EP0561383A1 - A refrigeration compressor - Google Patents
A refrigeration compressor Download PDFInfo
- Publication number
- EP0561383A1 EP0561383A1 EP93104357A EP93104357A EP0561383A1 EP 0561383 A1 EP0561383 A1 EP 0561383A1 EP 93104357 A EP93104357 A EP 93104357A EP 93104357 A EP93104357 A EP 93104357A EP 0561383 A1 EP0561383 A1 EP 0561383A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- chamber
- silencer
- gas
- pipe
- 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.)
- Granted
Links
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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
- F04B39/0066—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using sidebranch resonators, e.g. Helmholtz resonators
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Separation By Low-Temperature Treatments (AREA)
Abstract
Description
- The present invention relates to a special form of inlet pipe for cooling gas inside an airtight enclosure containing an electric compressor, particularly employed in refrigerators for household use.
- For better illustration of the present invention it is assumed that the pipe operates in close association with the compressor and that it is made of injection-molded or stamped plastic. This naturally does not limit the invention to this type of material and to this connection.
- The fluctuations of gas pressure inside displacement compressors particularly for household refrigerators are of considerable importance in view of their influence on the efficiency and the level of acoustic power emitted by the compressors. Therein the cooling gas coming from the inlet pipe enters inside the airtight housing of the compressor.
- The body of the compressor has an inlet pipe inside the casing connected to the inlet valve via various channels and cavities that permit the drawn-in gas to be conveyed inside the cylinder.
- Being in contact with all the hot surfaces of the compressor, the gas heats up and reduces its density during these passages.
- This leads to a reduction in the cylinder fill and thus ultimately to a reduction in the cooling capacity of the compressor.
- The basic mechanisms regulating the dynamics of the gas movements are as follows.
- 1) The mechanism of restriction of flow through each "collar" and each connecting cavity constituting the system is regarded as an opening constricting the flow of gas. This effect is of virtually static character since the inertia of the gas is low, normally negligible, in the inlet and outlet passages which have reasonable dimensions.
- 2) The second mechanism is essentially of a dynamic nature, relating to the sudden opening and closing of the inlet and outlet valves. The sudden discharge of an amount of gas inside a cavity of the system causes an acceleration in the mass of the gas already existing in the passages downstream of the cavity, thus permitting the arriving gas to alter its thermodynamic characteristics minimally. The inertia of the gas offers resistance to this variation of motion and results in a pressure increase inside the cavity. Once this change of state has been established the gas persists in its motion (due to inertia), producing a rarefaction of gas in the cavity in which there was previously an overpressure. The repetition of this process, as is characteristic of reciprocating displacement compressors, produces a vibration of the gas.
- From the point of view of efficiency alone, the ideal solution would be the total elimination of any system of pipes, manifolds and cavities that have the function of collecting the gas upstream and downstream of the automatic valves.
- However, maximizing thermodynamic efficiency in this way would accordingly increase the level of acoustic power emitted, particularly during intake, that is transmitted directly outside the casing of the compressor, thereby compromising the requirements of quietness.
- It would therefore be desirable, and is the object of the present invention, to realize a compressor that combines high efficiency with low noise, and is reliable, economical and easy to assemble while using materials and techniques permitted by the state of the art.
- This object is achieved with the device described, by way of example and nonrestrictively, with reference to the adjoined figures in which:
- Fig. 1
- shows a view of the inside of the compressor casing with the device shown from the front, comprising a silencer interposed between the intake of the gas from outside of the compressor and the cylinder head;
- Fig. 2
- shows a front inside view of the cover of the silencer;
- Fig. 3
- shows a lateral view of the same detail;
- Fig. 4
- shows a front inside view of the body of the silencer;
- Fig. 5
- shows a lateral section of the same detail.
- The essential idea of the invention is described here as follows.
- In order to maintain the process of gas intake within an adiabatic change (thereby preserving the cooling efficiency of the compressor), the acoustic control system is preferably made of plastic material.
- An expansion silencer is realized between two pipes (having different sections) and by a Helmholtz resonator whose collar is positioned along the pipe at the outlet of the silencer on the side of the inlet valve.
- Inside the silencer the spread of the acoustic waves is subject to interference and reflection phenomena that attenuate their acoustic intensity (understood to be the energy flow per unit of area).
- Experiments have shown the transfer function of this component (understood to be the relation between an acoustic signal at the input and an acoustic signal at the output) when the silencer is subjected to an accidental-type acoustic signal, in static states and in air. The silencer has been found to be a low-pass acoustic filter, equipped with two resonances f1 and f2 (see Fig. 6). The attenuation of the acoustic intensity to resonant frequencies f1 and f2 is obtained by means of the Helmholtz resonator.
- It is known that in systems composed of several weakly coupled components (silencer and resonator) the (generally complex) resonant frequencies are divided and shifted along the axis of the frequencies of a known range, so that one frequency is higher and one is lower than the frequency of the unmodified system.
