EP0300884A1 - Hermetic or semi-hermetic refrigeration motor compressor unit - Google Patents

Hermetic or semi-hermetic refrigeration motor compressor unit Download PDF

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Publication number
EP0300884A1
EP0300884A1 EP88401839A EP88401839A EP0300884A1 EP 0300884 A1 EP0300884 A1 EP 0300884A1 EP 88401839 A EP88401839 A EP 88401839A EP 88401839 A EP88401839 A EP 88401839A EP 0300884 A1 EP0300884 A1 EP 0300884A1
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Prior art keywords
pressure
engine
compressor
hole
piston
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EP88401839A
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German (de)
French (fr)
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EP0300884B1 (en
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Bernard Zimmern
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a refrigerated, hermetic or semi-hermetic motor-compressor fitted with an economizer.
  • hermetic motor-compressors are those in which sealing is obtained by welded assemblies, while semi-hermetic motor-compressors are those in which sealing is obtained by dismountable connections and seals .
  • Hermetic or semi-hermetic motor-compressors are known in which the engine is cooled by gas or liquid, or a mixture of gas and liquid coming from the condenser of the refrigeration circuit.
  • the gas including the volume of gas created by the vaporization necessary to cool the engine is sent from the engine to an economizer hole of the compressor, this economizer hole being at an intermediate pressure between the intake pressure and the pressure of compressor exhaust.
  • each compression chamber When a compressor such as a screw compressor operates under partial load, the closing of each compression chamber with respect to the compressor inlet is delayed until the volume of this room has decreased significantly. This reduces the effective capacity of each chamber, and therefore the capacity of the compressor. Under these conditions, each room is only closed when it will soon communicate or already communicates with the economizer hole. Thus, the pressure in the economizer hole is very close to the intake pressure and the engine is therefore no longer at an intermediate pressure between the intake and the discharge. This leads to a series of problems since, for example, it becomes difficult to evacuate the liquid from the engine to the evaporator, in particular if the evaporator is in an elevated position relative to the engine.
  • the object of the invention is to overcome these problems.
  • the refrigerating motor-compressor comprising a rotary positive displacement compressor driven by a motor, means for introducing refrigerating fluid into the interior of the engine to cool the engine, said interior being connected by a pipe to a hole economizer of the compressor, is characterized by closing means arranged in said pipe for at least partially closing off the latter, these closing means being connected to an inlet pressure of the compressor and being designed to release said pipe when the pressure at the hole economiser exceeds the inlet pressure by a predetermined differential pressure.
  • the closure means reduces the flow rate, and this establishes, upstream of the closure means, a pressure which preferably is determined by the action of a spring on the closure means. It is thus possible to maintain in the engine a minimum pressure useful for removing from the engine the liquid separated from the gas. But when the compressor operates at full speed, this throttling of the flow would adversely affect the efficiency since it would create a pressure drop between the engine and the economiser hole, and would lead to supplying the economiser hole with gas whose pressure would be reduced by the closing means.
  • the piston can be mounted in an extension of the pipe between the interior space of the engine and the economiser hole, and when said difference - or differential pressure - exceeds the threshold, the piston retracts beyond the economizer hole so that the line between the economizer hole and the inside of the engine is completely clear of any piston when the compressor is at full speed. This is achieved by taring the spring so that its force is significantly less than the force created on the piston by the differential pressure when it is equal to the threshold.
  • a shaft 1 ( Figure 1) carries a cooperating screw 2 with pinions (not shown) as is well known for example from US-A-3 180 565.
  • This shaft is supported by bearings 3 and 4 and rotated by an electric motor consisting of a rotor 5 attached to the shaft 1 beyond the bearing 4 and rotating inside a stator 6 which is fixed in an envelope 7 secured to the casing 8 of the compressor.
  • the casing 7 is sealed and the interior space of the casing 7 is sealed from the inlet 20 of the compressor by means of a bearing support flange 4a, carrying a bearing 4.
  • the bearing support flange 4a is provided with a sealing device 22 cooperating with the shaft 1.
  • the discharge port 31 of the compressor is connected to an intake port 32 of the compressor through a refrigeration circuit comprising in series in the following order: a condenser 33, a tank 34, an expansion valve 36 and an evaporator 37.
  • the casing 8 is provided with an economizer hole 9 as described in numerous patents, for example US-A-4,261,691, this hole being connected to the inside of the casing 7 of the engine by a pipe 10 .
  • the engine is cooled by liquid and / or gas reaching the interior of the casing 7 of the engine by a pipe 11 which is shown in the axis of the engine but which could be located elsewhere, for example at the top of the engine.
  • the liquid and / or gas arriving in the casing 7 through the pipe 11 may be, as shown, liquid arriving directly from the condenser 33 to through a conduit and partially vaporizing in the engine as described in US-A-4,573,324. This may also be liquid with or without gas coming from a centrifugal economizer which would be mounted at the end of the shaft 1 beyond the rotor 5. Such a centrifugal economizer is described in US - A - 4,509,341. It could also be, quite simply, gas from a conventional economizer.
  • the motor casing is generally used to separate the liquid intended to be discharged to another point.
  • the liquid is collected in the bottom of the casing 7 and sent to the evaporator 37 by a conduit 38, by exploiting the prevailing pressure in the casing 7, pressure which is higher than downstream of the valve 36.
  • the differential pressure in a conventional air conditioning system can range between 200 to 300 and 800 to 900 kPa.
  • This differential pressure is useful for moving the liquid refrigerant towards the evaporator, particularly when the evaporator is installed at a level higher than that of the compressor, or to move the oil.
  • a piston 12 is mounted in a sliding and sealed manner in an extension 13 of the pipe 10.
  • This extension extends between the economizer hole and a space 19 subjected to the intake pressure, provided at- beyond bearing 3 away from the engine.
  • the space 19 is connected to the intake region 20 through the bearing 3 and through a passage 21 passing through the screw 2.
  • the piston 12 thus has a front face 12a subjected to the economizer pressure and a rear face 12b , of the same area, subject to inlet pressure.
  • the piston 12 is biased by a spring 14 so that, in the absence of differential pressure, the piston 12 moves to its position 15 shown in dotted lines, close to a shoulder 16 of the pipe 10, and forms therewith. ci a choke 17.
  • the front face 12a of the piston 12 is at economiser pressure while the rear face 12b is subjected to the intake pressure.
  • the spring 14 is designed so that in the position shown in solid lines, in which the economizer hole 9 is completely released by the piston 12, the elastic force is balanced by a differential pressure equal to a threshold value of approximately 25 kPa, i.e. corresponding to a pressure at the economiser hole exceeding 25 kPa the intake pressure.
  • the extension 13 is no longer provided, and the piston 12 is housed in a bore 39 which is arranged in the casing 8 transversely to the axis of the motor-compressor, so as to connect the pipe 10 and the intake region 20.
  • the bore 39 has a shoulder 16 designed to cooperate with the face 12a of the piston 12.
  • the spring 14 is a tension spring extending through the shoulder 16.
  • the spring 14 brings the piston 12 back towards the shoulder 16 and the piston 12 forms therewith a pressure regulating throttle, maintaining in the part 10a, and consequently in the motor casing 7, a pressure significantly exceeding 25 kPa the intake pressure.
  • the closure means is a butterfly 112 which is pivotally mounted in the pipe 10 between the portions 10a and 10b thereof, about a pivot axis 41 which is offset laterally with respect to the axis 42 of the pipe 10.
  • a lever 43 rigidly connected to the downstream face of the butterfly 112 is pivotally and slidingly connected to a rod 44 of a piston 46 mounted in a sliding and sealed manner in a bore 47 extending between the part 10b of the pipe 10 and the admission region 20.
  • the piston 46 thus has a front face 46a subjected to the pressure at the economizer hole, and a rear face 46b subjected to the intake pressure.
  • the pressure at the economizer hole acts on the piston 46 to open the butterfly 112.
  • the intake pressure and the return spring 14 act together on the piston 46 in the direction of closing the butterfly 112.
  • the piston 46 opens the butterfly 112.
  • the present invention has been described in the case of a single screw compressor but could, without change, apply to any type of compressor which can be equipped with an economizer hole, in particular a stationary economizer, for example twin screw compressors, mobile vane compressors, fixed vane compressors.
  • the closure member instead of regulating the pressure in the engine casing when the differential pressure at the economiser hole is low, could simply create a fixed calibrated passage for the gas coming from the engine casing.
  • the shutter could be of different types from the examples which have been described.

