EP3828413B1 - Pompe à chaleur comprenant un silencieux - Google Patents

Pompe à chaleur comprenant un silencieux Download PDF

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Publication number
EP3828413B1
EP3828413B1 EP19212130.9A EP19212130A EP3828413B1 EP 3828413 B1 EP3828413 B1 EP 3828413B1 EP 19212130 A EP19212130 A EP 19212130A EP 3828413 B1 EP3828413 B1 EP 3828413B1
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EP
European Patent Office
Prior art keywords
port
heat pump
pressure pulsation
pulsation reducing
pump according
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.)
Active
Application number
EP19212130.9A
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German (de)
English (en)
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EP3828413A1 (fr
Inventor
Josef Cesky
Pavel Skopovy
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Europe NV
Daikin Industries Ltd
Original Assignee
Daikin Europe NV
Daikin Industries Ltd
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Publication date
Application filed by Daikin Europe NV, Daikin Industries Ltd filed Critical Daikin Europe NV
Priority to EP19212130.9A priority Critical patent/EP3828413B1/fr
Publication of EP3828413A1 publication Critical patent/EP3828413A1/fr
Application granted granted Critical
Publication of EP3828413B1 publication Critical patent/EP3828413B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound

Definitions

  • the present invention relates to a heat pump comprising a muffler, for example a heat pump to be used in an air conditioner.
  • a heat source heat exchanger such as heat pumps used in air conditioners
  • a compressor In heat pumps, such as heat pumps used in air conditioners, a heat source heat exchanger, a compressor, a utilisation side heat exchanger and an expansion valve are connected by refrigerant piping.
  • the compressor often contains an electric motor, which produces noise. This noise can be transmitted via the refrigerant, for example to the room to be air conditioned where it will be deemed disturbing.
  • air conditioners are frequently used in domestic and work environments, where noise should be kept to a minimum so as to not disturb sleep or to distract employees.
  • FIG. 1 A typical prior art muffler 10' is shown in Figure 1 .
  • the left part of that figure shows a cross-section along the length of the muffler 10' whilst the right part of that figure shows a cross-section perpendicular to the length of the muffler 10'.
  • This muffler 10' is provided as part of the refrigerant piping so that refrigerant can be led through it via a first port 11' and an outlet port 12'.
  • Noise sound waves carried by the refrigerant entering through the first port 11' will (partially) impinge on the enlarged section A of the muffler 10'. This reflection will cause them to lose some of their energy, which will lead to an attenuation of the noise.
  • the area S1 of the enlarged section A is determinative in the attenuation of the noise. Put simply, the larger it is, the stronger the attenuation. However, one cannot enlarge this area indefinitely.
  • the attenuation of the noise also depends on the length of the muffler 10'.
  • Typical noise from a compressor has a frequency of 50 Hz to 400 Hz. This leads to a wavelength of from about 1 to about 4 m.
  • the muffler should be larger than that wavelength or should at least have a length of half that wavelength, which would lead to mufflers having a length of between about 1 to 4 m. It is clear that such mufflers would be too long for being installed in a lot of domestic and work environments.
  • JP H05 322379 A discloses features falling under the preamble of claim 1.
  • US 4 330 239 A is further prior art.
  • the present invention aims to solve or at least alleviate some of the problems mentioned above.
  • a heat pump comprises a heat source heat exchanger, a compressor, a utilisation side heat exchanger and an expansion valve connected by refrigerant piping.
  • the heat pump comprises a muffler which has first and second ports (inlet and outlet, respectively) and a pressure pulsation reducing space.
  • first and second ports we mean any inlet/outlet which can be used for introducing a refrigerant into the pressure pulsation reducing space or through which a refrigerant can be led out of that space.
  • the pressure pulsation reducing space is an enclosed space.
  • the shape of the pressure pulsation reducing space is nonlimited and could, in principle, be any sort of shape as long as a space is enclosed. In most practical situations, it will have the shape of a closed cylinder (i.e. a cylinder which is blind at both ends).
  • the first and the second ports are respectively connected to the refrigerant piping and are also in communication with the pressure pulsation reducing space. Through those ports, a fluid (such as the refrigerant) can flow into the pressure pulsation reducing space and can then flow out of it.
  • a fluid such as the refrigerant
