• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    SOUND DAMPER FOR A BODY THAT MOLDS A CAVITY, IN TUBE SHAPE.The present invention relates to the refrigerant circuit of a refrigeration system with a tube-shaped body (2), into which a sound damper (1) is inserted, depending on what the body (2) forms. cavity (3) and as a result of which the sound damper (1) is designed as an insert (26) which is inserted into the cavity (3) of the tube-shaped body (2) and as a function of what the insert (26 ) delimits at least one resonator chamber (5, 6, 7, 8) and a flow channel (4) that is connected to the resonator chamber (5, 6, 7, 8) through a connection channel (19, 19 ' , 20, 20 ', 21, 21', 22, 22 ').
    公开号:BR112012008931A2
    申请号:R112012008931-5
    申请日:2010-10-04
    公开日:2020-09-24
    发明作者:Dominik Kempf；Olaf Emmerich；Denny Liers
    申请人:Ti Automotive Engineering Centre (Heidelberg) Gmbh；
    IPC主号:
    专利说明:

    Descriptive Report of the Invention Patent for "AMORTE- SOUNDER OF A BODY THAT MOLDS A CAVITY, IN THE TUBE SHAPE".
    FIELD OF THE INVENTION The present invention relates to a refrigerant circuit of a refrigeration system with a tube-shaped body, into which a sound damper is inserted.
    A resonating sound damper for tubes is known from DE 43 27 562 A1, for example. A sound damper for tubes through which a flow of hot gases having multiple concentrically located sound damping chambers is known from this publication. DE 196 47 425 A1 describes an acoustic resonator f having multiple resonant chambers. The resonating chambers can be located along the inner circumference or on the outer circumference of the tube.
    Another sound absorber having resonant chambers located on the outer circumference of the tube is known from DE 101 02 040 A1.
    The aforementioned sound absorbers have the disadvantage of being complex and expensive to manufacture. In addition, they require a large installation space that is often not available, particularly in applications for the automobile industry.
    DE 10 2004 029 221 A1 describes a sound damper for a combustion engine air intake system.
    The object of the present invention is to improve the acoustic insulation of a refrigeration system. This objective is achieved with a refrigerating circuit of a refrigeration system with a tube-shaped body, into which a sound damper is inserted, depending on what the body forms a cavity and depending on what the sound damper. sound is conceived as an
    serto that is inserted into the body cavity in the form of a tube and depending on what the insert delimits at least one resonating chamber and a flow channel that is connected to the resonator channel through a connection channel.
    This design allows effective noise absorption, using the principle of acoustic resonator. The volume of gas enclosed in the resonator chamber is connected to the flow channel via the preferably narrow connection channel. A mechanical mass-spring system having a distinct natural resonance occurs due to the elasticity of the gas volume inside the resonator chamber in combination with the inert mass of the gas located in the connection channel.
    : The occurrence of noise can be effectively reduced due to this natural resonance. When the frequency of the noise source is known, the natural frequency of the resonating chamber can be adjusted to it.
    In order to allow noise absorption in different frequency bands, multiple resonant chambers, each having different natural frequencies, can be provided. In accordance with the present invention, the sound softener is designed as an insert, the insert forming at least one resonating chamber and the flow channel. In this way, the sound damper is manufactured in a particularly easy way. It is sufficient to place the insert in the body in the form of a tube. Further adaptations to the tube-shaped body are not absolutely necessary. In addition, the sound damper requires no additional installation space on the outside of the tube-shaped body. In this way, assembly can be done in a particularly easy way, since the sound damper is manufactured separately and only needs to be inserted into the body in the form of a tube. The manufacturing costs are also low, due to the design of the sound absorber as an insert. A sound damper of this type is particularly suitable for pipe-shaped bodies through which at least partially a gas flows. The sound damper is particularly suitable for closed loop systems, such as cooling circuits. The insert is inserted into a refrigerant circuit of a
    F 3/12 refrigeration in order to effectively dampen compressor noise. The sound absorber is particularly suitable for mobile cooling systems, for example, in a motor vehicle. The sound damper, according to the invention, has a tube-shaped body that is integrated into the refrigerant circuit of a cooling system. The tube-shaped body can have a rigid design or a flexible design. The tube-shaped body is advantageously a flexible hose made of plastic, for example.