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

Abstract

Du liquide provenant du condenseur (34) est fourni à l'intérieur du moteur par un conduit (11) et s'y vaporise tout en refroidissant le moteur. Le gaz qui en résulte est envoyé par une conduite (10) à un trou d'économiseur (9) du compresseur. A pleine charge, le trou (9) est à une pression supérieure à la pression d'admission du compresseur. A charge partielle, le trou (9) est à une pression voisine de la pression d'admission. Un piston (12) est soumis sur une face (12a) à la pression à l'intérieur du moteur, et sur l'autre face à la pression d'aspiration. Lorsque les deux pressions tendent à devenir égales, le piston (12) se déplace vers un épaulement (16) pour créer avec lui une perte de charge élevant la pression dans l'enveloppe moteur (7), de manière à y maintenir une pression capable de refouler le liquide depuis le moteur jusqu'à l'évaporateur (37) à travers un conduite (38). Utilisation pour refouler de manière fiable le liquide vers l'évaporateur même à régime partiel.Liquid from the condenser (34) is supplied to the interior of the engine through a conduit (11) and vaporizes therein while cooling the engine. The resulting gas is sent through a line (10) to an economizer hole (9) in the compressor. At full load, the hole (9) is at a pressure higher than the inlet pressure of the compressor. At partial load, the hole (9) is at a pressure close to the intake pressure. A piston (12) is subjected on one side (12a) to the pressure inside the motor, and on the other side to the suction pressure. When the two pressures tend to become equal, the piston (12) moves towards a shoulder (16) to create with it a pressure drop raising the pressure in the engine casing (7), so as to maintain a pressure capable thereof. to discharge the liquid from the engine to the evaporator (37) through a line (38). Use to reliably discharge the liquid to the evaporator even at partial speed.

