EP0926343B1 - Silencieux d'un compresseur pour fluides frigorigènes - Google Patents

Silencieux d'un compresseur pour fluides frigorigènes Download PDF

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Publication number
EP0926343B1
EP0926343B1 EP98124260.5A EP98124260A EP0926343B1 EP 0926343 B1 EP0926343 B1 EP 0926343B1 EP 98124260 A EP98124260 A EP 98124260A EP 0926343 B1 EP0926343 B1 EP 0926343B1
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EP
European Patent Office
Prior art keywords
channel
outlet
damping
refrigerant compressor
chamber
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.)
Expired - Lifetime
Application number
EP98124260.5A
Other languages
German (de)
English (en)
Other versions
EP0926343A2 (fr
EP0926343A3 (fr
Inventor
Volker Pollrich
Helmut Ruprecht
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP0926343A2 publication Critical patent/EP0926343A2/fr
Publication of EP0926343A3 publication Critical patent/EP0926343A3/fr
Application granted granted Critical
Publication of EP0926343B1 publication Critical patent/EP0926343B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

Definitions

  • the invention relates to a refrigerant compressor comprising a compressor housing, at least one cylinder chamber arranged in the compressor housing, a piston oscillating in the cylinder chamber, a suction chamber upstream of the cylinder chamber, from which refrigerant enters the cylinder chamber, a pressure chamber connected downstream of the cylinder chamber, in which Cylinder chamber compressed refrigerant enters, and an outlet channel downstream of the pressure chamber.
  • the invention is therefore an object of the invention to improve a refrigerant compressor of the generic type such that the most effective damping of pulsations is possible.
  • a refrigerant compressor of the type described above in that compressed refrigerant flows through a damper channel from the pressure chamber into the outlet channel, that an inlet opening of the damper channel opens with a jump in the pressure chamber and that an outlet opening of the damper channel with a jump in cross section the exhaust duct opens, the damper duct 50 also having a length calculated from the fact that at the most frequently occurring pulsation frequency, reflection should occur at the open end, so that the returning wave extinguishes the incoming wave.
  • This concept according to the invention has the great advantage that a damping element to be provided in the lines is eliminated, so that additional pipe connections for installation of this damping element omitted and also that the damper channel acts optimally, since it dampens all pulsations immediately in the region of their formation, namely in the pressure chamber of the refrigerant compressor While a damping element provided in the lines always has the disadvantage that, even if it acts optimally, while it is able to dampen the pulsations at the point at which it is arranged, it still remains, however, until Damping element, the unwanted pulsations occur and cause unwanted noise and other disturbances.
  • the decoupling between the damper channel and the pressure chamber is also favored by the fact that the cross-sectional jump between the damper channel and the pressure chamber is at least a factor of 5, in which case a jump in cross section from the large cross section of the pressure chamber to a smaller by a factor of 5 cross-section, namely, the inlet opening of the damper channel occurs.
  • the pressure chamber has a buffer volume which damps pressure oscillations of the compressed refrigerant and ensures that the intermittently from the cylinder chambers to the pressure chamber supplied compressed refrigerant not too large pressure oscillations or pulsations in the pressure room leads.
  • the buffer volume is dimensioned so large that it dampens pressure oscillations so far that they have at most a maximum amplitude of 20% of a mean outlet pressure.
  • the outlet channel also forms a buffer volume for damping pressure oscillations or pulsations.
  • the outlet channel forms an outlet chamber with a buffer volume.
  • the outlet chamber is dimensioned so that the buffer volume so far attenuates pressure oscillations that they have at most a maximum amplitude of 20% of a mean outlet pressure.
  • This solution is particularly favorable when following the outlet channel, preferably flanged to the compressor housing, a valve is provided, so that the outlet channel with the outlet chamber forms a total volume in which pressure oscillations could build up or in which pressure oscillations through the above-mentioned buffer volume can be damped.
  • an advantageous embodiment provides that the damper channel extends at least partially in a damper tube, said damper tube is formed in the simplest case by a separate, inserted into the pressure chamber or the outlet tube.
  • a provision of a damper tube consistently further solution provides that the damper channel extends over its entire length in the damper tube, so that the damper tube is used as an additional part in the compressor housing.
  • the damper tube can be arranged, for example, so that it extends into the pressure chamber.
  • damper tube extends in the outlet channel.
  • a particularly favorable solution provides that the damper tube extends both in the pressure chamber and in the outlet channel in order to open up the possibility of providing a sufficiently large length of the damper tube, on the other hand thereby also the volume of the compressor housing, indirectly through again the dimensions of the outlet channel and the pressure chamber is determined not to adversely affect.