    According to an advantageous embodiment of the present invention, it is provided that the insert has a dividing wall that forms the flow channel and separates it from at least one resonating chamber. The "dividing wall can be formed, in this case, by a section of the insert that forms an inner tube. In this way, a sound damper is obtained, which can be easily manufactured and assembled. The inner tube forms the flow channel. inside the sound absorber. It can be placed coaxially in the tube-shaped body. The inner tube can have a rounded or angled cross section. The flow channel is preferably located inside the inner tube, while that at least one resonator chamber is formed on the outside of the inner tube, in the space formed between the inner tube and the tube-shaped body.
    An internal cross-sectional area of the inner tube advantageously changes in the axial direction of the insert. This can be achieved, in particular, in such a way that the inner tube, which starts from an entrance area in cross section at an entrance of the sound damper, narrows in an area of cross section intermediate and expands from there to an exit area in cross section at the exit of the sound damper. In this way, the space for the resonating chamber or resonating chambers can be created using the insert without having to modify the tube-shaped body. However, a low resistance to the flow of a gas flowing through the flow channel can be achieved. This resistance to flow is kept particularly low when the change in the internal area in cross section in the axial direction does not occur suddenly. This can be achieved through a conical design of the inner tube, at least in some sections. When the cross-sectional entry area and the cross-sectional exit area of the sound absorber essentially correspond to the cross-sectional area of the tube-shaped body, additional adjustments of the insert or the tube-shaped body are not necessary in order to guide the fluid into the flow channel. The inner tube advantageously fits tightly over the tube-shaped body in the sound absorber inlet and outlet areas.
    An advantageous embodiment of the present invention provides that the insert has at least one net, which points outwards, to fit over the inner wall of the body in the form of a tube, at least one re: delimiting the resonating chamber in an axial direction of the insert. The mesh can be located on the outside of the inner tube and forms a spacer.
    f In this way, the space required for the resonator chamber is formed between the inner tube and the tube-shaped body. The net can be designed as a circumferential ring-shaped frieze, for example. In addition, this network is advantageous when the sound damper is used in a curved tube-shaped body. With the mesh fitting over the tube-shaped body, the insert is able to adapt to the radius of curvature of the tube-shaped body, even if it is manufactured without a curvature or with a different curvature.
    A particularly compact configuration results when the network separates two adjacent resonator chambers. In this case, the sound softener can have, in a simple way, multiple resonant chambers that are tuned to different natural frequencies, which makes it possible to reduce the sound in different frequency ranges. For example, in order to form multiple resonating chambers, multiple networks can be provided spaced in the axial direction, a network separating two resonant chambers.
    Easy fabrication and assembly also occur due to the fact that the connection channel is formed by a channel-shaped section in the partition wall. Additional components are not required for this project. The insert can advantageously be a single piece component together with the partition wall and the connection channel, which can be manufactured as an injection molded contiguous piece. The length and diameter of the connection channel (or connection channels) can be selected according to the Helmholtz resonator principles in such a way that the respective natural frequency of the resonator chamber is within the desired frequency range. The channel-shaped section advantageously runs in the radial direction.
    Further refinement is achieved by the fact that at least one resonator chamber has, in an axial direction of the insert, a changeable inner diameter, and at the same time an outer diameter that remains constant. In this way, in particular, the resistance to flow in the flow channel can be kept low.
    Usability and assembly are further enhanced when the sound damper is made of an elastically flexible material. In this way, the sound damper can be inserted into the tube-shaped bodies with a curve or into flexible tubes. For example, an elastic plastic can be used as an elastically flexible material. In this way, it can be obtained that the ends of the insert are able to assume a curvature angle, with respect to each other, of more than 5º, in particular of more than 20º, and advantageously up to 90º.
    Effective noise absorption in various frequency ranges can advantageously be obtained as multiple resonating chambers are formed in the axial direction adjacent to each other, which are each connected to the flow channel through a channel of connection. Each of the resonator chambers can be tuned to a natural frequency! different. In practice, it has proved advantageous to provide up to four resonant chambers adjacent to each other, which makes it possible to reduce noise in a corresponding number of frequency bands. Depending on the application, a single resonator chamber may be sufficient or a larger number of resonator chambers may be provided.
    . At least one resonating chamber is advantageously bounded on its external side by a tube-shaped body wall.
    In particular, the resonator chamber can be delimited from the outside depending on the inside of the tube-shaped body, which in this case forms the outer resonator chamber at the same time that it is delimited inside by the insert.