Description

La présente invention concerne un moto-­compresseur frigorifique, hermétique ou semi-hermétique muni d'un économiseur.The present invention relates to a refrigerated, hermetic or semi-hermetic motor-compressor fitted with an economizer.

Selon une terminologie généralement admise, les moto-compresseurs hermétiques sont ceux dans lesquels l'étanchéïté est obtenue par des assemblages soudés, tandis que les moto-compresseurs semi-hermétiques sont ceux dans lesquels l'étanchéïté est obtenue par des liaisons démontables et des joints.According to generally accepted terminology, hermetic motor-compressors are those in which sealing is obtained by welded assemblies, while semi-hermetic motor-compressors are those in which sealing is obtained by dismountable connections and seals .

On connaît des moto-compresseurs hermétiques ou semi-hermétiques dans lesquels le moteur est refroidi par du gaz ou du liquide, ou un mélange de gaz et de liquide venant du condenseur du circuit frigorifique. Le gaz incluant le volume de gaz créé par la vaporisation nécessaire pour refroidir le moteur est envoyé du moteur à un trou d'économiseur du compresseur, ce trou d'économiseur étant à une pression intermédiaire entre la pression d'admission et la pression d'échappement du compresseur.Hermetic or semi-hermetic motor-compressors are known in which the engine is cooled by gas or liquid, or a mixture of gas and liquid coming from the condenser of the refrigeration circuit. The gas including the volume of gas created by the vaporization necessary to cool the engine is sent from the engine to an economizer hole of the compressor, this economizer hole being at an intermediate pressure between the intake pressure and the pressure of compressor exhaust.

Les US-A- 4 553 399 et 4 573 324 donnent des exemples de tels moto-compresseurs.US-A-4,553,399 and 4,573,324 give examples of such motor-compressors.

Il est plus avantageux d'envoyer au trou d'économiseur le gaz résultant de l'écoulement de refroidissement à travers le moteur que d'envoyer ce gaz à l'admission du compresseur, car cela permet au compresseur d'utiliser entièrement sa capacité d'admission pour aspirer du gaz provenant de l'évaporateur. En d'autres termes, l'utilisation d'un débit partiel pour refroidir le moteur ne se traduit pas par une réduction de la capacité frigorifique de la machine.It is more advantageous to send the gas resulting from the cooling flow through the engine to the economizer hole than to send this gas to the compressor inlet, as this allows the compressor to fully utilize its capacity. inlet to suck gas from the evaporator. In other words, the use of partial flow to cool the engine does not result in a reduction of the refrigerating capacity of the machine.

Lorsqu'un compresseur tel qu'un compresseur à vis fonctionne sous charge partielle, la fermeture de chaque chambre de compression par rapport à l'admission du compresseur est retardée jusqu'à ce que le volume de cette chambre ait sensiblement diminué. Ceci réduit la capacité effective de chaque chambre, et par conséquent la capacité du compresseur. Dans ces conditions, chaque chambre n'est fermée que lorsqu'elle va bientôt communiquer ou communique déjà avec le trou d'économiseur. Ainsi, la pression dans le trou d'économiseur est très voisine de la pression d'admission et le moteur n'est donc plus à une pression intermédiaire entre l'admission et le refoulement. Ceci conduit à une série de problèmes car il devient par exemple difficile d'évacuer le liquide du moteur vers l'évaporateur, en particulier si l'évaporateur se trouve en position surélevée par rapport au moteur.When a compressor such as a screw compressor operates under partial load, the closing of each compression chamber with respect to the compressor inlet is delayed until the volume of this room has decreased significantly. This reduces the effective capacity of each chamber, and therefore the capacity of the compressor. Under these conditions, each room is only closed when it will soon communicate or already communicates with the economizer hole. Thus, the pressure in the economizer hole is very close to the intake pressure and the engine is therefore no longer at an intermediate pressure between the intake and the discharge. This leads to a series of problems since, for example, it becomes difficult to evacuate the liquid from the engine to the evaporator, in particular if the evaporator is in an elevated position relative to the engine.

Le but de l'invention est de surmonter ces problèmes.The object of the invention is to overcome these problems.

Selon l'invention, le moto-compresseur frigorifique comprenant un compresseur volumétrique rotatif entraîné par un moteur, des moyens pour introduire du fluide frigorifique à l'intérieur du moteur pour refroidir le moteur, ledit intérieur étant relié par une conduite à un trou d'économiseur du compresseur, est caractérisé par des moyens de fermeture disposés dans ladite conduite pour obturer au moins partiellement celle-­ci, ces moyens de fermeture étant reliés à une pression d'admission du compresseur et étant conçus pour dégager ladite conduite lorsque la pression au trou d'économiseur dépasse d'une pression différentielle prédéterminée la pression d'admission.According to the invention, the refrigerating motor-compressor comprising a rotary positive displacement compressor driven by a motor, means for introducing refrigerating fluid into the interior of the engine to cool the engine, said interior being connected by a pipe to a hole economizer of the compressor, is characterized by closing means arranged in said pipe for at least partially closing off the latter, these closing means being connected to an inlet pressure of the compressor and being designed to release said pipe when the pressure at the hole economiser exceeds the inlet pressure by a predetermined differential pressure.

