EP1165963B1 - Compresseur frigorifique - Google Patents

Compresseur frigorifique Download PDF

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Publication number
EP1165963B1
EP1165963B1 EP01911527A EP01911527A EP1165963B1 EP 1165963 B1 EP1165963 B1 EP 1165963B1 EP 01911527 A EP01911527 A EP 01911527A EP 01911527 A EP01911527 A EP 01911527A EP 1165963 B1 EP1165963 B1 EP 1165963B1
Authority
EP
European Patent Office
Prior art keywords
accordance
channel
refrigerant compressor
refrigerant
section
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
EP01911527A
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German (de)
English (en)
Other versions
EP1165963A1 (fr
Inventor
Günter DITTRICH
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
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Publication of EP1165963A1 publication Critical patent/EP1165963A1/fr
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Publication of EP1165963B1 publication Critical patent/EP1165963B1/fr
Anticipated expiration legal-status Critical
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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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • 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, extending between a first end and a second end damper channel, via which compressed refrigerant flows from the pressure chamber into an outlet channel.
  • Such a refrigerant compressor is for example from the EP 0 926 343 known.
  • the object of the invention is to further optimize such a refrigerant compressor with regard to the damping of pulsations and the space requirement.
  • damper channel has an inlet opening lying between the first end and the second end.
  • the solution according to the invention makes it possible to further optimize the damping of pulsations in refrigerant compressors, namely in that a pressure wave entering the damper channel from the inlet opening propagates both in the direction of the first end and in the direction of the second end and then through reflections both ends of the damper channel the damping of pulsations is even better.
  • the outlet opening can in principle be arranged at different points of the damper channel.
  • a particularly favorable solution provides that the outlet opening is in the region of one of the ends, so that the damper channel is so far traversed by compressed refrigerant, as it is guided from the inlet opening to the outlet opening in the region of one of the ends.
  • the damper channel in addition to the inlet opening has two mouth openings and that at least one of the mouth openings forms the outlet opening.
  • This solution is structurally particularly easy to implement, especially when the mouth openings are arranged in the region of opposite ends.
  • damper channel in such a way that the compressed refrigerant flows through the inlet opening in the damper channel and then flows in the direction of both ends to the respective outlet openings.
  • a solution particularly favorable in terms of its damping effect provides that the damper channel extending between the ends comprises a section through which the compressed refrigerant flows and an acoustically blinded section, ie a section with reflection at the acoustically closed end , wherein in particular the acoustically blinded portion of the damper channel contributes significantly to the damping of pulsations or pressure waves, as in this a reflection of a pressure wave occurs, which then in turn superimposed with subsequently entering through the inlet pressure waves in the damper channel.
  • an acoustically blind portion is formed so that there is an opening or a gap through which oil can flow, so that oil accumulation is avoided.
  • the acoustically blinded section of the damper channel to adjoin the outlet opening, so that a pressure wave entering the damper channel initially migrates from the inlet opening to the outlet opening and then a part of the same does not leave the damper channel through the outlet opening, but continues to propagate from the outlet opening in the acoustically blinded section.
  • the portion traversed by the refrigerant and the acoustically blinded section extend in opposite directions away from the inlet opening, so that in particular reflections in the acoustically blinded section can propagate directly further into the section through which the refrigerant flows.
  • the inlet opening As far as the position of the inlet opening is concerned, no information has yet been given. In principle, it would be conceivable to provide the inlet opening at arbitrary locations between the first end and the second end.
  • a particularly favorable solution provides that the inlet opening is in the region of a central portion of the damper channel, preferably in the range of about half the total length of the damper channel, so that an incoming pressure wave distributed over two orders of magnitude approximately equal lengths.
  • an advantageous embodiment provides that the damper channel in a part which is mountable on the compressor housing and in that the part is mountable on the compressor housing such that either the orifice arranged at the first end or the orifice at the second end serves as an outlet and leads into the outlet duct provided in the compressor housing, for example.
  • Such an acoustically blind completion of the mouth opening could be done for example by an inserted or screwed plug.
  • the part mountable on the compressor housing is the valve plate carried by a crankcase of the compressor housing, which closes it with a region covering the outlet opening.
  • damper channel having and mountable on the compressor housing part no details have been made. So this could be a separate part that is completely independent of the usual parts of the compressor housing and is used as a separate use, for example, during assembly of the cylinder head.
