between the two scrolls 20, 30 is also reduced in the height direction of the wraps in the middle of the spirals.
- the height of the wrap in both of the stationary scroll 20 and the revolving scroll 30 is less on the inner circumferential side than the outer circumferential side.
- an end plate on an opposite side of the stepwise wraps is made to protrude inward to a greater extent at the inner circumferential side than the outer circumferential side.
- the scroll-type compressor 1 provided with the above-described configuration is subject to excitation of the electric motor 12 and introduction of the refrigerant into the housing 10 through the intake pipe 13.
- the main shaft 17 rotates, thereby revolving the revolving scroll 30 with respect to the stationary scroll 20.
- the refrigerant is compressed in the compression chamber PR between the revolving scroll 30 and the stationary scroll 20, and the refrigerant introduced into the low-pressure chamber 10A within the housing 10 from the intake pipe 13 is taken in between the revolving scroll 30 and the stationary scroll 20.
- the refrigerant compressed in the compression chamber PR passes through the ejection port 23 of the stationary end plate 21 and the ejection port 27 of the discharge cover 25 in the stated order and is ejected into the high-pressure chamber 10B, and is then further ejected to the outside from the ejection pipe 14.
- the intake, compression, and ejection of the refrigerant are continuously performed.
- the refrigerant compressed by the stationary scroll 20 and the revolving scroll 30 is ejected from the compression chamber PR to the upstream port section 23A, and passes through the upstream port section 23A and the downstream port section 23B in the stated order.
- the refrigerant having passed through the downstream port section 23B is ejected from the ejection port 27 into the high-pressure chamber 10B.
- the refrigerant ejected into the high-pressure chamber 10B through this pathway produces a resonance at a frequency corresponding to each of the ejection ports.
- the production of this resonance causes a dramatic increase in amplitude of vibration of the ejection port, resulting in noise being increased.
- the internal space of the downstream port section 23B is partitioned into the outside area OA and the inside area IA by providing the partitioning wall 40 in the downstream port section 23B. Doing so changes the natural frequency of the downstream port section 23B relative to a case where the partitioning wall 40 is not provided. Changing the natural frequency in this manner enables a reduction in sound of a desired frequency band.
- the reduction in sound may be applied to a desired frequency band by setting a length L of the partitioning wall 40 to 1/2 the wavelength ⁇ of the sound to be reduced.
- Determining the frequency f of the sound to be reduced enables the wavelength ⁇ to be calculated from Expression 1. Then, the length L of the partitioning wall 40 is set to 1/2 of the wavelength ⁇ thus calculated.
- the partitioning walls 40a, 40b may be connected by a portion at one of the gaps G, thus forming the partitioning wall 40 in a C shape as illustrated in FIG. 3A .
- the length L of the arc of the partitioning wall 40 is increased, thus enabling a reduction in sound of a lower frequency.
- a center of symmetry C' of the partitioning wall 40 (40a, 40b) may be provided at a position having eccentricity with respect to the center C of the downstream port section 23B.
- the partitioning walls 40a, 40b having different arc lengths may be used. Doing so enables sounds of different frequency bands to be reduced. In such a situation, as illustrated in FIG. 3C , the respective distances from the center C to the partitioning walls 40a, 40b may be different from each other.
- the partitioning wall 40 may be provided as divided into three or more pieces (three in FIG. 3D ). Providing the partitioning wall 40 in plurality enables the sound reduction effect to be increased.
- partitioning walls 40A, 40C, 40B, 40D may be doubly provided with spacing in the radial direction.
- the downstream port section 23B is partitioned into a plurality of areas. That is, each of the partitioning walls 40A to 40D partitions the downstream port section 23B into an inside area and an outside area in terms of the radial direction.
- the overall length L of the arc of the partitioning wall 40 is increased, which is effective in a case where an increase in the sound reduction effect is desired.
- the partitioning walls 40 are not limited to being provided doubly, and may also be provided triply or more.
- the partitioning wall 40 may have a spiral shape.
- the partitioning wall 40 having the spiral shape partitions the downstream port section 23B into an inside area surrounded by the partitioning wall 40 in the radial direction and an outside area of the outermost circumference of the partitioning wall 40.
- the length L of the partitioning wall 40 may be increased with the partitioning wall 40 having the spiral shape. As such, this configuration is effective for reducing sound of a lower frequency.