  • a first centre axis of the first port and a second centre axis of the second port are oriented so that a flow direction of the refrigerant flowing in through the first port and exiting the pressure pulsation reducing space via the second port changes at least once between the first port and the second port.
  • the centre axis of a port is defined as the axis at which the refrigerant leaves the port and flows into the pressure pulsation reducing space. In most cases, it will be the centre axis of the pipe constituting the port. In other cases, it may be the centre axis of one opening provided at the end of or in the shell of the pipe constituting the port.
  • the refrigerant By enforcing this change in direction of the refrigerant flow, the refrigerant needs to lose energy thanks to it having to change its direction. This then means that some energy is lost, which, in turn, reduces the noise, in particular at audible frequencies. This reduction in noise volume occurs regardless of the frequency. Also, since there will almost certainly be reflections of the refrigerant at the housing of the pressure pulsation reducing space, those reflections will lead to a significant energy loss of the sound wave, thus reducing the noise volume. Further, due to the reflections, an interference phenomenon occurs, which tends to reduce the sound volume which is transmitted through the muffler. The energy which is lost will be converted into thermal energy (heat).
  • the pressure pulsation reducing space has a cylindrical portion, wherein a third centre axis of the cylindrical portion is non- parallel to the first centre axis of the first port and/or the second centre axis of the second port.
  • the first centre axis extends along a chord of the cylindrical portion and the second centre axis extends radially.
  • the first and second centre axes are parallel to each other and offset. This means that a particularly high number of reflections occurs, so that the noise attenuation is particularly significant.
  • first and second centre axes are offset in two directions. That is, when viewed along the longitudinal direction of the pressure pulsation reducing space, the first and second centre axis are at different positions. By this feature, a large number of reflections is achieved.
  • first and second centre axes are at an angle relative to each other. This, again, leads to a comparatively high number of reflections and, accordingly, a significant attenuation whilst giving greater flexibility in the design of the muffler.
  • first and second centre axis are perpendicular to each other. By them being arranged at a right angle, the reflections are particularly strong, so that the noise attenuation is particularly pronounced.
  • the pressure pulsation reducing space has a circular cross-section, with the cross-section being perpendicular to the longitudinal axis of the pressure pulsation reducing space.
  • a circular cross-section leads to a significant number of reflections, which is beneficial for attenuating noise. This feature could, for example, be realised by a cylindrical or spherical pressure pulsation reducing space.
  • the diameter of the pressure pulsation reducing space is larger than the diameter of the first port and/or the second port.
  • the cross-sectional area of the pressure pulsation reducing space will be larger than that of the first and the second port, a significant number of reflections will occur, which is, again, beneficial for reducing the sound volume of the noise.
  • the third centre axis is perpendicular to the first centre axis and/or the second centre axis. A large number of reflections occurs in such a case, which attenuates the noise.
  • first and the second port each comprise a pipe having opposite first and second ends, where the first end is connected to the refrigerant piping and where the second end is located within the pressure pulsation reducing space, compared with the second end being provided in the wall of the pressure pulsation reducing space, without extending into that pressure pulsation reducing space. I.e., the second end is located in the interior of the pressure pulsation reducing space.
  • an opening of the pipes at the second end has a smaller cross-sectional area than an opening at the first end.
  • the second end is closed and at least one opening is provided in a shell of the pipe adjacent the second end. Again, a change of direction of the refrigerant is enforced, thanks to it having to squeeze through the openings, which reduces the noise volume.
  • a plurality of openings are provided in the shell of the pipe adjacent the second end. By such a plurality of openings, the refrigerant enters in a variety of directions, which reduces the noise.
  • the second port opens into the pressure pulsation reducing space in a bottom portion of the pressure pulsation reducing space. That is, the heat pump is to be arranged so that the second end of the second port is arranged in a bottom portion (for example the bottom half or the bottom third of the pressure pulsation reducing space) rather than a top portion of the pressure pulsation reducing space.