  • the outlet opening of the damper channel lies in an outlet chamber of the outlet channel, since in this case the outlet channel designed as an outlet chamber with a larger volume than the damper tube itself surrounds it and also has a favorable effect on the effect of the damper tube.
  • the outlet chamber has a volume that is more than about 1.5 times, more preferably more than 2 times, the portion of the damper channel located therein.
  • damper channel is formed so that substantially all of the compressed refrigerant flows through the damper channel.
  • the damper channel in the region of a transition of the pressure chamber in the outlet passage passes through a closure element between the pressure chamber and the outlet channel.
  • a closure element can be a collar connected to a damper tube receiving the damper channel.
  • an advantageous embodiment provides that the damper channel has a straightened portion.
  • Such a straightened portion of the damper channel has the great advantage that it can easily be used with the damper tube receiving it.
  • the damper channel has a curved portion.
  • the curved section can in principle be located both in the outlet channel and in the pressure chamber.
  • a particularly favorable solution provides that the curved portion of the damper channel in the cylinder head, in particular in the pressure chamber of the same, is arranged, since in particular the Pressure chamber in any case has a large volume, so that in this case the arrangement of the curved portion in these is favorable.
  • the pressure chamber is arranged in a cylinder head and such a cylinder head due to its removability allows easy accessibility of the pressure chamber and thus easy mounting a damper tube with a curved section.
  • the damper channel is at least partially formed in the compressor housing.
  • a particularly suitable place for this purpose is the cylinder head of the compressor housing, in which the damper channel can be molded in a simple manner, whereby on the one hand the assembly is facilitated and on the other hand, the possibility is created to accommodate the largest possible length of the damper channel.
  • a particularly advantageous construction with respect to the assembly provides that the introduced into the cylinder head damper channel continues in a arranged in the outlet duct damper tube.
  • the inlet opening of the damper channel can point in any direction.
  • a curved portion of the damper channel looks advantageous embodiment, in that the inlet opening of the damper channel outlet valves is arranged facing in the pressure chamber.
  • FIG. 1 to 3 An embodiment of a refrigeration compressor according to the invention, shown in the Fig. 1 to 3 , Comprising a designated as a whole with 10 compressor housing with a crankcase 11, in which two cylinder chambers 12a, 12b are arranged, in which pistons 14a, 14b are oscillatingly movable, wherein the pistons 14a, 14b via connecting rods 16a, 16b with a crankshaft 18 cooperate , which is mounted in the crankcase 11.
  • crankshaft 18 is driven, for example, by a motor, not shown in the drawing, preferably an electric motor.
  • the cylinder chambers 12a, b are closed at the head by a resting on the crankcase 11 valve plate 20 which carries both inlet valves 22a, b and exhaust valves 24a, b.
  • a suction chamber 26 which is connected to a guided through the crankcase 11 suction channel 28 and a pressure chamber 30th
  • the suction chamber 26 and the pressure chamber 30 are both arranged above the valve plate 20 in a cylinder head 32 enclosed by the compressor housing 10, which bell-like the Valve plate 20 engages over and connected to this together with the crankcase 11, for example via screws.
  • the cylinder head 32 has an outer wall 34, which encloses the suction chamber 26 and the pressure chamber 30 on the outside, and a partition wall 36 which extends between opposite regions of the outer wall 34 for the separation of the suction chamber 26 and the pressure chamber 30. Both the outer wall 34 and the partition 36 extend from the valve plate 20 to a cylinder head cover 38, which closes the suction chamber 26 and the pressure chamber 30 on its opposite side of the valve plate 20.
  • a breakthrough 40 is provided so that a connection between the pressure chamber 30 and provided in the compressor housing 10, preferably formed in a crankcase 11, outlet channel 42, which then in turn opens into an outlet opening 44, to which a usual, not graphically illustrated line system connects.
  • the outlet channel 42 is preferably formed as extending relative to the opening 40 and the outlet opening 44 again narrowing outlet chamber 46.
  • damper channel which is arranged in the first embodiment in a damper tube 51, which on the one hand extends in the pressure chamber 30, then passes through the opening 40 and then in the outlet chamber 46 also extends.
  • the damper channel 50 has a straightened portion 52, with which the damper channel 50 extends through the aperture 40 into the outlet chamber 46 and opens in this with an outlet opening 54, due to the enlarged cross-sectional configuration of the outlet chamber 46 relative to the opening 40th the portion 52 extends in a central region at a distance from walls 56 of the outlet chamber 46, so that at the outlet opening 54 results in a cross-sectional jump from the small cross section of the outlet opening on the large cross section of the outlet chamber 46 at this point, preferably at least a factor of 5, even better a factor of 10, is.