- the refrigerant flowing in from the upstream port section 23A passes through the downstream port section 23B while flowing in a spiral along the partitioning wall 40, and is ejected to the ejection port 27.
- FIGS. 3A to 3F may be combined as appropriate.
- the partitioning wall 40 may have any of various shapes, including a linear shape, a U shape, and the like. Furthermore, in a case where a plurality, for example, two, of the partitioning walls 40a, 40b are provided, a non-symmetric arrangement may also be applied. In essence, any shape may be used for the partitioning wall provided that tuning of the partitioning wall in accordance with a frequency band of sound to be reduced is possible.
- the end portions E, E of the partitioning walls 40a, 40b each may be provided with a rib 41 extending toward the outside in the radial direction. Providing these ribs 41 improves the rigidity of the partitioning walls 40a, 40b with respect to the pressure of the refrigerant from the inside area IA to the outside in the radial direction.
- the ribs 41 have the same height as the partitioning wall 40, and equal thickness in the height direction. However, no such limitation is intended provided that the effect of rigidity improvement is obtained.
- the ribs 41 serve to form a throttle, in addition to serving the function of rigidity improvement. That is, providing the ribs 41 causes a port 44 of the refrigerant from the inside area IA to the outside area OA to be throttled. As such, the effect of sound reduction is increased.
- a rib 42 may also be provided at any position between the end portions E, E, for example at a median position. Doing so provides further improvement to the rigidity of the partitioning wall 40, and also forms a partitioning wall 50 having a length of 1/2 L between the rib 41 and the rib 42. As such, sound of a high frequency may also be reduced.
- a partitioning wall 43 having a wave-shaped horizontal cross-section may be applied.
- the partitioning wall 43 has portions corresponding to peaks and troughs of the wave shape producing a similar effect to the rib 41. Further, these portions are present in plurality, resulting in the partitioning wall 43 having higher rigidity.
- the partitioning wall 40 is not limited to being integrally formed with the discharge cover 25.
- the partitioning wall 40 may also be integrally formed with the stationary end plate 21, or may be separately manufactured from the stationary end plate 21 and the discharge cover 25 and fixed to the downstream port section 23B at a predetermined position using an appropriate approach.
- the tip of the partitioning wall 40 do not have to be in contact with the stationary end plate 21.
- the tip of the partitioning wall 40 may be separated from the stationary end plate 21, provided that the effect of noise reduction is obtained by the partitioning wall.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Description
- The present invention relates to a scroll-type compressor configuring an air conditioning device for indoor use, for example.
- A scroll-type compressor used in a refrigerating cycle of an air conditioning device, a refrigerating device, and the like is provided with a stationary scroll and a revolving scroll. The stationary scroll and the revolving scroll are each formed by a spiral-shaped wrap wall being integrally formed with one surface of an end plate having a round shape. Such a stationary scroll and revolving scroll are made to face each other with the wrap walls mutually engaged, and the revolving scroll is revolved with respect to the stationary scroll by an electric motor or the like. Then, a compression chamber formed between the two wrap walls is displaced from an outer circumferential side to an inner circumferential side while decreasing in volume. As such, a refrigerant gas within the compression chamber is compressed.
- The refrigerant gas compressed in the compression chamber passes through to an ejection port formed in the end plate of the stationary scroll, flows into a high-pressure chamber between a discharge cover and a housing, and is further ejected from an ejection pipe provided in the housing toward a refrigerant circuit.
- The ejection port formed in the stationary scroll has an influence on the performance or noise of the scroll-type compressor. As such, various ejection ports have been proposed.
- For example, in
Patent Document 1, in order to suppress vibrations and noise due to ejection of fluid compressed by the revolving motion of the scroll, fitting a collar having a hollow tube shape to the ejection port is proposed. Providing such a collar enables the vibration force of pressure pulses within the tube to be reduced, and an increase in compressor noise to be suppressed. -
Patent document 2 discloses a scroll compressor muffling according to the preamble ofclaim 1 of the present invention. -
- Patent Document 1:
Japanese Unexamined Utility Model Application Publication No. H4-82391U - Patent Document 2: UK
Patent Application GB 2 299 136 A - However, the vibrations and noise produced by the scroll-type compressor occur across a wide range of frequency. Accordingly, reducing noises in the entire frequency range using a single noise reduction measure is difficult. As such, there is a need to apply a countermeasure corresponding to a target frequency for noise reduction. For example, in
Patent Document 1, the volume of the ejection port provided with a collar is limited, which makes it difficult to reduce the noise of a low-frequency range. - The present invention has been made in view of this technological problem, and thus an object thereof is to provide a scroll-type compressor enabling reduction in the noise of a desired frequency band produced by the scroll-type compressor.