  • the reason for this is that, when in use, oil will often accumulate in the pressure pulsation reducing space.
  • Figure 2 shows a muffler for use in a heat pump according to a first embodiment.
  • the left drawing shows a longitudinal cross-section whilst the right drawing shows a cross-section taken perpendicular to the longitudinal direction.
  • the muffler has a first port 11 and a second port 12 and a cylindrical pressure pulsation reducing space 10 into which the first and the second ports 11, 12 extend with their second ends, with their first ends being outside of the pressure pulsation reducing space 10.
  • the pressure pulsation reducing space 10 has a roughly cylindrical shape, with tapered portion ends 18 and tube-like stubs 19 at the outer ends of the tapered portions 18.
  • the tapering is provided at each longitudinal end of a cylindrical space 15.
  • the first and second ports 11, 12 extent parallel to each other but are displaced relative to each other - i.e., they are not provided at the same position when viewed along the third centre axis 16 of the cylindrical space 15.
  • first and second centre axes 13, 14 extend perpendicular to the third centre axis 16 of the cylindrical portion 15. Since any sound entering via the first port 11 has to undergo a change of direction before it leaves through the second port 12 (and most likely several such changes of direction), the noise volume will be attenuated.
  • the muffler should be arranged in the configuration shown in in Figure 2 , i.e. with the first and second ports 11, 12 pointing upwards (or, alternatively, horizontal). This is because during use, oil will accumulate at the bottom of the pressure pulsation reducing space 10.
  • Figure 3 shows the configuration of a muffler for use in a heat pump according to the second example.
  • a first port 11 and a second port 12 with respective first and second centre axes 13, 14.
  • the pressure pulsation reducing space 10 uses a simple pipe as the cylindrical portion 15 and has two closed ends (stubs) 19 which extend past the points where the first and second ports 11, 12 are connected to the cylindrical portion 15.
  • the first and second ports 11, 12 are arranged so that their first and second centre axes 13, 14 are perpendicular to the third centre axis 16 of the cylindrical portion 15.
  • Such a device is easier to manufacture than the more complicated muffler according to Figure 2 .
  • the diameter of the cylindrical portion 15 is greater than or equal to the diameter of the first port 11 (which serves as the inlet).
  • the diameter of the first port 11 is greater than the diameter of the second port 12. This also reduces the noise volume.
  • Figure 4 shows a muffler for use in a heat pump according to a third embodiment.
  • a cylindrical portion 15 having cone-shaped tapered portions 18 leading into closed pipe stubs 19 constitutes the pressure pulsation reducing space 10.
  • first and second ports 11, 12 are provided so as to extend into the pressure pulsation reducing space 10.
  • the first port 11 has a curvature along its length and has a hole 22 in its sidewall which, in addition to an opening at the second end of that port, allows for a refrigerant to enter into the pressure pulsation reducing space 10.
  • the second port 12 has a tapered second end 12' which is closed and has also provided in its side wall several holes 21. By the bend in the first port 11, and by the holes 21, 22, a change in direction of the refrigerant is enforced, which reduces the sound volume.
  • FIG. 5 shows a muffler for use in a heat pump according to the fourth example.
  • the pressure pulsation reducing space 10 comprises a cylindrical portion 15 which has tapered portions 18 at either end. One of those tapered portions 18 leads into a closed pipe stub 19, but the respective other tapered portion 18 leads to the second port 12.
  • the first port 11 is provided so as to extend into the cylindrical portion 15 and extends along a radial direction and past the centre of the cylindrical portion 15 when viewed perpendicularly to both the third centre axis 16 and to the respective one of the first and second centres axis 11, 12.
  • the first centre axis 13 of the first port is at right angles to the second centre axis 14 of the second port 12.
  • Figure 6 shows a muffler for use in the fifth embodiment of the present invention.
  • a first port 11 and a second port 12 extend into the cylindrical portion 15 such that the first and second centre axes 13, 14 are at right angles relative to the third centre axis 16 of the cylindrical portion 15.
  • the pressure pulsation reducing space 10 comprises the cylindrical portion 15 which is joined at either longitudinal end to tapered portions 18 which lead into closed pipe stubs 19. Both the first and the second port 13, 14 extend past the centre of the cylindrical portion 15 when viewed perpendicularly to both the third centre axis 16 and to the respective one of the first and second centres axis 11, 12.
  • Figure 7 shows two mufflers for use in a heat pump according to the sixth embodiment.