    As an alternative, the insert can also have an additional wall that delimits the resonating chamber or the resonating chambers in the radial direction to the outside.
    To be fixed to the body in the form of a tube, the insert advantageously has a clamping zone on its external side, which is used to fix the sound absorber after being inserted into the body in a pipe.
    Fixing is particularly simple when the tube-shaped body is made of a deformable material and is fixed to the clamping area by means of a clamping device, such as a hose clamp, for example.
    The tube-shaped body can be made of an elastically deformable material, for example, plastic, or of a ductile material, for example, aluminum, which is stamped for the clamping zone.
    In order to obtain a good fixation, the clamping area can be delimited by a clamping edge on one or both sides.
    This makes it possible to obtain a positive fit between the insert and the tube-shaped body.
    The clamping edge can be formed by the net.
    A compact configuration can be achieved when the clamping edge has breaks, since the volume on both sides of the clamping edge can be part of a resonating chamber.
    The tube-shaped body advantageously has the same diameter in which the insert is located and in the adjacent areas in the axial direction.
    Modifications to the tube-shaped body, in particular an enlargement, in order to provide resonator chambers in this area, are not necessary.
    The insert can simply be inserted into the body in the form of a tube, which can be continuous, for example.
    Other objectives, characteristics, advantages and possibilities of application of the present invention will result from the description of exemplary modalities below, based on the drawings.
    All aspects described and / or illustrated by themselves or in any combination form the object of the present invention, regardless of whether they are combined in individual claims or from their previous reference.
    Figure 1 shows a sectional view of a sound damper, according to the present invention, inserted in a body in the form of a straight tube.
    Figure 2a shows a perspective view of a sound absorber according to the present invention of Figure 1; Figure 2b shows a perspective view in section of a sound damper according to Figure 2a; t Figure 3a shows the sound absorber of Figure 1a inserted into a curved tube-shaped body, the tube-shaped body being shown in a section view; Figure 3b shows the sound damper of Figure 3a, the sound dampener and the tube-shaped body being shown in a section view; Figure 4a shows a perspective view of another embodiment of a sound damper according to the present invention; Figure 4b shows a perspective section view of the sound dampener in Figure 4a.
    Figure 1 shows a sound damper 1 for a tube-shaped body 2, which forms a cavity 3. The tube-shaped body 2 can be a tube made of plastic - or metal, for example. The tube-shaped body 2 can be made of an elastically deformable material and can be designed as a hose, for example. The tube-shaped body 2 is a part of a refrigerating circuit in a cooling system in which the refrigerant fluid circulates inside the tube-shaped body. The illustrated sound absorber 1 is particularly suitable for that part of a refrigerant circuit in which the refrigerant is present in a gaseous form. In this way, the sound damper 1 can effectively reduce the noise generated by a compressor (not shown). The sound absorber 1 is designed as an insert 26 which is manufactured separately and inserted during assembly into the cavity 3 of the tube-shaped body 2. The sound absorber 1 has a central flow channel 4. The housing —Naldeflux4 is located coaxially with respect to the tube-shaped body
    2. In addition, four resonator chambers 5, 6, 7, 8 are provided adjacent to each other in the axial direction. The flow channel 4 and the resonator chambers 5, 6, 7, 8 are separated by a dividing wall 9 that forms the flow channel 4 inside and separates it from the respective external resonator chamber 5,6, 7e8.The partition wall 9 consists of a section of the sound absorber 1 designed as an insert. The resonated-DP chambers 5, 6, 7, 8 extend, in this case, in a ring shape around the inner tube 10. In addition, it is apparent in Figure 1 that the inner cross-sectional area of the inner tube changes in the axial direction of the sound damper 1. From an entrance area in cross section at an entrance 11 of the sound damper 1, the internal area in cross section of the inner tube 10 narrows until it reaches an intermediate area in section transverse in a central area 15. From this point, the internal cross-sectional area widens again to a cross-sectional exit area at output 12 of the sound absorber 1. The cross-sectional entrance area and the exit area in cross section at inlet 11 and outlet 12 correspond approximately to the internal area in cross section of the tube-shaped body 2. In this way, the flow can reach the flow channel 4 of the sound absorber 1 through the shaped body tube 2 unimpeded and with only in small flow losses and can leave this point again for the tube-shaped body 2. In the shown mode, the inner tube 10 has two conical sections 13, 14 that connect the inlet 11 and the outlet 12 to an area 15 having the narrower cross section. In the modality shown, the conical sections 13 and 14 have the same axial length. Area 15 with the narrowest cross section has a cylindrical cross section.