- The resonance frequency in the ejection port may be changed by changing the length and volume (hereinafter termed specifications) of the ejection port. However, given restrictions on the dimensions of the scroll-type compressor, the specifications of the ejection port cannot be largely changed. As such, the resonance frequency cannot be changed either.
- Therefore, in the present invention, the ejection port provided in the stationary scroll is partitioned into an upstream port section and a downstream port section and the volume of the downstream port section is increased, thereby the ejection port functioning as a muffler. In addition, the downstream port section is partitioned in order to have a plurality of compartments, thereby realizing a different resonance frequency than is obtained with a non-partitioned downstream port section. As such, noise reduction of a desired frequency band is made possible. However, there is a need for the plurality of partitioned compartments to function as a passage for the refrigerant in order for the refrigerant to pass through the downstream port section without waste.
- That is, the scroll-type compressor of the present invention is provided with a revolving scroll rotatably connected to an eccentric shaft portion of a main shaft, a stationary scroll facing the revolving scroll to form a compression chamber compressing a refrigerant, and having an ejection port on an end plate, the ejection port ejecting the compressed refrigerant toward a high-pressure chamber, and a discharge cover covering the ejection port.
- The scroll-type compressor of the present invention has the ejection port formed by an upstream port section provided on an upstream side in an inflow direction of the refrigerant, and a downstream port section provided on a downstream side in the inflow direction of the refrigerant, the downstream port section having a greater volume than the upstream port section. Moreover, the downstream port section is provided with partitioning wall(s) partitioning the interior of the downstream port section into a plurality of areas, and with a refrigerant passage passing the refrigerant through the plurality of areas.
- In the scroll-type compressor of the present invention, the partitioning wall is provided in the downstream port section of the ejection port, and the specifications of the partitioning wall, such as the length and height, can be set as desired. That is, tuning of the partitioning wall is made possible. As a result, sound reduction in a desired frequency band is enabled by tuning the partitioning wall in correspondence with the target scroll-type compressor.
- Typically, the ejection port including the downstream port section has a round internal space (cavity) formed therein. Taking this as a given, the partitioning wall preferably has a horizontal cross-section in an arc shape. This serves to minimize turbulence in the flow of refrigerant passing through the downstream port section. The arc-shaped partitioning wall may be provided in one of singularity and plurality along the circumferential direction of the downstream port section. In a case where the partitioning wall is provided in plurality, symmetrically positioning the partitioning walls is preferable in order to minimize the turbulence in the flow of the refrigerant.
- In the present invention, any means may be used to provide the partitioning wall. However, forming the partitioning wall integrally with the discharge cover is preferable. The discharge cover is manufactured by casting, similarly to the revolving scroll and the stationary scroll. However, integrally forming the partitioning wall by casting reduces the number of manufacturing processes in comparison to fixing a separately manufactured partitioning wall. The partitioning wall with a rib is preferably formed integrally with the discharge cover in order to increase the rigidity.
- According to the present invention, a partitioning wall is provided in a downstream port section of a scroll-type compressor and tuning is applied to the partitioning wall. This produces sound reduction in a desired frequency band and suppresses noise.
-
-
FIG. 1 is a vertical cross-sectional view of a scroll-type compressor of an embodiment. -
FIG. 2A is a partial enlarged view of a vicinity of an ejection port of a stationary scroll ofFIG. 1 , andFIG. 2B is a perspective view schematically illustrating the vicinity of the ejection port ofFIG. 2A . -
FIGS. 3A to 3F are horizontal cross-sectional views for explaining various states of arrangement of a partitioning wall. -
FIGS. 4A to 4C are horizontal cross-sectional views for explaining measures of improving rigidity of the partitioning wall. -
FIG. 5 shows a sound reduction effect of the embodiment. - The invention is described in detail below on the basis of embodiments illustrated in the accompanying drawings.