  • Figure 7a shows a first variant of a muffler which can be used in that embodiment.
  • a pressure pulsation reducing space 10 comprises a cylindrical portion 15 which is joined, at either longitudinal end, to tapered portions 18 leading into closed pipe stubs 19.
  • a single pipe constituting the first port 11 extends from one side whilst, from the respective other side, two pipes extend into the cylindrical portion 15. Those two pipes form the second port 12.
  • the second ends of the pipe of the first port 11 and of the pipes of the second port 12 are arranged such that they extend past each other and past the centre of the cylindrical portion when viewed perpendicularly to both the third centre axis 16 and to the respective one of the first and second centres axes 13, 14. In that way, a refrigerant which enters via the first port 11 will need to flow backwards before it can leave via the second ports 12. This enforced change of direction reduces the noise volume.
  • FIG. 7b shows the muffler according to a second variant.
  • a pressure pulsation reducing space 10 comprises a cylindrical portion 15 which is joined, at either longitudinal end, to tapered portions 18.
  • One of those tapered portions 18 leads into a pipe stub 19 whilst the respective other tapered portion 18 leads into a bent pipe 24 which is then connected to the cylindrical portion 15 so that its end extends through that wall and opens towards the interior of the cylindrical portion 15.
  • the second end of the first pipe 11 extends past the second outlet of the second port 12 when viewed perpendicularly to the third centre axis 16 and to the respective one of the first and second centres axis 13, 14, so that, similarly to what was discussed previously, the refrigerant entering via the first port 11 needs to change direction at least once, again reducing the sound volume.
  • Figure 8 shows a muffler for use in a heat pump according to the seventh example.
  • a cylindrical portion 15 is provided which is joined at either longitudinal end to tapered portions 18 leading into pipe stubs 19. Both pipe stubs 19 are closed.
  • a first port 11 and a second port 12 extend into the pressure pulsation reducing space 10.
  • the first centre axis 13 of the first port 11 and the second centre axis 14 of the second port 12 are provided at an acute angle relative to the third centre axis 16 of the cylindrical portion 15 when viewed perpendicularly to both the third centre axis 16 and to the respective one of the first and second centres axis 13, 14, as shown in Figure 8a ).
  • the first port 11 and the second port 12 have their respective first centre axis 13 and second centre axis 14 arranged at an angle relative to each other, as is seen in figure 8b ). By having such an angle, the reflections are more significant, which reduces the noise volume.
  • first and second ports tune the mufflers by adjusting their length and their diameter, by adjusting the depth of penetration and the position of the first and second ports, and by adjusting the second ends of the first and second ports (e.g. their diameter, whether they are closed, their shape, ). It is also possible to modify the muffler by changing the respective arrangement of the first and second ports - in particular whether they are arranged radially or tangentially (along the direction of a chord) or whether they are arranged at some other angle. It is also possible to insert further reflective and absorbing surfaces into the muffler, and one can use several first and second ports.
  • FIG. 9 shows an air conditioning apparatus 1 which is a heat pump according to the invention.
  • the air conditioning apparatus 1 includes a refrigerant circuit 7.
  • the refrigerant circuit 7 is configured so that a compressor 2 for compressing a refrigerant, an indoor heat exchanger 3, an outdoor heat exchanger 4, and a four-way switch valve 5 are connected via a refrigerant piping 6.
  • the four-way switch valve 5 switches the flow of refrigerant compressed by the compressor 2 to either the indoor heat exchanger 4 or the outdoor heat exchanger 3.
  • the air conditioning apparatus 1 further includes a pressure pulsation reducing component (muffler) 10, which is the muffler according to one of the preceding Figures.
  • the muffler 10 is provided between the four-way switch valve 5 and the indoor heat exchanger 3.
  • the muffler 10 reduces pressure pulsations inside the refrigerant circuit 7 that are generated by the compressor 2.
  • an electromagnetic expansion valve 8 is connected to the refrigerant piping 6.
  • the outdoor heat exchange 4, expansion valve 8, muffler 10, heat pump 2, four-way switch valve 5, and parts of the refrigerant piping 6 form an outdoor unit 9 of the air conditioning apparatus 1.
  • the muffler 10 is provided as part of the outdoor unit 9 and is provided directly between the four-way switch valve 5 and the indoor unit 3, its position is not limited to this. As long as the muffler 10 is provided somewhere on the refrigerant piping 6, it will reduce pressure pulsation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (12)