Lorsque le compresseur fonctionne à régime partiel, la pression au trou d'économiseur tombe à la pression d'admission, ou se rapproche de celle-ci. Dans ce cas, le moyen de fermeture réduit le débit, et ceci établit, en amont du moyen de fermeture, une pression qui de préférence est déterminée par l'action d'un ressort sur le moyen de fermeture. Il est ainsi possible de maintenir dans le moteur une pression minimale utile pour évacuer du moteur le liquide séparé du gaz. Mais quand le compresseur fonctionne à plein régime, cet étranglement de l'écoulement nuirait au rendement car il créerait une perte de charge entre le moteur et le trou d'économiseur, et conduirait à alimenter le trou d'économiseur avec du gaz dont la pression serait réduite par le moyen de fermeture.When the compressor is operating at partial speed, the pressure at the economizer hole drops to, or near, the intake pressure. In this case, the closure means reduces the flow rate, and this establishes, upstream of the closure means, a pressure which preferably is determined by the action of a spring on the closure means. It is thus possible to maintain in the engine a minimum pressure useful for removing from the engine the liquid separated from the gas. But when the compressor operates at full speed, this throttling of the flow would adversely affect the efficiency since it would create a pressure drop between the engine and the economiser hole, and would lead to supplying the economiser hole with gas whose pressure would be reduced by the closing means.

Cet inconvénient est évité car l'écoulement n'est étranglé que lorsque la différence de pression entre le trou d'économiseur et l'admission du compresseur est inférieure à un seuil prédéterminé. Au-dessus de ce seuil, le moyen de fermeture permet une communication sensiblement libre entre l'intérieur du moteur et le trou d'économiseur.This drawback is avoided because the flow is only throttled when the pressure difference between the economizer hole and the compressor intake is less than a predetermined threshold. Above this threshold, the closure means allows substantially free communication between the interior of the engine and the economizer hole.

Pour minimiser les volumes occupés par la conduite, le piston peut être monté dans un prolongement de la conduite entre l'espace intérieur du moteur et le trou d'économiseur, et lorsque ladite différence - ou pression différentielle - dépasse le seuil, le piston se rétracte au-delà du trou d'économiseur de sorte que la conduite entre le trou d'économiseur et l'intérieur du moteur est tout-à-fait dégagée de tout piston lorsque le compresseur est à plein régime. Ce résultat est obtenu en tarant le ressort de façon que sa force soit sensiblement inférieure à la force créée sur le piston par la pression différentielle lorsqu'elle est égale au seuil.To minimize the volumes occupied by the pipe, the piston can be mounted in an extension of the pipe between the interior space of the engine and the economiser hole, and when said difference - or differential pressure - exceeds the threshold, the piston retracts beyond the economizer hole so that the line between the economizer hole and the inside of the engine is completely clear of any piston when the compressor is at full speed. This is achieved by taring the spring so that its force is significantly less than the force created on the piston by the differential pressure when it is equal to the threshold.

La présente invention sera mieux comprise à la lecture de la description qui va suivre, concernant des exemples non limitatifs, en référence aux dessins annexés, dans lesquels :

  • - la figure 1 montre partiellement en coupe un moto-compresseur selon l'invention, et schématiquement le circuit frigorifique associé ; et
  • - les figures 2 et 3 sont des vues partielles en coupe d'un second et d'un troisième mode de réalisation du compresseur.
The present invention will be better understood on reading the description which follows, relating to nonlimiting examples, with reference to the appended drawings, in which:
  • - Figure 1 shows partially in section a motor-compressor according to the invention, and schematically the associated refrigeration circuit; and
  • - Figures 2 and 3 are partial sectional views of a second and a third embodiment of the compressor.

Un arbre 1 (figure 1) porte une vis 2 coopérant avec des pignons (non représentés) comme cela est bien connu par exemple d'après le US-A- 3 180 565. Cet arbre est supporté par des paliers 3 et 4 et entraîné en rotation par un moteur électrique constitué d'un rotor 5 attaché à l'arbre 1 au-delà du palier 4 et tournant à l'intérieur d'un stator 6 qui est fixe dans une enveloppe 7 solidaire du carter 8 du compresseur.A shaft 1 (Figure 1) carries a cooperating screw 2 with pinions (not shown) as is well known for example from US-A-3 180 565. This shaft is supported by bearings 3 and 4 and rotated by an electric motor consisting of a rotor 5 attached to the shaft 1 beyond the bearing 4 and rotating inside a stator 6 which is fixed in an envelope 7 secured to the casing 8 of the compressor.

A l'exception de raccordements à des conduites pour fluides qui seront décrites plus loin, l'enveloppe 7 est étanche et l'espace intérieur de l'enveloppe 7 est séparé de manière étanche de l'admission 20 du compresseur au moyen d'un flasque porte-palier 4a, portant un palier 4. Le flasque porte-palier 4a est muni d'un dispositif d'étanchéïté 22 coopérant avec l'arbre 1.With the exception of connections to pipes for fluids which will be described later, the casing 7 is sealed and the interior space of the casing 7 is sealed from the inlet 20 of the compressor by means of a bearing support flange 4a, carrying a bearing 4. The bearing support flange 4a is provided with a sealing device 22 cooperating with the shaft 1.