- Thus, if a resonator is applied to a cavity (and tuned to have the same natural frequency as an acoustic mode of the cavity), two new coupled modes are produced whose natural frequencies are disposed on the edges of the original frequency. The separation between the frequencies is proportional to the value of the coupling parameter.
- To obtain good results with this type of coupling it is necessary to optimize the volume of the resonator in accordance with the volume of the cavity and also the position of the resonator neck, which must be located near a loop of the acoustic mode tending to attenuate to a greater extent. It is therefore necessary to apportion these parameters to obtain a reduction of acoustic pressure to the starting frequency, whereby the reduction should be considerable but not excessive so as not to be compensated by a considerable increase of acoustic pressure to the two new frequencies that will be produced.
- It is furthermore stressed that there is no flow of gas through the resonator cavity. Since there is thus no variation in the gas temperature due to the interposed cavity, the efficiency characteristics of the thermodynamic cycle are maintained unchanged.
- The gas entering the compressor and coming from the inlet pipe is not dispersed in the casing to be then drawn into the inlet pipe present in the compressor body, but is immediately "intercepted" and directed toward the head without being allowed to spread.
- For this purpose a silencer is designed and mounted for guiding the path of the gas and connecting on one side the area facing the gas entry port in the casing, and on the other side the inlet port in the cylinder head. The separation which the flow of gas thus undergoes and the particular path that develops achieve the result of preventing the gas from overheating and of blocking the intake noise within the pipe.
- The features of the invention are specified in the claims that follow.
- Referring to the figures we can see the following components:
- 1) compressor casing
- 2) compressor body
- 3) cylinder head
- 4) silencer, seen from its cover
- 5) expansion chamber of silencer
- 6) gas entry pipe into
chamber 5 - 7) gas admission port in inlet valve
- 8) gas outlet pipe from
chamber 5 - 9) outlet pipe to Helmholtz resonator
- The cooling gas in
pipe 6 enterschamber 5 insidesilencer 4. - The silencer is interposed between the cavity inside the compressor casing and the gas inlet pipe within cylinder head 3, and is substantially L-shaped, whereby the greater side, widened at the center and virtually box-shaped, contains
expansion chamber 5 andgas admission pipe 6 into the chamber, and the restriction of the lesser side constitutesgas outlet pipe 8 fromchamber 5. - After the restriction the lesser side leads first to gas admission hole 7 in the inlet valve and then to outlet
pipe 9 toward a Helmholtz resonator, consisting of a suitable cavity formed within the compressor body. -
Expansion chamber 5 can have different forms, but preferably has two substantially parallel plane opposing walls and two curved opposing walls with the same direction and with substantially the same angle of curvature. -
Chamber 5 can also have different forms provided that the following proportions are maintained between some critical dimensions. - The ratio between the area of
admission pipe 6 and the transverse section ofchamber 5 must be approximately 0.03. - Furthermore the length of
cavity 5 must be approximately 34 mm. - In order to maintain the process of gas intake within an adiabatic change (thereby preserving the cooling efficiency of the compressor), the silencer is preferably made of plastic material.
- It is understood that what has been said and shown with reference to the adjoined drawings is intended only to exemplify the invention, and that numerous variants and modifications may be produced without departing from the present invention.
Claims (7)
- An electric compressor, particularly for household refrigerators, comprising an outside casing (1), an inside body (2), a cylinder head (3), a silencer (4) interposed between the cavity inside the compressor casing and the gas inlet pipe within the cylinder head (3), characterized in that in the chamber (5) inside the silencer (4) the ratio between the area of the admission pipe (6) and the transverse section of the chamber (5) must be approximately 0.03, and the length of the chamber (5) must be approximately 34 mm.
- The compressor of claim 1, characterized in that the silencer (4) is substantially L-shaped, whereby the greater side contains the expansion chamber (5) and the gas admission pipe (6) into the chamber, and the lesser side constitutes the gas outlet pipe (8) from the chamber (5).
- The compressor of claim 2, characterized in that the lesser side leads first to the gas admission port (7) in the inlet valve and then to the outlet pipe (9) toward a Helmholtz resonator.
- The compressor of claim 3, characterized in that the Helmholtz resonator is formed within the compressor body.
- The compressor of claim 4, characterized in that the expansion chamber (5) has two substantially parallel plane opposing walls and two curved opposing walls with the same direction and substantially the same angle of curvature.
- The compressor of the preceding claim, characterized in that the silencer (4) has a constructional form substantially as shown in Figs. 2, 3, 4, 5.