    : 9/12
    Each resonator chamber 5, 6, 7, 8 is bounded on the inside by the inner tube 10 and on the outside by a section of the body in the form of tube 2. In addition, the sound absorber 1 has networks 16 , 17, 18 so that the multiple resonator chambers 5, 6, 7, 8 are separated in the space formed between the inner tube 10 and the tube-shaped body 2. Each of these networks 16, 17, 18 is located on the tube internal 10 and has a circumferential ring-shaped design.
    The external diameter of the networks 16, 17, 18 corresponds to the internal diameter of the tube-shaped body 2, so that the tube-shaped body 2 is in close contact with the sound damper in the area of the networks 16, 17, 18 Circumferential networks 16, 17, 18 point outwards in the radial direction.
    The network 16 separates the resonant Ep chambers 5, 6, which are adjacent in the axial direction.
    Likewise, the network 17 separates the resonator chambers 6, 7 and the network 18 separates the resonator chambers 7, 8. The resonator chambers 5 and 8 are delimited at their outer ends by a section of the inner tube 10 that is in contact with the tube-shaped body 2. The resonator chambers 5, 5,7, 8 have a constant external diameter along their axial length,
    but a changeable internal diameter.
    The resonator chambers 5, 6, 7, 8 make possible the reduced reduction according to the Helmholtz resonator principle.
    For this purpose, the resonator chambers 5, 6, 7, 8, each including a volume, are connected to the flow channel 4 via connection channels 19 and 19 ', 20 and 20', 21 and 21 'and 22 and 22 '. In the embodiment shown, each resonator chamber 5, 6, 7, 8 is connected to flow channel 4 through two opposite connection channels 19e19 ', 20e20', 21e21'e 22 e22. Each connection channel includes a small circular opening.
    The connection channels 19, 19 ', 20, 20', 21, 21 ', 22 and 22' have different lengths for each resonator channel 5, 6, 7, 8, which makes the adjustment to the desired frequency range becomes possible.
    In the embodiment shown, the two opposite connecting channels 19, 19 have a length of the order of magnitude of the wall thickness.
    The two connection channels 21, 21 'are slightly longer.
    Connecting channels 22, 22 'and 20, 20' are distinctly longer in length.
    The f 10/12 f connection channels 19, 19 ', 20, 20', 21, 21 ', 22, 22' are formed by a channel-shaped section of the partition wall 9 and the inner tube 10. The cables connection pins 19, 19 ', 20, 20', 21, 21 ', 22, 22' can be placed in a desired position on the circumference of the insert.
    The sound damper shown 1 can be made of plastic like an injection molded part. Particularly suitable is an elastic plastic material. The sound absorber 1 is therefore also easily inserted into curved tube-shaped bodies. In addition, the sound damper is therefore able to adapt without any problems to a flattening or ovalisation of the tube-shaped body, which can occur in the area of a curve of the tube-shaped body, for example. Figures 2a and 2b show the sound absorber 1 of Figure 1, before its insertion in the tube-shaped body. The nets 16, 17, 18: located in the inner tube 10 and the conical sections 13, 14 and 15 that have the narrowest cross section of the inner tube 10 are clearly recognizable. In addition, connection channels 19, 19 ', 20, 20', 21, 21 ', 22, 22' are clearly recognizable. Figures 3a and 3b show the sound absorber 1 inserted in a tube-shaped body 2 with a curve. For example, the tube-shaped body can be designed as a hose that is installed with a curve. Since the sound absorber 1 is made of an elastic plastic material, it will be able to adapt to the curve of the tube-shaped body 2, even if it is manufactured in the straight shape shown in Figure 2a. Also in a curved tube-shaped body, the networks 16, 17, 18 offer good contact between the sound damper 1 and the interior of the tube-shaped body without preventing the tube-shaped body from flexing. Figures 4a and 4h show another modality of the sound damper according to the present invention before its insertion into a tube-shaped body. Parts that have the same function are labeled with the same reference numbers as the previous figures. Reference is made to their respective description, which also applies to Figures
    ; 12/11 To 4a e4b.