  • damper channel extends in the cylinder head and thus the cylinder head forms the damper channel having and mountable on the compressor housing part.
  • a damper channel forming element such as a damper tube.
  • the damper channel is formed in the cylinder head, that is, for example, when the cylinder head is designed as a casting, is provided in this casting the damper channel.
  • the damper channel it would also be conceivable to realize the damper channel as to be provided in the cylinder head bore.
  • the damper channel extends with a portion in an approximately parallel to a cylinder head cover of the cylinder head surface, that is, that the damper channel, which preferably for damping pulsations with certain frequency components must have a corresponding length, advantageously by its extension in this area may have a sufficient length, without causing the cylinder head builds appreciably larger.
  • the damper channel extends with a substantial portion in the direction of a crankshaft and thus preferably also extends in the direction in which the cylinders are arranged in succession in a multi-cylinder refrigerant compressor.
  • a particularly favorable solution provides that the damper channel extends on a side facing away from the cylinder chambers of the pressure chamber, since thus, for example, the possibility exists, the damper channel along the cylinder head cover, for example, formed on this molded or run in these.
  • the damper channel has in the direction of a crankcase extending end portions, so that these end portions are then provided in a simple manner accessible in the crankcase - preferably accessible via the crankcase - mouth openings can.
  • a particularly favorable solution provides that the mouth openings of the damper channel in a bearing surface of the cylinder head lie and thus, for example, by placing the cylinder head on the rest of the compressor housing in a simple manner, a seal in the mouth openings can be realized.
  • the inlet opening of the damper channel opens with a cross-sectional jump in the pressure chamber and that the outlet opening of the damper channel opens with a cross-sectional jump in the outlet channel.
  • the size of the cross-sectional jumps is preferably such that the cross-sectional jump between the damper channel and the outlet channel is at least a factor of 2 or 3, in which case a cross-sectional jump from a small cross section, namely the outlet opening, to a large cross section, namely that of the outlet channel ,
  • 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 3, even better a factor of 5, in which case a cross-sectional jump of the large cross-section the pressure chamber to a smaller by a factor of 3 or 5 cross-section, namely that of the inlet opening of the damper channel occurs.
  • damper channel As a channel with a constant cross section.
  • damper channel with cross-sectional constrictions, for example generated by diaphragms, in order to increase the damping effect even further, so that the damper channel has different cross-sections at different points in the longitudinal direction.
  • the cross-sectional constrictions and the cross-sectional extensions may be arranged in each section of the damper channel. For example, in the portion traversed by the refrigerant or in the acoustically blinded section.
  • cross-sectional constrictions and cross-sectional enlargements are arranged symmetrically with respect to the inlet opening.
  • FIG. 1 to 5 A first embodiment of a refrigerant compressor according to the invention, shown in FIG Fig. 1 to 5 comprises a compressor housing designated as a whole by 10 with a crankcase 11, in which two cylinder chambers 12a and 12b are arranged, in which pistons 14a, 14b are oscillatingly movable, wherein the pistons 14a, 14b via connecting rods 16a, 16b cooperate with a crankshaft 18, which is arranged in the crankcase 11.
  • crankshaft 18 is driven for example by an electric motor 20, the motor shaft 22 is arranged coaxially with the crankshaft 18 and carries a rotor 24 which is surrounded by a stator 26, which in turn is arranged stationarily in the compressor housing 10.
  • the cylinder chambers 12a and 12b are closed at the head by a resting on the crankcase 11 valve plate 30 which carries both intake valves and exhaust valves 32a and 32b.
  • valve plate 30 On a side opposite the crankcase 11 side of the valve plate 30 is seated as a whole with 40 designated cylinder head, which together with the valve plate 30 on the one hand a suction chamber 34 which lies above the inlet openings and in which to be compressed refrigerant flows via a suction channel 36, and the other a pressure space 38 which overlies the exhaust valves 32a and 32b so that refrigerant discharged through the exhaust valves 32a and 32b enters the pressure space 38 from the cylinder chambers 12a and 12b.
  • the cylinder head 40 comprises an outer wall portion 42 which rests with a bearing surface 44 on a support surface 46 formed by the valve plate 30 and a cylinder head cover 48 which extends over the space enclosed by the outer wall portion 42, comprising the suction space 34th and extends the pressure chamber 38 and extends approximately parallel to the valve plate 30 to complete the suction chamber 34 and the pressure chamber 38 on the valve plate 30 opposite side.
  • the cylinder head 40 also comprises a partition 50, which also extends from the valve plate 30 to the cylinder head cover 58 to separate the suction chamber 34 and the pressure chamber 38 from each other.