  1. Pompe à chaleur comprenant
    un échangeur de chaleur source de chaleur (3), un compresseur (2), un échangeur de chaleur côté utilisation (4) et un détendeur (8) reliés par des tubes de réfrigérant (6) ; et
    un silencieux ayant des premier (11) et deuxième (12) orifices et un espace de réduction de pulsations de pression (10), l'espace de réduction de pulsations de pression (10) étant en communication fluidique avec au moins le premier orifice (11) et le deuxième orifice (12), dans laquelle les premier (11) et deuxième (12) orifices sont respectivement reliés aux tubes de réfrigérant (6),
    dans laquelle un premier axe central (13) du premier orifice (11) et un deuxième axe central (14) du deuxième orifice (12) sont orientés de telle façon qu'une direction d'écoulement du réfrigérant circulant dans les tubes de réfrigérant (6) change au moins une fois entre le premier orifice (11) et le deuxième orifice (12),
    l'espace de réduction de pulsations de pression (10) présente une partie cylindrique (15), dans laquelle un troisième axe central (16) de la partie cylindrique (15) est non parallèle au premier axe central (13) du premier orifice (11) et/ou au deuxième axe central (14) du deuxième orifice (12),
    caractérisé en ce que
    le premier axe central (13) du premier orifice (11) s'étend le long d'une corde de la partie cylindrique et le deuxième axe central (14) du deuxième orifice (12) s'étend radialement.
  2. Pompe à chaleur selon la revendication 1, dans laquelle les premier (13) et deuxième (14) axes centraux sont parallèles et décalés.
  3. Pompe à chaleur selon la revendication 2, dans laquelle les premier (13) et deuxième (14) axes centraux sont décalés dans deux directions.
  4. Pompe à chaleur selon la revendication 1, dans laquelle les premier (13) et deuxième (14) axes centraux sont inclinés.
  5. Pompe à chaleur selon la revendication 4, dans laquelle les premier (13) et deuxième (14) axes centraux sont perpendiculaires.
  6. Pompe à chaleur selon l'une quelconque des revendications précédentes, dans laquelle l'espace de réduction de pulsations de pression (10) présente une section transversale circulaire.
  7. Pompe à chaleur selon la revendication 6, dans laquelle le diamètre de l'espace de réduction de pulsations de pression (10) est plus grand que le diamètre du premier orifice (11) et/ou du deuxième orifice (12).
  8. Pompe à chaleur selon l'une quelconque des revendications précédentes, dans laquelle le premier orifice (11) et/ou le deuxième orifice (12) comprennent un tube ayant des première et seconde extrémités opposées, dans laquelle la première extrémité est reliée aux tubes de réfrigérant et la seconde extrémité se situe à l'intérieur de l'espace de réduction de pulsations de pression (10).
  9. Pompe à chaleur selon la revendication 8, dans laquelle une ouverture au niveau de la seconde extrémité présente une aire de section transversale plus petite qu'une ouverture au niveau de la première extrémité.
  10. Pompe à chaleur selon la revendication 8, dans laquelle la seconde extrémité est fermée et au moins une ouverture est ménagée dans une chemise du tube à côté de la seconde extrémité.
  11. Pompe à chaleur selon la revendication 8, 9 ou 10, dans laquelle une pluralité d'ouvertures sont ménagées dans la chemise du tube à côté de la seconde extrémité.
  12. Pompe à chaleur selon l'une quelconque des revendications précédentes, dans laquelle le deuxième orifice (12) débouche dans l'espace de réduction de pulsations de pression (10) dans une partie inférieure de l'espace de réduction de pulsations de pression (10).
EP19212130.9A 2019-11-28 2019-11-28 Pompe à chaleur comprenant un silencieux Active EP3828413B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19212130.9A EP3828413B1 (fr) 2019-11-28 2019-11-28 Pompe à chaleur comprenant un silencieux

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19212130.9A EP3828413B1 (fr) 2019-11-28 2019-11-28 Pompe à chaleur comprenant un silencieux

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EP3828413A1 EP3828413A1 (fr) 2021-06-02
EP3828413B1 true EP3828413B1 (fr) 2023-03-22

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Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5044959U (fr) * 1973-08-24 1975-05-07
US4330239A (en) * 1979-10-10 1982-05-18 Tecumseh Products Company Compressor muffler
JPH05322379A (ja) * 1992-05-28 1993-12-07 Hitachi Ltd 空気調和機の冷媒分配器
JPH09250845A (ja) * 1996-03-19 1997-09-22 Fujitsu General Ltd 冷凍サイクル
JP2004218934A (ja) * 2003-01-15 2004-08-05 Mitsubishi Electric Corp 膨張形マフラー及びそれを用いた冷凍サイクル回路、並びにその製造方法
JP2008045778A (ja) 2006-08-11 2008-02-28 Daikin Ind Ltd 空気調和装置
JP4983158B2 (ja) * 2006-08-30 2012-07-25 ダイキン工業株式会社 冷凍装置

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