    In the modality shown in Figures 4a and 4b, only two resonating chambers are formed, which are separated by the circumferential network 36. The network 16 'has, like the networks 16, 17 and 18 of the above described mode, a circumferential ring-shaped design. In addition, the network 16 'is projected on the outer side of the inner tube 10. Each of the resonating chambers is connected to the flow of channel 4 through two connection channels 20, 20' and 22, 22 '. In the modality shown in Figures 4a and 4b, the inner tube also has conical sections 13, 14. However, these sections are shorter in the axial direction than is the case in the modality shown in Figure 1. Therefore, the area 15 that has the narrowest cross section is correspondingly longer. In this way, a greater volume becomes available for the resonator chambers.
    For fixing the sound absorber 1, the insert has a tightening zone 23 on the outside of the inner tube 10. When the tube-shaped body is made of a deformable material, such as a hose , the tube-shaped body having the sound absorber 1 can be fixed in the clamping zone 23 using a clamping device, for example, a hose clamp. In the embodiment shown, the wall thickness of the inner tube 10 is reinforced in the clamping zone 23 for this purpose. The clamping zone 23 is bounded on both sides by the clamping edges 24, 24 'which point outwards. Good axial fixation is achieved in this way. In the embodiment shown, the clamping edge 24 is formed by an oblique lateral surface of the mesh 16º. The clamping edge 24 spaced in the axial direction of the clamping edge 24 has breaks 25. In this way, the space on both sides of the clamping edge 24 'can form a continuous resonating chamber.
    Reference listing 1 - 2-body tube-shaped sound damper 3 - cavity 4 - flow channel
    At 12/12: 5 - resonating chamber 6 - resonating chamber 7 - resonating chamber 8 - resonating chamber 9-partition wall
    - inner tube 11 - inlet 12 - outlet 13 - conical section
    10 14-conical section - area having the narrowest cross section
    E 16, 16 '- network 17 - network ã 18 - network
    15 19,19'-connection channels 20, 20 '- connection channels 21, 21'- connection channels 22, 22' - connection channels 23 - clamping zone
    24.24'-clamping edges - break 26 - insert
    权利要求:
    Claims (15)
    [1]
    1. Refrigerant circuit of a refrigeration system with a tube-shaped body (2), into which a sound damper (1) is inserted, according to which the body (2) forms a cavity (3) and in as a function of the sound absorber (1) is designed as an insert (26) that is inserted into the cavity (3) of the body in the form of a tube (2) and as a function of what the insert (26) delimits at least one resonating chamber (5, 6, 7, 8) and a flow channel (4), which is connected to the resonator chamber (5, 6, 7, 8) through a connection channel (19, 19 ', 20, 20 ', 21, 21', 22, 22).
    [2]
    2. Refrigerant circuit according to claim 1, characterized by the fact that the insert (26) has a dividing wall (9) that forms the flow channel (4) and separates it from at least one resonating chamber (5, 6, 7.8).
    [3]
    3. Refrigerant circuit according to claim 2, characterized by the fact that the dividing wall (9) is formed by a section of the insert (26) that forms an inner tube (10).
    [4]
    4. Refrigerant circuit, according to claim 3, characterized by the fact that the internal cross-sectional area of the inner tube (10) changes in the axial direction of the insert (26).
    [5]
    5. Refrigerant circuit according to claim 3 or 4, characterized by the fact that the inner tube (10), which starts from an entrance area in cross section at an entrance (11) of the sound damper , narrows to an area of intermediate cross section and extends from it to an area of exit section in cross section at the exit (12) of the sound damper.
    [6]
    Refrigerant circuit according to one of claims 1 to 5, characterized by the fact that the insert (26) has at least one network pointing outwards (16, 17, 18) in order to contact an interior wall of the body in tube-shaped (2), at least one net (16, 17, 18) delimiting the resonating chamber (5,6,7,8) in an axial direction of the insert (26).
    [7]
    7. Refrigerant circuit, according to claim 6, characterized by the fact that the network (16, 17, 18) separates two resonant chambers
    R 2/2 And adjacent beds (5, 6.7, 8).
    [8]
    Refrigerant circuit according to one of claims 1 to 7, characterized by the fact that the connection channel (19, 19 ', 20, 20', 21, 21 ', 22, 22) is formed by a section in channel shape in the partition wall (9)
    [9]
    9. Refrigerant circuit according to one of claims 1 to 8, characterized by the fact that at least one resonating chamber (5, 6, 7, 8) has an inside diameter that changes in an axial direction of the insert ( 26), while the outside diameter remains constant.