- As illustrated in
FIG. 1 , a scroll-type compressor 1 of the present embodiment includes ahousing 10 housing anelectric motor 12 and a scroll-type compressor mechanism 2 driven by theelectric motor 12. The scroll-type compressor 1 compresses a refrigerant such as R410C or R407C and, for example, supplies the refrigerant to a refrigerant circuit such as that of an air conditioning device or a refrigerator. The configuration of the scroll-type compressor 1 is described below. - The
housing 10 is provided with ahousing body 101 shaped as a bottomed cylinder open at a top end, and ahousing top 102 covering an opening at the top end of thehousing body 101. - An
intake pipe 13 is provided on a side face of thehousing body 101, introducing the refrigerant from an accumulator (not illustrated) into thehousing body 101. - An
ejection pipe 14 is provided on thehousing top 102, ejecting the refrigerant compressed by the scroll-type compressor mechanism 2. The interior of thehousing 10 is partitioned by adischarge cover 25 into a low-pressure chamber 10A and a high-pressure chamber 10B. - The
electric motor 12 is provided with astator 15 and arotor 16. - The
stator 15 is provided with a coil generating a magnetic field upon being supplied with electric power from a power supply unit (not illustrated) that is affixed to the side face of thehousing body 101. Therotor 16 is provided with a permanent magnet and a yoke as main components, and further joined integrally with amain shaft 17 at the center. - An
upper bearing 18 and alower bearing 19 are provided at both ends of themain shaft 17 so as to interpose theelectric motor 12, rotatably supporting themain shaft 17. - An
accommodating space 190 is formed in theupper bearing 18. Aneccentric pin 17A provided on the top end of themain shaft 17 protrudes and is accommodated by theaccommodating space 190. - The scroll-
type compressor mechanism 2 is provided with astationary scroll 20 and a revolvingscroll 30 configured to revolve with respect to thestationary scroll 20. - The
stationary scroll 20 is provided with astationary end plate 21 and a wrap 22 having a spiral shape originating from one face of thestationary end plate 21. Thestationary scroll 20 also includes anejection port 23 provided on thestationary end plate 21. - As illustrated in
FIG. 2A , theejection port 23 includes anupstream port section 23A and adownstream port section 23B that communicates with theupstream port section 23A and has a greater volume than theupstream port section 23A. Both theupstream port section 23A and thedownstream port section 23B have round-shaped openings (cavities). Theupstream port section 23A is disposed on an upstream side in a direction A of the flow of the refrigerant, and thedownstream port section 23B is disposed on a downstream side thereof. Enlarging an opening surface area of thedownstream port section 23B, positioned on the downstream side in the direction A, enables a reduction in pressure loss for the refrigerant in that section. Here,FIG. 2B only illustrates the surrounding vicinity of thedownstream port section 23B with thedischarge cover 25 removed, relating to thestationary end plate 21. The same applies toFIGS. 3A to 3F , described later. - The upstream side of the
upstream port section 23A communicates with a compression chamber PR formed between thestationary scroll 20 and the revolvingscroll 30. In addition, the downstream side of thedownstream port section 23B communicates with anejection port 27 of thedischarge cover 25 covering the top of thestationary scroll 20. - A
partitioning wall 40 is provided in thedownstream port section 23B. Thepartitioning wall 40 is formed ofpartitioning walls - The
partitioning wall 40 partitions thedownstream port section 23B into an outside area OA and an inside area IA, thus changing the natural frequency of thedownstream port section 23B. Thepartitioning walls downstream port section 23B. Symmetrically disposing thepartitioning wall 40 enables turbulence in the flow of the refrigerant in thedownstream port section 23B to be minimized. A gap G is provided between end portions E, E of thepartitioning walls partitioning walls downstream port section 23B passes through the refrigerant passage connecting the outside area OA, the gap G, and the inside area IA, and flows into theejection port 27 of thedischarge cover 25. - The
partitioning wall 40 is integrally formed with thedischarge cover 25 and is provided so that a tip of thepartitioning wall 40 is in contact with a surface of thestationary end plate 21. - The action and effect obtained by providing the
partitioning wall 40 are described later. - The revolving