L'orifice de refoulement 31 du compresseur est relié à un orifice d'admission 32 du compresseur à travers un circuit frigorifique comprenant en série dans l'ordre suivant : un condenseur 33, un réservoir 34, une valve d'expansion 36 et un évaporateur 37.The discharge port 31 of the compressor is connected to an intake port 32 of the compressor through a refrigeration circuit comprising in series in the following order: a condenser 33, a tank 34, an expansion valve 36 and an evaporator 37.

Le carter 8 est muni d'un trou d'économiseur 9 tel que décrit dans de nombreux brevets, par exemple US-A-­4 261 691, ce trou étant relié à l'intérieur de l'enveloppe 7 du moteur par une conduite 10.The casing 8 is provided with an economizer hole 9 as described in numerous patents, for example US-A-4,261,691, this hole being connected to the inside of the casing 7 of the engine by a pipe 10 .

Le moteur est refroidi par du liquide et/ou du gaz atteignant l'intérieur de l'enveloppe 7 du moteur par une conduite 11 qui est représentée dans l'axe du moteur mais qui pourrait se trouver ailleurs, par exemple au sommet du moteur.The engine is cooled by liquid and / or gas reaching the interior of the casing 7 of the engine by a pipe 11 which is shown in the axis of the engine but which could be located elsewhere, for example at the top of the engine.

Ce liquide et/ou gaz passe à travers le moteur en le refroidissant. Le gaz ayant refroidi le moteur est aspiré par le compresseur à travers le trou d'économiseur 9. Le liquide et/ou gaz arrivant dans l'enveloppe 7 par la conduite 11 peut être, comme représenté, du liquide arrivant directement du condenseur 33 à travers un conduit et se vaporisant partiellement dans le moteur comme décrit dans le US-A- 4 573 324. Ce peut-être aussi du liquide avec ou sans gaz provenant d'un économiseur centrifuge qui serait monté à l'extrémité de l'arbre 1 au-delà du rotor 5. Un tel économiseur centrifuge est décrit dans le US - A - 4 509 341. Ce pourrait être aussi, tout simplement, du gaz provenant d'un économiseur classique.This liquid and / or gas passes through the engine cooling it. The gas having cooled the engine is sucked by the compressor through the economizer hole 9. The liquid and / or gas arriving in the casing 7 through the pipe 11 may be, as shown, liquid arriving directly from the condenser 33 to through a conduit and partially vaporizing in the engine as described in US-A-4,573,324. This may also be liquid with or without gas coming from a centrifugal economizer which would be mounted at the end of the shaft 1 beyond the rotor 5. Such a centrifugal economizer is described in US - A - 4,509,341. It could also be, quite simply, gas from a conventional economizer.

Quel que soit le cas, l'enveloppe du moteur est généralement utilisée pour séparer le liquide destiné à être évacué vers un autre point. Par exemple, comme cela est représenté, et comme le décrit le US-A- 4 573 324, le liquide est collecté dans le fond de l'enveloppe 7 et envoyé à l'évaporateur 37 par un conduit 38, en exploitant la pression régnant dans l'enveloppe 7, pression qui est plus élevée qu'en aval de la valve 36.Whatever the case, the motor casing is generally used to separate the liquid intended to be discharged to another point. For example, as shown, and as described in US-A-4,573,324, the liquid is collected in the bottom of the casing 7 and sent to the evaporator 37 by a conduit 38, by exploiting the prevailing pressure in the casing 7, pressure which is higher than downstream of the valve 36.

Lorsqu'on utilise des compresseurs sans injection d'huile, comme enseigné dans le US-A- 4 553 399, il est intéressant d'utiliser l'enveloppe moteur pour collecter l'huile séparée du liquide vaporisé et par la chaleur du moteur et de l'envoyer aux paliers.When using compressors without oil injection, as taught in US-A-4,553,399, it is advantageous to use the engine casing to collect the oil separated from the vaporized liquid and by the heat of the engine and send it to the landings.

Dans tous les cas, lorsque le compresseur fonctionne à plein régime, la pression dans le moteur est significativement supérieure à la pression d'admission du compresseur. Lorsqu'on opère avec du réfrigérant type "R22", la pression différentielle dans un système classique de conditionnement d'air peut s'échelonner entre 200 à 300 et 800 à 900 kPa.In all cases, when the compressor is operating at full speed, the pressure in the engine is significantly higher than the intake pressure of the compressor. When operating with "R22" type refrigerant, the differential pressure in a conventional air conditioning system can range between 200 to 300 and 800 to 900 kPa.

Cette pression différentielle est utile pour déplacer le réfrigérant liquide vers l'évaporateur, particulièrement lorsque l'évaporateur est installé à un niveau spuérieur à celui du compresseur, ou bien pour déplacer l'huile.This differential pressure is useful for moving the liquid refrigerant towards the evaporator, particularly when the evaporator is installed at a level higher than that of the compressor, or to move the oil.