    [10]
    10. Refrigerant circuit according to one of claims 1 to 9, characterized by the fact that the sound absorber (1) is made of one; elastically flexible material.
    [11]
    11. Refrigerant circuit according to one of claims 1 to 10, characterized by the fact that multiple adjacent resonating chambers (5,6,7,8) are formed in the axial direction, which are, each of them, connected to the flow channel through at least one connection channel (19, 19 ', 20, 20', 21, 21 ', 22, 22).
    [12]
    Refrigerant circuit according to one of claims 1 to 11, characterized by the fact that at least one resonating chamber (5,6,7,8) is bounded on its outer side by a tube-shaped body wall ( two).
    [13]
    13. Refrigerant circuit according to one of claims 1 to 12, characterized by the fact that the insert (26) has a clamping zone (23) on its external side for attachment to the tube-shaped body (2).
    [14]
    Refrigerant circuit according to one of claims 1 to 13, characterized in that the tube-shaped body is a flexible hose.
    [15]
    15. Refrigerant circuit according to claim 14 or 15, characterized by the fact that the tube-shaped body (2) has essentially the same diameter in the area in which the insert (26) is located, and in the areas adjacent in the axial direction.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2051515A|1935-10-07|1936-08-18|Maxim Silencer Co|Sound attenuating device|
    US2127672A|1935-10-25|1938-08-23|Maxim Silencer Co|Sound attenuating device|
    US2271892A|1936-07-15|1942-02-03|Maxim Silencer Co|Sound attenuating device|
    US2311676A|1941-07-02|1943-02-23|Maxim Silencer Co|Silencer|
    US3043499A|1958-01-22|1962-07-10|Basf Ag|Process and apparatus for circulating hot gases, especially under high pressures|
    DE1199514B|1962-05-12|1965-08-26|Guenther Gerber|Silencer|
    JPH036325B2|1983-09-29|1991-01-29|Sanshin Kogyo Kk|
    SU1453057A1|1987-04-27|1989-01-23|Войсковая часть 27177|Exhaust silencer|
    US5317112A|1991-10-16|1994-05-31|Hyundai Motor Company|Intake silencer of the variable type for use in motor vehicle|
    US5205719A|1992-01-13|1993-04-27|Copeland Corporation|Refrigerant compressor discharge muffler|
    DE4327562A1|1993-08-17|1995-02-23|Erwin Dipl Ing Koetter|Coaxial resonator silencer for high alternating pressures|
    US6116375A|1995-11-16|2000-09-12|Lorch; Frederick A.|Acoustic resonator|
    JP3213567B2|1997-06-16|2001-10-02|株式会社オーツカ|Silencer for air conditioner|
    US6265081B1|1998-06-08|2001-07-24|Mitsubishi Engineering Plastics Corporation|Integrally molded articles of polyamide resins|
    DE10102040A1|2001-01-18|2002-07-25|Mahle Filtersysteme Gmbh|Silencer, for a motor exhaust or turbo charger air intake, has a hollow body at the component to be suppressed containing a number of parallel Helmholtz resonators|
    US6684842B1|2002-07-12|2004-02-03|Visteon Global Technologies, Inc.|Multi-chamber resonator|
    US7114525B2|2003-08-29|2006-10-03|Dana Corporation|Method and apparatus for reduction of fluid-borne noise in hydraulic systems|
    DE102004029221A1|2004-06-16|2006-01-12|Geiger Technik Gmbh|Acoustic damping device and device for conducting a fluid|
    JP2008031918A|2006-07-28|2008-02-14|Denso Corp|Intake device|
    FR2929172A1|2008-03-31|2009-10-02|Hutchinson Sa|NOISE REDUCING DEVICE FOR THE AIR CONDITIONING CIRCUIT OF A MOTOR VEHICLE, DRIVING AND CIRCUIT INCORPORATING IT|
    US7934581B2|2009-01-30|2011-05-03|Eaton Corporation|Broadband noise resonator|
    US8323556B2|2009-09-30|2012-12-04|Ford Global Technologies, Llc|Manufacture of an acoustic silencer|US8596398B2|2007-05-16|2013-12-03|Polaris Industries Inc.|All terrain vehicle|