  • damper channel 60 As in Fig. 1 to 4 is shown in the cylinder head 40 as a whole designated 60 damper channel, in the region of the partition wall 50 and near the cylinder head cover 48, the damper channel 60 having a central portion 62 parallel to the cylinder head cover 48 and with end portions 64, 66 curved in the region of the outer walls 42 passes and thereby in the region of the first end portion 64 has a first mouth opening 70 and in the region of the second end portion 66 has a second mouth opening 72, which are preferably in the plane of the support surface 44.
  • an inlet opening 74 is provided, which opens into the central region 62 of the damper channel 60.
  • the cylinder head 40 is mounted on the valve plate 30 such that a passage 76 provided in the valve plate 30 is aligned with the first orifice 70, and also protrudes above an inlet 78 of an 80 generally designated as 80 in FIG Crankcase 11 guided outlet channel 80 opens. This flows into the
  • the section 84 thus serves as a so-called “blind section” of the damper channel 60.
  • both the compressed refrigerant flowing through section 82 and the non-flow section 84 of the damper channel 60 are effective because the pulsations or pressure waves entering through the inlet opening 74 propagate in both directions along the sections 82 and 84. All recently occurs in the area 86 of the valve plate 30 acoustically blind closed end portion 66 a reflection at the closed end and the returning pressure waves are then superimposed again with the further entering through the inlet port 74 pressure waves.
  • a partial reflection also takes place at the first orifice 70 in the form of a reflection at the open end, so that superimpose the likewise returning pressure waves again with the entering through the inlet port 74 pressure waves and a total of an advantageous damping effect of the damper channel 60 occurs.
  • the reflection in the region of the mouth opening 70 is due to a cross-sectional jump in the transition from the mouth opening 70 into the outlet channel 80, wherein this cross-sectional jump is at least a factor of 3 with respect to the effective for the outflowing compressed refrigerant cross section.
  • a cross-sectional jump of at least a factor of 3, even better a factor of 5 or greater, is preferably also provided in the region of the inlet opening 74.
  • damper channel 60 whose relevant length for the damping effect of the length of the sections 82 and 84 is that only the portion 82 is flowed through by the exiting compressed refrigerant and thus the resulting pressure loss is less than in the case in which the entire damper channel 60 is flowed through by the compressed refrigerant.
  • the damping effect of the damper channel 60 is further improved by the fact that the inlet opening 74 is located near the cylinder head cover 48 and is preferably formed by a channel portion 88 whose longitudinal axis 90 is not directly the exhaust valves 32a and 32b facing, so that the pulsation or pressure wave first Deflection on the inside 92 of the cylinder head cover learns before it can enter the damper channel 60.
  • an advantageous effect of the damper channel 60 is also achievable in that the inlet port 74 is positioned so that it can be arranged at approximately equal distances from the two exhaust valves 32a and 32b.
  • the solution according to the invention has, as in Fig. 5 shown, still the further advantage that the same inventive cylinder head 40 can also be used for a crankcase 11 ', in which the outlet channel 80' is arranged so that the compressed refrigerant can enter through the second orifice 72 in this and consequently also the Valve plate 30 'has a passage 76', while on the other hand, the valve plate 30 'has a portion 86' which closes the first orifice 70 of the damper channel 60.
  • the damper channel 60 acts in the same way, but in this case the section 84 flows through the compressed refrigerant, while the section 82 represents the so-called "blind portion" of the damper channel 60.
  • a four-cylinder refrigerant compressor can be produced, wherein in two arranged on one side of the compressor housing 10 cylinder chambers 12a and 12b, the corresponding crankcase 11, the in Fig. 1 and 4 shown in the exhaust port 80 and compressed refrigerant flows through the first orifice 70, while on the other side of the compressor housing 10, the corresponding crankcase 11 'is provided, wherein the outlet passage 80' is arranged so that compressed via the second orifice 72 Refrigerant flows into this.
  • the cylinder head according to the invention can be used as a common part in different crankcases 11, 11 'with different outlet channels 80 and 80'.
  • FIG Fig. 6 In a second embodiment, shown in FIG Fig. 6 , those parts which are identical to those of the first embodiment are given the same reference numerals, so that the description of them may be made to the contents of the first embodiment in its entirety.
  • damper channel 60 in each case over its entire length has a constant cross-section, it is provided in the second embodiment that in the damper channel 60 'aperture 100 are used, which vary the cross section of the damper channel 60', so that cross-section narrowed portions 102 of the damper channel 60 'and cross-sectional widened portions 104 of the damper channel 60' follow each other and thus the damping effect can be increased.
  • the arrangement of the cross-sectional narrowed portions 102 and the cross-sectional widened portions 104 is carried out both in the refrigerant-flowing portion 82 and in the acoustically blind portion 84, preferably symmetrically to the inlet port 74th
  • the second embodiment is formed in the same manner as the first embodiment, so that identical parts are provided with identical reference numerals and thus the description thereof in conjunction with the first embodiment may be fully incorporated by reference.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)