  • the straight portion 52 further extends through the aperture 40 through into the pressure chamber 30 and in this up to a curved portion 58 of the damper channel 50, which in the connection to the straightened portion 52 inverted U-shaped bent and with an inlet opening 60 of Valve plate 20 is facing. Also in the region of the inlet opening 60, a cross-sectional jump from the large cross section of the pressure chamber 30 is provided at this point to the small cross section of the inlet opening 60, which is preferably at least a factor of 5, even better a factor of 10.
  • the damper channel 50 also has a length which is calculated from the fact that at the most frequently occurring pulsation frequency reflection at the open end should occur, so that the returning wave extinguishes the incoming wave.
  • the pressure chamber 30 is preferably dimensioned so large that it represents a buffer volume, the pressure pulsations through the By-pass supply of compressed refrigerant already damps, preferably so far attenuates that a maximum amplitude of pressure oscillations is less than 20% of a mean outlet pressure in the pressure chamber 30.
  • the damping of pressure pulsations is further improved by the fact that the outlet channel 42, preferably the outlet chamber 46, form a buffer volume, the oscillations in the outlet channel 42 from the damper channel 50 decouple, wherein the attenuation is preferably so large that a maximum amplitude of pressure oscillations is less than 20% of a mean outlet pressure in the outlet channel 42.
  • the damper tube 51 is preferably provided with a collar 62 which is supported on an upper surface 64 of the valve plate 20, wherein the damper tube 51 is fixed by this with respect to its position relative to the valve plate 20 and also by the collar 62 such a seal of the damper tube 51 relative Breakthrough 40 is carried out that substantially all the entering into the pressure chamber 30 compressed refrigerant flows through the damper channel 50 into the outlet chamber 46 in that it enters the pressure chamber 30 in the inlet port 60 of the damper channel 50, flows through this and the outlet opening 54th the same exits while flowing into the outlet chamber 46 and from this then to the outlet opening 44 in the usually connected lines, for example, as a first element of these lines, a valve is provided, so that in this case the buffer volume of the outlet channel 42 plays a significant role.
  • FIG Fig. 4 In a variant of the embodiment according to the invention, shown in FIG Fig. 4 , those parts which are identical to those of the first embodiment are given the same reference numerals, so that the description of the same may be made in its entirety by reference to the first embodiment.
  • the damper tube 51 'used in this variant comprises only the straightened portion 52 of the damper channel 50 and extends therewith from the pressure chamber 30 in the outlet chamber 46, in which case the inlet port 60 of the valve plate 20 is disposed facing away from and in the direction of the cylinder head cover 38 has.
  • the damper tube 51 'with the damper channel 50 according to the simplified embodiment in Fig. 4 the same effect as the damper tube 51 according to the first embodiment, as long as the length of the damper channel 50 is sufficient to satisfactorily attenuate the pulsations occurring, and if appropriate, sufficient buffer volumes are provided.
  • FIG Fig. 5 In a fifth embodiment of a refrigerant compressor according to the invention, shown in FIG Fig. 5 , those parts which are identical to those of the first embodiment are given the same reference numerals, so that reference is made to the description of the same to the first and optionally second embodiments.
  • the damper channel 50 is formed in principle analogous to the first embodiment, wherein in the outlet chamber 46, a damper tube 51 "is provided which extends from the outlet opening 54 to the valve plate 20 and a first straightened portion 52a of the damper channel 50 receives.
  • the damper tube 51 is connected in the region of the opening 40 through the valve plate 20 with this.
  • the damper channel 50 extends with a second straightened portion 52 b up to the U-shaped bent portion 58, which in turn ends with the valve plate 20 facing inlet port 60.
  • Both the second straightened portion 52 b and the U-shaped bent portion 58 of the damper channel 50 extend in contrast to the first embodiment not in the damper tube 51, but are formed as channels in the cylinder head 32 as a whole, including the cylinder head 32 with a channel wall 70th is provided, which first parallel to the outer wall 34, then merges into a channel wall 72 which extends parallel to the cylinder head cover 38 and finally into a channel wall 74 which is parallel to the partition wall 36, wherein the walls 70, 72 and 74 respectively from the outer wall 34, the cylinder head cover 38 and the partition wall 36, starting from the damper channel 50, for example, enclose U-shaped and in turn to the outer wall 34, the cylinder head cover 38 and the partition 36 are returned.
  • the channel walls 70, 72 and 74 integrally formed on the cylinder head 32 and form a unit with this, so that with attachment of the cylinder head 32 on the valve plate 20 is a connection to the damper tube 51 '' made on the opening 40 and also in the Cylinder head 32 extending portion of the damper channel 50 is present.
  • the damper pipe 51 ' can be fixedly connected to the valve plate 20, for example, before assembling the refrigerant compressor, so that with the mounting of the valve plate 20, the damper pipe 51 "is already mounted in the refrigerant compressor.