    US8994494B2|2008-10-10|2015-03-31|Polaris Industries Inc.|Vehicle security system|
    US9488079B2|2012-02-07|2016-11-08|Black Widow Performance, Inc.|Muffler for automobile|
    CN103711984B|2012-09-28|2018-04-13|费希尔控制国际公司|Simplified modal attenuator|
    WO2014093215A1|2012-12-10|2014-06-19|Eaton Corporation|Resonator with liner|
    WO2014184377A2|2013-05-17|2014-11-20|Resmed Paris Sas|Flow diffuser and sound cone|
    CN104500178B|2013-11-27|2016-11-09|广东西电动力科技股份有限公司|A kind of complex muffler preventing and treating diesel generating set low-frequency noise|
    US9845004B2|2014-01-10|2017-12-19|Polaris Industries Inc.|Snowmobile|
    US10358187B2|2014-01-10|2019-07-23|Polaris Industries Inc.|Snowmobile|
    DE102014115898B4|2014-10-31|2019-07-25|Dietrich Denker|resonator|
    KR101683491B1|2014-12-09|2016-12-07|현대자동차 주식회사|Heat exchanger for vehicle|
    RU2590216C1|2015-03-18|2016-07-10|федеральное государственное бюджетное образовательное учреждение высшего образования "Пермский национальный исследовательский политехнический университет"|Resonance cell for suppression of acoustic waves|
    US9982639B2|2015-08-11|2018-05-29|Rl Hudson & Company|Tunable injection molded resonator|
    CN105946502B|2016-05-03|2019-01-29|北京新能源汽车股份有限公司|For the noise reduction tube assembly of air-conditioning and with its electric car|
    GB2551578B|2016-06-24|2019-12-11|Jaguar Land Rover Ltd|Conduit for reducing noise|
    KR20190061821A|2017-11-28|2019-06-05|현대자동차주식회사|Heat exchanger for vehicle|
    DE102017130661A1|2017-12-20|2019-06-27|Montaplast Gmbh|Broadband damper for a motor vehicle engine|
    US10793181B2|2018-02-13|2020-10-06|Polaris Industries Inc.|All-terrain vehicle|
    CN108561669B|2018-03-09|2020-05-12|中国人民解放军海军工程大学|Elastic back cavity type pipeline vibration damping and noise eliminating device|
    CN108425719A|2018-05-17|2018-08-21|潍柴动力股份有限公司|Muffler and automobile|
    CN108974305B|2018-06-27|2020-06-30|中国船舶重工集团公司第七一九研究所|Resonance silencing inter-board flow channel|
    WO2020154295A1|2019-01-21|2020-07-30|Toledo Molding & Die, Inc.|Inline high frequency fiber silencer|
    JP6871285B2|2019-02-04|2021-05-12|フタバ産業株式会社|Tail pipe|
    CN109854854A|2019-03-27|2019-06-07|麦映辉|Airflow line and gas processing device|
    US10823036B1|2019-06-25|2020-11-03|Faurecia Emissions Control Technologies, Usa, Llc|Method and apparatus to accommodate sensors on an exhaust component|
    KR102233359B1|2019-08-27|2021-03-30|주식회사 화승알앤에이|System for refrigerants pipe|
    DE102019123902A1|2019-09-05|2021-03-11|Hanon Systems|Device for damping pressure pulsations for a compressor of a gaseous fluid|
    CN111609243A|2020-05-26|2020-09-01|北京绿创声学工程股份有限公司|Manufacturing method of large equivalent diameter conical tandem type noise elimination channel|
    法律状态:
    2020-10-06| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-10-20| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-10-27| B08F| Application dismissed because of non-payment of annual fees [chapter 8.6 patent gazette]|Free format text: REFERENTE AS 9A E 10A ANUIDADES. |
    2021-02-02| B11B| Dismissal acc. art. 36, par 1 of ipl - no reply within 90 days to fullfil the necessary requirements|
    2021-11-23| B350| Update of information on the portal [chapter 15.35 patent gazette]|
    优先权:
    申请号 | 申请日 | 专利标题
    EP09013111.1|2009-10-16|
    EP09013111.1A|EP2357330B1|2009-10-16|2009-10-16|Cooling circuit with acoustic baffler for a tubular body forming a cavity|
    PCT/EP2010/006034|WO2011044993A1|2009-10-16|2010-10-04|Sound absorber for a pipe-shaped, cavity-forming body|
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