scroll 30 is likewise provided with a revolvingend plate 31 having a round shape, and awrap 32 having a spiral shape originating from one face of the revolvingend plate 31. - A
boss 34 is provided on a back face of the revolvingend plate 31 of the revolvingscroll 30, and adrive bush 36 is assembled on theboss 34 through a bearing. Theeccentric pin 17A is fit into thedrive bush 36. As a result, the revolvingscroll 30 is eccentrically joined to a shaft center of themain shaft 17. As such, upon rotation of themain shaft 17, the revolvingscroll 30 rotates (revolves) with an eccentric distance from the shaft center of themain shaft 17 as a radius of revolution. - Here, an Oldham's ring (not illustrated) is provided between the revolving
scroll 30 and themain shaft 17 in order to restrain the rotation of the revolvingscroll 30 so that the revolvingscroll 30 does not rotate upon itself while revolving. - The wraps 22, 32 have a predetermined amount of eccentricity with respect to each other, engage with each other with a phase offset of 180°, and are in contact with each other at a plurality of positions according to a rotation angle of the revolving
scroll 30. Then, the compression chamber PR is formed with point symmetry with respect to a central portion (innermost circumferential portion) of the spirals of thewraps 22, 32. Also, as the revolvingscroll 30 revolves, the compression chamber is displaced gradually toward the inner circumferential side while decreasing in volume. Then, the refrigerant is maximally compressed at the central portion of the spirals. The compression chamber PR illustrated inFIG. 1 depicts this portion. - In the scroll-
type compressor mechanism 2, the volume of the compression chamber PR formed between the twoscrolls stationary scroll 20 and the revolvingscroll 30 is less on the inner circumferential side than the outer circumferential side.
Also, an end plate on an opposite side of the stepwise wraps is made to protrude inward to a greater extent at the inner circumferential side than the outer circumferential side. - The scroll-
type compressor 1 provided with the above-described configuration is subject to excitation of theelectric motor 12 and introduction of the refrigerant into thehousing 10 through theintake pipe 13. - Upon excitation of the
electric motor 12, themain shaft 17 rotates, thereby revolving the revolvingscroll 30 with respect to thestationary scroll 20. Then, the refrigerant is compressed in the compression chamber PR between the revolvingscroll 30 and thestationary scroll 20, and the refrigerant introduced into the low-pressure chamber 10A within thehousing 10 from theintake pipe 13 is taken in between the revolvingscroll 30 and thestationary scroll 20. Afterward, the refrigerant compressed in the compression chamber PR passes through theejection port 23 of thestationary end plate 21 and theejection port 27 of thedischarge cover 25 in the stated order and is ejected into the high-pressure chamber 10B, and is then further ejected to the outside from theejection pipe 14. As such, the intake, compression, and ejection of the refrigerant are continuously performed. - Next, the actions and effects obtained by providing the
partitioning wall 40 in thedownstream port section 23B are described. - The refrigerant compressed by the
stationary scroll 20 and the revolvingscroll 30 is ejected from the compression chamber PR to theupstream port section 23A, and passes through theupstream port section 23A and thedownstream port section 23B in the stated order. The refrigerant having passed through thedownstream port section 23B is ejected from theejection port 27 into the high-pressure chamber 10B. - The refrigerant ejected into the high-
pressure chamber 10B through this pathway produces a resonance at a frequency corresponding to each of the ejection ports. The production of this resonance causes a dramatic increase in amplitude of vibration of the ejection port, resulting in noise being increased. - As such, in the present embodiment, the internal space of the
downstream port section 23B is partitioned into the outside area OA and the inside area IA by providing thepartitioning wall 40 in thedownstream port section 23B. Doing so changes the natural frequency of thedownstream port section 23B relative to a case where thepartitioning wall 40 is not provided. Changing the natural frequency in this manner enables a reduction in sound of a desired frequency band. - Here, in the present embodiment, the reduction in sound may be applied to a desired frequency band by setting a length L of the
partitioning wall 40 to 1/2 the wavelength λ of the sound to be reduced. - The principles of sound reduction applied to the sound of a desired frequency are as follows.