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

Claims (25)

  1. Compresseur frigorifique, comprenant un carter de compresseur (10), au moins une chambre de cylindre (12) agencée dans un carter de vilebrequin (11) du carter de compresseur (10), un piston (14) mobile par oscillation dans la chambre de cylindre (12), une plaque de soupape (20) terminant les chambres de cylindre (12) côté tête, un espace d'aspiration (26) agencé dans une tête de cylindre (32) recouvrant en forme de cloche la plaque de soupape (20) monté en amont de la chambre de cylindre (12), duquel un agent frigorifique entre dans la chambre de cylindre (12), un espace de compression (30) agencé dans la tête de cylindre (12) monté en aval de la chambre de cylindre (12), dans lequel entre un agent frigorifique comprimé dans la chambre de cylindre (12), un canal de sortie (42) et un canal amortisseur (50), par lequel l'agent frigorifique comprimé passe de l'espace de compression (30) dans le canal de sortie (42), une ouverture d'entrée (60) du canal amortisseur (50) débouchant avec un saut de section dans l'espace de compression (30) et une ouverture de sortie (54) du canal amortisseur (50) débouchant avec un saut de section dans le canal de sortie (42), le canal de sortie (42) étant formé dans le carter de vilebrequin (11) et le canal amortisseur (50) traversant la plaque de soupape (20),
    caractérisé en ce que le canal amortisseur (50) présente une longueur qui se calcule du fait que pour la fréquence de pulsation survenant le plus souvent une réflexion doit se produire sur l'extrémité ouverte de sorte que l'onde en retour efface l'onde arrivant.
  2. Compresseur frigorifique selon la revendication 1, caractérisé en ce que le saut de section entre le canal amortisseur (50) et le canal de sortie (42) s'élève au moins à un facteur 5.
  3. Compresseur frigorifique selon la revendication 2, caractérisé en ce que le saut de section entre le canal amortisseur (50) et le canal de sortie (42) s'élève au moins à un facteur 10.
  4. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le saut de section entre le canal amortisseur (50) et l'espace de compression (30) s'élève au moins à un facteur 5.
  5. Compresseur frigorifique selon la revendication 4, caractérisé en ce que le saut de section entre le canal amortisseur (50) et l'espace de compression (30) s'élève au moins à un facteur 10.
  6. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace de compression (30) présente un volume tampon qui amortit des oscillations de pression de l'agent frigorifique comprimé.
  7. Compresseur frigorifique selon la revendication 6, caractérisé en ce que le volume tampon amortit des oscillations de pression dans la mesure où celles-ci présentent au maximum une amplitude maximale de 20 % d'une pression de sortie moyenne.
  8. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de sortie (42) forme une chambre de sortie (46) avec un volume tampon.
  9. Compresseur frigorifique selon la revendication 8, caractérisé en ce que la chambre de sortie (46) présente un volume tampon qui amortit des oscillations de pression dans la mesure où celles-ci présentent au maximum une amplitude maximale de 20 % d'une pression de sortie moyenne.
  10. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) s'étend au moins en partie dans un tube amortisseur (51, 51').
  11. Compresseur frigorifique selon la revendication 10, caractérisé en ce que le canal amortisseur (50) s'étend sur l'ensemble de sa longueur dans le tube amortisseur (51, 51').
  12. Compresseur frigorifique selon la revendication 10 ou 11, caractérisé en ce que le tube amortisseur (51, 51') s'étend dans l'espace de pression (30).
  13. Compresseur frigorifique selon l'une quelconque des revendications 10 à 12, caractérisé en ce que le tube amortisseur (51, 51', 51") s'étend dans le canal de sortie (42).
  14. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'ouverture de sortie (54) du canal amortisseur (50) se trouve dans une chambre de sortie (46) du canal de sortie (42).
  15. Compresseur frigorifique selon la revendication 14, caractérisé en ce que l'ouverture de sortie (54) du canal amortisseur (50) se trouve dans une zone médiane de la chambre de sortie (46).
  16. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) est utilisé de sorte que sensiblement l'ensemble de l'agent frigorifique compressé traverse le tube amortisseur (51).
  17. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) traverse dans la zone d'un passage de l'espace de compression (30) dans le canal de sortie (42) un élément de fermeture (62) entre l'espace de compression (30) et le canal de sortie (42).
  18. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) présente une section redressée (52).
  19. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) présente une section courbée (58).
  20. Compresseur frigorifique selon la revendication 19, caractérisé en ce que la section courbée (58) du canal amortisseur (50) est agencée dans l'espace de compression (30).
  21. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal amortisseur (50) est formé au moins en partie dans le carter de compresseur (10).
  22. Compresseur frigorifique la revendication 21, caractérisé en ce que le canal amortisseur (50) est formé dans une tête de cylindre (32) du carter de compresseur (10).
  23. Compresseur frigorifique selon la revendication 22, caractérisé en ce que le canal amortisseur (50) s'étend le long d'un couvercle de tête de cylindre (38) et d'au moins une paroi (34) de la tête de cylindre (32).
  24. Compresseur frigorifique selon la revendication 22 ou 23, caractérisé en ce que le canal amortisseur (50) formé dans la tête de cylindre (32) se prolonge dans un tube amortisseur (51") agencé dans le canal de sortie (42).
  25. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'ouverture d'entrée (60) du canal amortisseur (50) est agencée tournée vers la plaque de soupape (20).
EP98124260.5A 1997-12-24 1998-12-18 Silencieux d'un compresseur pour fluides frigorigènes Expired - Lifetime EP0926343B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997157829 DE19757829A1 (de) 1997-12-24 1997-12-24 Kältemittelkompressor
DE19757829 1997-12-24