Claims (20)

  1. Compresseur de réfrigérant, comprenant un carter de compresseur (10), au moins une chambre de cylindre (12) disposée dans le carter de compresseur (10), un piston (14) mobile oscillant dans la chambre de cylindre (12), une chambre d'aspiration (34) montée en amont de la chambre de cylindre (12), depuis laquelle du réfrigérant est admis dans la chambre de cylindre (12), une chambre de pression (38) montée en aval de la chambre de cylindre (12), où est admis du réfrigérant comprimé dans la chambre de cylindre (12), un canal d'amortissement (60) s'étendant entre une première extrémité (64) et une deuxième extrémité (66) par lequel du réfrigérant comprimé s'écoule de la chambre de pression (38) vers le canal de sortie (80), caractérisé en ce que le canal d'amortissement (60) comporte une ouverture d'admission (74) disposée entre la première extrémité (64) et la deuxième extrémité (66).
  2. Compresseur de réfrigérant selon la revendication 1, caractérisé en ce que l'ouverture de sortie (70, 72) est située au niveau d'une des extrémités (64, 66).
  3. Compresseur de réfrigérant selon la revendication 1 ou la revendication 2, caractérisé en ce que le canal d'amortissement (60) comporte deux embouchures (70, 72) en plus de l'ouverture d'admission (74), et en ce qu'au moins une des embouchures (70, 72) forme l'ouverture de sortie.
  4. Compresseur de réfrigérant selon la revendication 3, caractérisé en ce que les deux embouchures (70, 72) sont situées au niveau d'extrémités opposées (64, 66).
  5. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60) s'étendant entre les deux extrémités (64, 66) comporte un tronçon (82) où s'écoule le réfrigérant comprimé et un tronçon (84) obturé de manière acoustiquement isolante.
  6. Compresseur de réfrigérant selon la revendication 5, caractérisé en ce que le tronçon (82) où s'écoule le réfrigérant comprimé et le tronçon (84) obturé de manière acoustiquement isolante du canal d'amortissement (60) s'étendent en s'éloignant de l'ouverture d'admission (74).
  7. Compresseur de réfrigérant selon la revendication 5 ou la revendication 6, caractérisé en ce que le tronçon (82) où s'écoule le réfrigérant comprimé et le tronçon (84) obturé de manière acoustiquement isolante s'éloignent dans des directions opposées de l'ouverture d'admission (74).
  8. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que l'ouverture d'admission (74) est située au niveau d'un tronçon central (62) du canal d'amortissement (60).
  9. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60) est disposé dans une pièce (40) montable sur le carter de compresseur (10), et en ce que la pièce (40) est montable sur le carter de compresseur (10) de telle manière que l'embouchure (70) disposée à la première extrémité (64), ou bien l'embouchure (72) disposée à la deuxième extrémité (66) serve d'ouverture de sortie et aboutisse dans le canal de sortie (80, 80') prévu.
  10. Compresseur de réfrigérant selon la revendication 9, caractérisé en ce que l'embouchure (70, 72) qui n'aboutit pas dans le canal de sortie (80, 80') est obturée de manière acoustiquement isolante.