- The compressor of any of the above claims, characterized in that the silencer (4) performs the function of reducing noise within an adiabatic change.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITPN920010 | 1992-02-11 | ||
IT92PN000010U IT229032Y1 (en) | 1992-03-18 | 1992-03-18 | REFRIGERATED COMPRESSORS |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0561383A1 true EP0561383A1 (en) | 1993-09-22 |
EP0561383B1 EP0561383B1 (en) | 1996-07-17 |
Family
ID=11394624
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93104357A Expired - Lifetime EP0561383B1 (en) | 1992-03-18 | 1993-03-17 | A refrigeration compressor |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0561383B1 (en) |
AT (1) | ATE140518T1 (en) |
DE (1) | DE69303644T2 (en) |
ES (1) | ES2090743T3 (en) |
IT (1) | IT229032Y1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1997027402A2 (en) * | 1995-09-29 | 1997-07-31 | Matsushita Refrigeration Company | Electrically-operated sealed compressor |
US6012908A (en) * | 1996-01-23 | 2000-01-11 | Matsushita Refrigeration Company | Electrically operated seal compressor having a refrigerant flow branch tube with a chamber disposed in the vicinity of a suction port |
CN101871444A (en) * | 2010-07-30 | 2010-10-27 | 丹佛斯制冷设备(天津)有限公司 | Muffler |
WO2016127702A1 (en) * | 2015-02-14 | 2016-08-18 | 浙江鸿友压缩机制造有限公司 | Compressor intake silencer based on multi-level tubular attenuation unit |
CN110285496A (en) * | 2019-07-29 | 2019-09-27 | 珠海格力电器股份有限公司 | Muffler, refrigeration system and air conditioner |
US11067071B2 (en) | 2015-08-14 | 2021-07-20 | Sabic Global Technologies B.V. | Cylinder head for compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2190151A (en) * | 1986-05-02 | 1987-11-11 | Brasil Compressores Sa | Silencing and reducing heat absorption in compressors |
US4960368A (en) * | 1988-07-29 | 1990-10-02 | Empresa Brasileira De Compressores S/A-Embraco | Suction system for hermetic compressor of refrigeration |
DE4217591A1 (en) * | 1991-05-28 | 1992-12-03 | Brasil Compressores Sa | INTAKE MUFFLER ASSEMBLY FOR HERMETICALLY SEALED COMPRESSORS |
-
1992
- 1992-03-18 IT IT92PN000010U patent/IT229032Y1/en active IP Right Grant
-
1993
- 1993-03-17 ES ES93104357T patent/ES2090743T3/en not_active Expired - Lifetime
- 1993-03-17 EP EP93104357A patent/EP0561383B1/en not_active Expired - Lifetime
- 1993-03-17 DE DE69303644T patent/DE69303644T2/en not_active Expired - Fee Related
- 1993-03-17 AT AT93104357T patent/ATE140518T1/en not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2190151A (en) * | 1986-05-02 | 1987-11-11 | Brasil Compressores Sa | Silencing and reducing heat absorption in compressors |
US4960368A (en) * | 1988-07-29 | 1990-10-02 | Empresa Brasileira De Compressores S/A-Embraco | Suction system for hermetic compressor of refrigeration |
DE4217591A1 (en) * | 1991-05-28 | 1992-12-03 | Brasil Compressores Sa | INTAKE MUFFLER ASSEMBLY FOR HERMETICALLY SEALED COMPRESSORS |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1997027402A2 (en) * | 1995-09-29 | 1997-07-31 | Matsushita Refrigeration Company | Electrically-operated sealed compressor |
WO1997027402A3 (en) * | 1995-09-29 | 1997-10-23 | Matsushita Refrigeration | Electrically-operated sealed compressor |
US6206655B1 (en) | 1995-09-29 | 2001-03-27 | Matsushita Refrigeration Company | Electrically-operated sealed compressor |
US6012908A (en) * | 1996-01-23 | 2000-01-11 | Matsushita Refrigeration Company | Electrically operated seal compressor having a refrigerant flow branch tube with a chamber disposed in the vicinity of a suction port |
EP1304480A1 (en) * | 1996-01-23 | 2003-04-23 | Matsushita Refrigeration Company | Compressor suction muffler |
CN101871444A (en) * | 2010-07-30 | 2010-10-27 | 丹佛斯制冷设备(天津)有限公司 | Muffler |
WO2016127702A1 (en) * | 2015-02-14 | 2016-08-18 | 浙江鸿友压缩机制造有限公司 | Compressor intake silencer based on multi-level tubular attenuation unit |
US11067071B2 (en) | 2015-08-14 | 2021-07-20 | Sabic Global Technologies B.V. | Cylinder head for compressor |
CN110285496A (en) * | 2019-07-29 | 2019-09-27 | 珠海格力电器股份有限公司 | Muffler, refrigeration system and air conditioner |
CN110285496B (en) * | 2019-07-29 | 2023-11-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Muffler, refrigerating system and air conditioner |
Also Published As
Publication number | Publication date |
---|---|
IT229032Y1 (en) | 1998-06-24 |
EP0561383B1 (en) | 1996-07-17 |
ITPN920010V0 (en) | 1992-03-18 |
ES2090743T3 (en) | 1996-10-16 |
ITPN920010U1 (en) | 1993-09-18 |
DE69303644T2 (en) | 1996-11-21 |
DE69303644D1 (en) | 1996-08-22 |
ATE140518T1 (en) | 1996-08-15 |
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