-
- Determining the frequency f of the sound to be reduced enables the wavelength λ to be calculated from
Expression 1. Then, the length L of thepartitioning wall 40 is set to 1/2 of the wavelength λ thus calculated. - Here, there is a tendency such that the longer the length L of the
partitioning wall 40, the lower the frequency of the sound reduced, and conversely, the shorter the length of thepartitioning wall 40, the higher the frequency of the sound reduced. Moreover, not only the length L but also the height T of thepartitioning wall 40 may be subject to the tuning of thepartitioning wall 40. - In order to confirm the effect of the present embodiment, the relationship between frequency and amount of sound reduction was investigated using both a compressor provided with the
partitioning wall 40 and a compressor not provided with thepartitioning wall 40. The results are given inFIG. 5 . The amount of sound reduction is indicated on the vertical axis. A larger value indicates a greater amount of sound reduction. - As shown in
FIG. 5 , providing thepartitioning wall 40 for a frequency band of 1.6 kHz, for example, was found to reduce sounds by approximately 25 dB. Similarly, providing thepartitioning wall 40 was found to enable the promotion of sound reduction in the frequency band of from 4.0 kHz to 5.0 kHz. - Given the above results, providing the
partitioning wall 40 in thedownstream port section 23B was confirmed as being able to reduce sounds corresponding to 1.6 kHz and 4.1 kHz, which are sources of noise. - The embodiment has been described above as symmetrically providing the two
partitioning walls partitioning wall 40 may be added. Several examples are illustrated, with reference toFIGS. 3A to 3F . - For example, the
partitioning walls partitioning wall 40 in a C shape as illustrated inFIG. 3A . As such, the length L of the arc of thepartitioning wall 40 is increased, thus enabling a reduction in sound of a lower frequency. - In addition, as illustrated in
FIG. 3B , a center of symmetry C' of the partitioning wall 40 (40a, 40b) may be provided at a position having eccentricity with respect to the center C of thedownstream port section 23B. - In addition, as illustrated in
FIG. 3C , thepartitioning walls FIG. 3C , the respective distances from the center C to thepartitioning walls - In addition, as illustrated in
FIG. 3D , thepartitioning wall 40 may be provided as divided into three or more pieces (three inFIG. 3D ). Providing thepartitioning wall 40 in plurality enables the sound reduction effect to be increased. - In addition, as illustrated in
FIG. 3E , partitioning walls 40A, 40C, 40B, 40D may be doubly provided with spacing in the radial direction. In such a case, thedownstream port section 23B is partitioned into a plurality of areas. That is, each of the partitioning walls 40A to 40D partitions thedownstream port section 23B into an inside area and an outside area in terms of the radial direction. - The overall length L of the arc of the
partitioning wall 40 is increased, which is effective in a case where an increase in the sound reduction effect is desired. Thepartitioning walls 40 are not limited to being provided doubly, and may also be provided triply or more. - Furthermore, as illustrated in
FIG. 3F , thepartitioning wall 40 may have a spiral shape. Thepartitioning wall 40 having the spiral shape partitions thedownstream port section 23B into an inside area surrounded by thepartitioning wall 40 in the radial direction and an outside area of the outermost circumference of thepartitioning wall 40. - The length L of the
partitioning wall 40 may be increased with thepartitioning wall 40 having the spiral shape. As such, this configuration is effective for reducing sound of a lower frequency. - Here, the refrigerant flowing in from the
upstream port section 23A passes through thedownstream port section 23B while flowing in a spiral along thepartitioning wall 40, and is ejected to theejection port 27. - The shapes illustrated in
FIGS. 3A to 3F may be combined as appropriate. - In addition, no limitation is intended to the arc shape (or oval arc shape) of the horizontal cross-section. For example, the
partitioning wall 40 may have any of various shapes, including a linear shape, a U shape, and the like. Furthermore, in a case where a plurality, for example, two, of thepartitioning walls - Next, there is a need to provide the
partitioning wall 40 with rigidity in order to withstand the pressure from the refrigerant passing through theejection port 23. Here, the term rigidity is used entirely in reference to a joining portion with thedischarge cover 25. - In the present embodiment, as illustrated in
FIG. 4A , the end portions E, E of thepartitioning walls rib 41 extending toward the outside in the radial direction. Providing theseribs 41 improves the rigidity of thepartitioning walls ribs 41 have the same height as thepartitioning wall 40, and equal thickness in the height direction. However, no such limitation is intended provided that the effect of rigidity improvement is obtained. - The
ribs 41 serve to form a throttle, in addition to serving the function of rigidity improvement. That is, providing theribs 41 causes aport 44 of the refrigerant from the inside area IA to the outside area OA to be throttled. As such, the effect of sound reduction is increased. - In addition to the
rib 41, as illustrated inFIG. 4B , arib 42 may also be provided at any position between the end portions E, E, for example at a median position. Doing so provides further improvement to the rigidity of thepartitioning wall 40, and also forms apartitioning wall 50 having a length of 1/2 L between therib 41 and therib 42. As such, sound of a high frequency may also be reduced. - In order to improve the rigidity, as illustrated in
FIG. 4C , apartitioning wall 43 having a wave-shaped horizontal cross-section may be applied. Thepartitioning wall 43 has portions corresponding to peaks and troughs of the wave shape producing a similar effect to therib 41. Further, these portions are present in plurality, resulting in thepartitioning wall 43 having higher rigidity. - The embodiments have been described above. However, configurations described in the above embodiments can be selected as desired, or can be changed to other configurations as necessary.