Cependant, lorsque le compresseur fonctionne à régime partiel et que la pression au trou d'économiseur 9 se rapproche de la pression d'admission ou la rejoint, la pression différentielle précitée tend à disparaître et, sans l'invention, il deviendrait difficile ou impossible de refouler le liquide vers l'évaporateur ou respectivement l'huile vers les paliers.However, when the compressor operates at partial speed and the pressure at the economizer hole 9 approaches or reaches the intake pressure, the aforementioned differential pressure tends to disappear and, without the invention, it would become difficult or impossible to discharge the liquid to the evaporator or respectively the oil to the bearings.

Selon l'invention, un piston 12 est monté de manière coulissante et étanche dans un prolongement 13 de la conduite 10. Ce prolongement s'étend entre le trou d'économiseur et un espace 19 soumis à la pression d'admission, prévu au-delà du palier 3 éloigné du moteur. L'espace 19 est relié à la région d'admission 20 à travers la palier 3 et à travers un passage 21 traversant la vis 2. Le piston 12 a ainsi une face frontale 12a soumise à la pression d'économiseur et une face arrière 12b, de même aire, soumise à la pression d'admission. Le piston 12 est sollicité par un ressort 14 de sorte que, en l'absence de pression différentielle, le piston 12 se déplace vers sa position 15 représentée en pointillé, voisine d'un épaulement 16 de la conduite 10, et forme avec celle-ci un étranglement 17.According to the invention, a piston 12 is mounted in a sliding and sealed manner in an extension 13 of the pipe 10. This extension extends between the economizer hole and a space 19 subjected to the intake pressure, provided at- beyond bearing 3 away from the engine. The space 19 is connected to the intake region 20 through the bearing 3 and through a passage 21 passing through the screw 2. The piston 12 thus has a front face 12a subjected to the economizer pressure and a rear face 12b , of the same area, subject to inlet pressure. The piston 12 is biased by a spring 14 so that, in the absence of differential pressure, the piston 12 moves to its position 15 shown in dotted lines, close to a shoulder 16 of the pipe 10, and forms therewith. ci a choke 17.

Ainsi, lorsque la pression au trou d'économiseur 9 tombe à la pression d'admission, le piston se déplace et il se crée une perte de charge à travers l'étranglement 17 de manière à maintenir dans l'enveloppe 7 du moteur, une pression excédant suffisamment la pression d'admission pour refouler le réfrigérant liquide vers l'évaporateur 37 ou l'huile vers les paliers 3 et 4.Thus, when the pressure at the economizer hole 9 falls to the intake pressure, the piston moves and a pressure drop is created through the throttle 17 so as to maintain in the casing 7 of the engine, a pressure exceeding the intake pressure enough to discharge the liquid refrigerant to the evaporator 37 or the oil to the bearings 3 and 4.

Cependant, lorsque le compresseur fonctionne à plein régime, la face frontale 12a du piston 12 est à la pression d'économiseur tandis que la face arrière 12b est soumise à la pression d'admission.However, when the compressor is operating at full speed, the front face 12a of the piston 12 is at economiser pressure while the rear face 12b is subjected to the intake pressure.

Le ressort 14 est conçu de sorte que dans la position représentée en trait plein, dans laquelle le trou d'économiseur 9 est complètement dégagé par le piston 12, la force élastique soit équilibrée par une pression différentielle égale à une valeur de seuil d'environ 25 kPa, c'est-à-dire correspondant à une pression au trou d'économiseur excédant de 25 kPa la pression d'admission.The spring 14 is designed so that in the position shown in solid lines, in which the economizer hole 9 is completely released by the piston 12, the elastic force is balanced by a differential pressure equal to a threshold value of approximately 25 kPa, i.e. corresponding to a pressure at the economiser hole exceeding 25 kPa the intake pressure.

Dans cette position, le piston 12 ne fait apparaître aucune perte de charge entre le moteur et le trou d'économiseur 9. Comme cela est évident et bien connu, une telle perte de charge serait très nuisible au rendement du compresseur.In this position, the piston 12 does not show any pressure drop between the engine and the economizer hole 9. As is obvious and well known, such a pressure drop would be very detrimental to the efficiency of the compressor.

Dans le mode de réalisation représenté à la figure 2, qui ne sera décrit qu'en ce qui concerne ses différences avec celui de la figure 1, le prolongement 13 n'est plus prévu, et le piston 12 est logé dans un alésage 39 qui est aménagé dans le carter 8 transversalement à l'axe du moto-compresseur, de manière à relier la conduite 10 et la région d'admission 20. L'alésage 39 comporte un épaulement 16 conçu pour coopérer avec la face 12a du piston 12.In the embodiment shown in Figure 2, which will only be described with regard to its differences from that of Figure 1, the extension 13 is no longer provided, and the piston 12 is housed in a bore 39 which is arranged in the casing 8 transversely to the axis of the motor-compressor, so as to connect the pipe 10 and the intake region 20. The bore 39 has a shoulder 16 designed to cooperate with the face 12a of the piston 12.