  11. Compresseur de réfrigérant selon la revendication 10, caractérisé en ce que l'embouchure (70, 72) obturée de manière acoustiquement isolante est fermée par une zone (86, 86') de la pièce (30) qui supporte la pièce (40) montable sur le carter de compresseur (10).
  12. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60) s'étend dans la tête de cylindre (40).
  13. Compresseur de réfrigérant selon la revendication 12, caractérisé en ce que le canal d'amortissement (60) est formé dans la tête de cylindre (40).
  14. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60) s'étend par un tronçon (62) sur une surface s'étendant sensiblement parallèlement à un couvercle (48) de la tête de cylindre (40).
  15. Compresseur de réfrigérant selon la revendication 14, caractérisé en ce que le canal d'amortissement (60) s'étend par un tronçon (62) substantiel dans la direction d'un vilebrequin (18).
  16. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60) s'étend sur un côté de la chambre de pression (38) opposé aux chambres de cylindre (12).
  17. Compresseur de réfrigérant selon la revendication 16, caractérisé en ce que le canal d'amortissement (60) comporte des parties d'extrémité (64, 66) s'étendant dans la direction d'un carter (11) de vilebrequin.
  18. Compresseur de réfrigérant selon la revendication 17, caractérisé en ce que les embouchures (70, 72) sont dirigées vers le carter (11) de vilebrequin.
  19. Compresseur de réfrigérant selon la revendication 17 ou la revendication 18, caractérisé en ce que les embouchures (70, 72) du canal d'amortissement (60) sont situées sur une surface d'appui (44) de la tête de cylindre (40).
  20. Compresseur de réfrigérant selon l'une des revendications précédentes, caractérisé en ce que le canal d'amortissement (60') comporte des rétrécissements de section (102) et des élargissements de section (104).
EP01911527A 2000-01-29 2001-01-25 Compresseur frigorifique Expired - Lifetime EP1165963B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10003882 2000-01-29
DE10003882A DE10003882C2 (de) 2000-01-29 2000-01-29 Kältemittelkompressor
PCT/EP2001/000783 WO2001055594A1 (fr) 2000-01-29 2001-01-25 Compresseur frigorifique

Publications (2)

Publication Number Publication Date
EP1165963A1 EP1165963A1 (fr) 2002-01-02
EP1165963B1 true EP1165963B1 (fr) 2009-04-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP01911527A Expired - Lifetime EP1165963B1 (fr) 2000-01-29 2001-01-25 Compresseur frigorifique

Country Status (8)

Country Link
US (1) US6568921B2 (fr)
EP (1) EP1165963B1 (fr)
CN (1) CN1114760C (fr)
AT (1) ATE428052T1 (fr)
DE (2) DE10003882C2 (fr)
DK (1) DK1165963T3 (fr)
ES (1) ES2322430T3 (fr)
WO (1) WO2001055594A1 (fr)

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DE10003882A1 (de) 2001-08-16
DE50114814D1 (de) 2009-05-20
DK1165963T3 (da) 2009-08-03
ES2322430T3 (es) 2009-06-22
US6568921B2 (en) 2003-05-27
EP1165963A1 (fr) 2002-01-02
WO2001055594A1 (fr) 2001-08-02
CN1114760C (zh) 2003-07-16
US20020062657A1 (en) 2002-05-30
CN1363018A (zh) 2002-08-07
ATE428052T1 (de) 2009-04-15
DE10003882C2 (de) 2003-10-02

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