Publications (3)

Publication Number Publication Date
EP0926343A2 EP0926343A2 (fr) 1999-06-30
EP0926343A3 EP0926343A3 (fr) 2000-05-10
EP0926343B1 true EP0926343B1 (fr) 2015-08-19

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Application Number Title Priority Date Filing Date
EP98124260.5A Expired - Lifetime EP0926343B1 (fr) 1997-12-24 1998-12-18 Silencieux d'un compresseur pour fluides frigorigènes

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DE (1) DE19757829A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10003882C2 (de) * 2000-01-29 2003-10-02 Bitzer Kuehlmaschinenbau Gmbh Kältemittelkompressor
DE10242139A1 (de) * 2002-09-03 2004-03-18 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
DE102014010018A1 (de) 2014-07-08 2016-01-14 Gea Bock Gmbh Verdichter
DE102021205041A1 (de) * 2021-05-18 2022-11-24 Thyssenkrupp Ag Kolbenverdichter, insbesondere Radialkolbenverdichter

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US3785453A (en) * 1970-12-10 1974-01-15 Carrier Corp Compressor discharge muffling means
DE2134181A1 (de) * 1971-03-03 1973-11-15 Monsator Haushaltsgrossgeraete Daempfer fuer verdichter, insbesondere fuer hermetische kaeltemittelverdichter
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DE3332259A1 (de) * 1983-09-07 1985-03-28 Danfoss A/S, Nordborg Kaeltemaschinenverdichter
JPS60152077U (ja) * 1984-03-21 1985-10-09 株式会社豊田自動織機製作所 斜板式圧縮機
JPH0717827Y2 (ja) * 1987-03-11 1995-04-26 株式会社豊田自動織機製作所 圧縮機のマフラー機構
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JP2763734B2 (ja) * 1993-05-20 1998-06-11 松下冷機株式会社 密閉型圧縮機

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Publication number Publication date
DE19757829A1 (de) 1999-07-01
EP0926343A2 (fr) 1999-06-30
EP0926343A3 (fr) 2000-05-10

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