Une partie amont 10a de la conduite 10, s'étendant entre l'enveloppe moteur 7 et l'alésage 39, rencontre l'alésage 39 au-delà de l'épaulement 16, tandis qu'une partie aval 10b de la conduite 10, s'étendant entre l'alésage 39 et le trou d'économiseur 9, est reliée à l'alésage 39 de façon à communiquer avec la partie 10a à travers l'épaulement 16 à condition que le piston 12 ne repose pas contre l'épaulement 16. Le ressort 14 est un ressort de traction d'étendant à travers l'épaulement 16.An upstream part 10a of the pipe 10, extending between the motor housing 7 and the bore 39, meets the bore 39 beyond the shoulder 16, while a downstream part 10b of the pipe 10, extending between the bore 39 and the economizer hole 9, is connected to the bore 39 so as to communicate with the part 10a through the shoulder 16 provided that the piston 12 does not rest against the shoulder 16. The spring 14 is a tension spring extending through the shoulder 16.

Lorsque la pression au trou d'économiseur 9 excède d'au moins 25 kPa la pression d'admission, le piston 12 est repoussé à l'encontre de l'action du ressort 14, et il y a libre communication entre les parties 10a et 10b de la conduite 10.When the pressure at the economizer hole 9 exceeds the inlet pressure by at least 25 kPa, the piston 12 is pushed back against the action of the spring 14, and there is free communication between the parts 10a and 10b of the pipe 10.

Dans le cas contraire, le ressort 14 ramène le piston 12 vers l'épaulement 16 et le piston 12 forme avec celui-ci un étranglement régulateur de pression, maintenant dans la partie 10a, et par conséquent dans l'enveloppe moteur 7, une pression excédant de sensiblement 25 kPa la pression d'admission.Otherwise, the spring 14 brings the piston 12 back towards the shoulder 16 and the piston 12 forms therewith a pressure regulating throttle, maintaining in the part 10a, and consequently in the motor casing 7, a pressure significantly exceeding 25 kPa the intake pressure.

Dans le mode de réalisation de la figure 3, le moyen de fermeture est un papillon 112 qui est monté de manière pivotante dans la conduite 10 entre les portions 10a et 10b de celle-ci, autour d'un axe de pivotement 41 qui est décalé latéralement par rapport à l'axe 42 de la conduite 10. Ainsi, si la pression en amont du papillon 112 (partie 10a de la conduite) dépasse la pression en aval du papillon 112 (10b de la conduite), le papillon 112 est sollicité à l'ouverture.In the embodiment of Figure 3, the closure means is a butterfly 112 which is pivotally mounted in the pipe 10 between the portions 10a and 10b thereof, about a pivot axis 41 which is offset laterally with respect to the axis 42 of the pipe 10. Thus, if the pressure upstream of the butterfly 112 (part 10a of the pipe) exceeds the pressure downstream of the butterfly 112 (10b of the pipe), the butterfly 112 is requested upon opening.

Un levier 43 relié rigidement à la face aval du papillon 112 est relié de manière pivotante et coulissante à une tige 44 d'un piston 46 monté de manière coulissante et étanche dans un alésage 47 s'étendant entre la partie 10b de la conduite 10 et la région d'admission 20.A lever 43 rigidly connected to the downstream face of the butterfly 112 is pivotally and slidingly connected to a rod 44 of a piston 46 mounted in a sliding and sealed manner in a bore 47 extending between the part 10b of the pipe 10 and the admission region 20.

Le piston 46 a ainsi une face frontale 46a soumise à la pression au trou d'économiseur, et une face arrière 46b soumise à la pression d'admission. La pression au trou d'économiseur agit sur le piston 46 pour ouvrir le papillon 112. La pression d'admission et le ressort de rappel 14 agissent ensemble sur le piston 46 dans le sens de la fermeture du papillon 112.The piston 46 thus has a front face 46a subjected to the pressure at the economizer hole, and a rear face 46b subjected to the intake pressure. The pressure at the economizer hole acts on the piston 46 to open the butterfly 112. The intake pressure and the return spring 14 act together on the piston 46 in the direction of closing the butterfly 112.

Si la pression au trou d'économiseur excède d'au moins 25 kPa la pression d'admission, le piston 46 ouvre le papillon 112.If the pressure at the economiser hole exceeds at least 25 kPa the intake pressure, the piston 46 opens the butterfly 112.

Dans le cas contraire, la combinaison piston 46 - ressort 14 tend à fermer le papillon 112. Cependant, ceci crée dans la partie 10a de la conduite une surpression qui agit sur le papillon 112 pour ouvrir légèrement celui-ci. Ceci régule la surpression dans la partie 10a de la conduite reliée à l'enveloppe moteur 7 (non représentée à cette figure).Otherwise, the piston 46 - spring 14 combination tends to close the butterfly 112. However, this creates in the part 10a of the pipe an overpressure which acts on the butterfly 112 to slightly open it. This regulates the overpressure in part 10a of the pipe connected to the motor housing 7 (not shown in this figure).

La présente invention a été décrite dans le cas d'un compresseur à vis unique mais pourrait, sans changement, s'appliquer à tout type de compresseur qui peut être équipé d'un trou d'économiseur, en particulier d'un trou d'économiseur fixe, par exemple les compresseurs à deux vis, les compresseurs à palettes mobiles, les compresseurs à palettes fixes.The present invention has been described in the case of a single screw compressor but could, without change, apply to any type of compressor which can be equipped with an economizer hole, in particular a stationary economizer, for example twin screw compressors, mobile vane compressors, fixed vane compressors.