- For example, provided that the
downstream port section 23B is partitioned into the outside area OA and the inside area IA, thepartitioning wall 40 is not limited to being integrally formed with thedischarge cover 25. For example, thepartitioning wall 40 may also be integrally formed with thestationary end plate 21, or may be separately manufactured from thestationary end plate 21 and thedischarge cover 25 and fixed to thedownstream port section 23B at a predetermined position using an appropriate approach. - Furthermore, the tip of the
partitioning wall 40 do not have to be in contact with thestationary end plate 21. The tip of thepartitioning wall 40 may be separated from thestationary end plate 21, provided that the effect of noise reduction is obtained by the partitioning wall. -
- 1
- Scroll-type compressor
- 2
- Scroll-type compressor mechanism
- 10
- Housing
- 10A
- Low-pressure chamber
- 10B
- High-pressure chamber
- 12
- Electric motor
- 13
- Intake pipe
- 14
- Ejection pipe
- 15
- Stator
- 16
- Rotor
- 17A
- Main shaft
- 17A
- Eccentric pin
- 18
- Upper bearing
- 19
- Lower bearing
- 20
- Stationary scroll
- 21
- Stationary end plate
- 22, 32
- Wrap
- 23
- Ejection port
- 23A
- Upstream port section
- 23B
- Downstream port section
- 25
- Discharge cover
- 27
- Ejection port
- 30
- Revolving scroll
- 31
- Revolving end plate
- 34
- Boss
- 36
- Drive bush
- 40, 40a to 40d, 43
- Partitioning wall
- 41, 42
- Rib
- 44
- Port
- 101
- Housing body
- 102
- Housing top
- 190
- Accommodating space
- A
- Direction
- OA
- Outside area
- IA
- Inside area
- C, C'
- Center
- G
- Gap
- PR
- Compression chamber
Claims (7)
- A scroll-type compressor (1) comprising:a revolving scroll (30) rotatably connected to an eccentric shaft portion of a main shaft (17);a stationary scroll (20) facing the revolving scroll (30) to form a compression chamber (PR) compressing a refrigerant, and having an ejection port (23) on an end plate (21), the ejection port (23) ejecting the compressed refrigerant toward a high-pressure chamber (10B); anda discharge cover (25) covering the ejection port (23);the ejection port (23) including:an upstream port section (23A) provided on an upstream side in an inflow direction of the refrigerant; anda downstream port section (23B) provided on a downstream side in the inflow direction of the refrigerant, the downstream port section (23B) having a greater volume than the upstream port section (23A);characterised in that the downstream port section (23B) includes:partitioning wall(s) (40) partitioning an interior of the downstream port section (23B) into a plurality of areas; anda refrigerant passage passing the refrigerant through the plurality of areas.
- The scroll-type compressor (1) according to claim 1, wherein
the downstream port section (23B) has a round cavity formed therein, and
one or several partitioning wall(s) (40) having a horizontal cross-section in an arc shape is/are provided along a circumferential direction of the downstream port section (23B). - The scroll-type compressor (1) according to claim 1 or 2, wherein the partitioning wall(s) (40) is/are integrally formed with the discharge cover (25).
- The scroll-type compressor (1) according to any one of claims 1 to 3, wherein
the partitioning wall(s) (40) with a rib (41,42) is/are integrally formed with the discharge cover (25). - The scroll-type compressor (1) according to any one of claims 1 to 4, wherein
the partitioning wall(s) (40) is/are provided so as to have a tip in contact with a surface of the end plate (21). - The scroll-type compressor (1) according to any one of claims 1 to 5, wherein
the partitioning wall(s) (40) (40) is/are symmetrically arranged with respect to a central portion of the downstream port section (23B) serving as a center. - The scroll-type compressor (1) according to any one of claims 1 to 5, wherein
the partitioning wall(s) (40) is/are symmetrically arranged with respect to a position having eccentricity relative to a central portion of the downstream port section (23B) serving as a center.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2013135496A JP6130748B2 (en) | 2013-06-27 | 2013-06-27 | Scroll compressor |
PCT/JP2014/003106 WO2014208029A1 (en) | 2013-06-27 | 2014-06-11 | Scroll-type compressor |
Publications (3)
Publication Number | Publication Date |
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EP3015709A1 EP3015709A1 (en) | 2016-05-04 |
EP3015709A4 EP3015709A4 (en) | 2016-06-22 |
EP3015709B1 true EP3015709B1 (en) | 2017-03-01 |
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EP14816917.0A Active EP3015709B1 (en) | 2013-06-27 | 2014-06-11 | Scroll-type compressor |
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EP (1) | EP3015709B1 (en) |
JP (1) | JP6130748B2 (en) |
CN (1) | CN105190041B (en) |
WO (1) | WO2014208029A1 (en) |
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US11493040B2 (en) | 2018-06-29 | 2022-11-08 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor |
CN110657097B (en) * | 2018-06-29 | 2024-08-23 | 谷轮环境科技(苏州)有限公司 | Damping device for exhaust valve in compressor, exhaust valve assembly and compressor |
CN111441951B (en) * | 2019-01-17 | 2024-07-26 | 谷轮环境科技(苏州)有限公司 | Compressor with a compressor body having a rotor with a rotor shaft |
CN117703717B (en) * | 2024-02-05 | 2024-05-03 | 亚新科智能汽车技术(仪征)有限公司 | Air compressor with air inlet silencing function |
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JPH0482391U (en) * | 1990-11-29 | 1992-07-17 | ||
JP3264034B2 (en) * | 1993-04-26 | 2002-03-11 | 松下電器産業株式会社 | Scroll compressor |
US5474431A (en) * | 1993-11-16 | 1995-12-12 | Copeland Corporation | Scroll machine having discharge port inserts |
JPH08319963A (en) * | 1995-03-22 | 1996-12-03 | Mitsubishi Electric Corp | Scroll compressor |
US5921761A (en) * | 1997-04-17 | 1999-07-13 | Copeland Corporation | Scroll machine with discharge duct |
JP2001132666A (en) * | 1999-11-09 | 2001-05-18 | Hitachi Ltd | Displacement compressor |
WO2007027168A1 (en) * | 2005-08-29 | 2007-03-08 | Carrier Corporation | Compressor muffler |
JP5758112B2 (en) * | 2010-12-07 | 2015-08-05 | 三菱重工業株式会社 | Scroll compressor |
CN202417950U (en) * | 2011-12-15 | 2012-09-05 | 上海日立电器有限公司 | Exhaust device for scroll compressor |
CN202937456U (en) * | 2012-09-21 | 2013-05-15 | 珠海格力电器股份有限公司 | High-low pressure division board and scroll compressor with amortization function |
-
2013
- 2013-06-27 JP JP2013135496A patent/JP6130748B2/en active Active
-
2014
- 2014-06-11 WO PCT/JP2014/003106 patent/WO2014208029A1/en active Application Filing
- 2014-06-11 EP EP14816917.0A patent/EP3015709B1/en active Active
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JP2015010519A (en) | 2015-01-19 |
CN105190041B (en) | 2017-06-09 |
JP6130748B2 (en) | 2017-05-17 |
CN105190041A (en) | 2015-12-23 |
EP3015709A4 (en) | 2016-06-22 |
EP3015709A1 (en) | 2016-05-04 |
WO2014208029A1 (en) | 2014-12-31 |
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