Dans une mode de réalisation moins performant de l'invention, l'organe de fermeture, au lieu de réguler la pression dans l'enveloppe moteur lorsque la pression différentielle au trou d'économiseur est basse, pourrait simplement créer un passage calibré fixe pour le gaz venant de l'enveloppe moteur.In a less efficient embodiment of the invention, the closure member, instead of regulating the pressure in the engine casing when the differential pressure at the economiser hole is low, could simply create a fixed calibrated passage for the gas coming from the engine casing.

L'obturateur pourrait être de types différents des exemples qui ont été décrits.The shutter could be of different types from the examples which have been described.

Claims (8)

1. Moto-compresseur frigorifique comprenant un compresseur rotatif volumétrique (2, 8) entraîné par un moteur (5, 6), des moyens (11) pour introduire du fluide frigorifique à l'intérieur du moteur pour refroidir le moteur, ledit intérieur étant relié par une conduite (10) à un trou d'économiseur (9) du compresseur, caractérisé par des moyens de fermeture (12, 112) disposés dans ladite conduite (10) pour obturer au moins partiellement celle-ci, ces moyens de fermeture étant reliés à une pression d'admission du compresseur et étant conçus pour dégager ladite conduite (10) lorsque la pression au trou d'économiseur (9) excède d'une pression différentielle prédéterminée la pression d'admission.1. Refrigeration motor compressor comprising a rotary positive displacement compressor (2, 8) driven by a motor (5, 6), means (11) for introducing refrigerant fluid inside the engine to cool the engine, said interior being connected by a pipe (10) to an economiser hole (9) of the compressor, characterized by closing means (12, 112) arranged in said pipe (10) for at least partially closing the latter, these closing means being connected to an inlet pressure of the compressor and being adapted to disengage said line (10) when the pressure at the economiser hole (9) exceeds the inlet pressure by a predetermined differential pressure. 2. Moto-compresseur frigorifique selon la revendication 1, caractérisé en ce que le moyen de fermeture est un piston coulissant (12) ayant une première face (12b) soumise à la pression d'admission du compresseur, et une second face (12a) soumise à la pression régnant à l'intérieur du moteur, des moyens (14) sollicitant le piston vers une position dans laquelle le piston forme un étranglement pour l'écoulement provenant de l'intérieur du moteur et allant vers le trou d'économiseur (9) et accroît la pression à l'intérieur du moteur par rapport à la pression au trou d'économiseur (9), la course de ce piston (12) et la force du ressort (14) étant choisies pour que le piston établisse une communication sensiblement libre entre l'intérieur du moteur et le trou d'économiseur (9) lorsque la différence de pression entre le trou d'économiseur (9) et la pression d'admission dépasse la pression différentielle prédéterminée précitée.2. Refrigerating motor-compressor according to claim 1, characterized in that the closing means is a sliding piston (12) having a first face (12b) subjected to the inlet pressure of the compressor, and a second face (12a) subjected to the pressure prevailing inside the engine, means (14) urging the piston towards a position in which the piston forms a constriction for the flow coming from inside the engine and going towards the economizer hole ( 9) and increases the pressure inside the engine relative to the pressure at the economiser hole (9), the stroke of this piston (12) and the force of the spring (14) being chosen so that the piston establishes a substantially free communication between the interior of the engine and the economizer hole (9) when the pressure difference between the economizer hole (9) and the intake pressure exceeds the aforementioned predetermined differential pressure. 3. Moto-compresseur selon la revendication 2, caractérisé en ce qu'un trajet du fluide depuis l'intérieur du moteur vers le trou d'économiseur (9) passe à travers un épaulement (16) avec lequel le piston (12) coopère pour former ledit également.3. Moto-compressor according to claim 2, characterized in that a fluid path from the interior of the engine to the economizer hole (9) passes through a shoulder (16) with which the piston (12) cooperates to form said also. 4. Moto-compresseur frigorifique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que, lorsque la pression au trou d'économiseur (9) est inférieure à ladite pression différentielle par rapport à la pression d'admission, l'obturateur (12, 112) du moyen de fermeture est positionné par l'équilibre des forces créées par la pression d'admission, la pression à l'intérieur du moteur, et les moyens de rappel (14) de façon à réguler la pression à l'intérieur du moteur en étranglant de manière variable l'écoulement allant de l'intérieur du moteur vers le trou d'économiseur.4. Refrigerating motor-compressor according to any one of claims 1 to 3, characterized in that, when the pressure at the economizer hole (9) is less than said differential pressure with respect to the intake pressure, the shutter (12, 112) of the closure means is positioned by the balance of forces created by the intake pressure, the pressure inside the engine, and the return means (14) so as to regulate the pressure at inside the engine by variably throttling the flow from the inside of the engine to the economizer hole. 5. Moto-compresseur frigorifique selon la revendication 2, caractérisé en ce que le piston (12) est monté dans un prolongement (13) de ladite conduite (10) reliant l'intérieur du moteur au trou d'économiseur (9) ce prolongement (13) s'étendant entre le trou d'économiseur (9) et un espace basse pression (19) aménagé à l'extrémité du compresseur éloignée du moteur.5. Refrigerating motor-compressor according to claim 2, characterized in that the piston (12) is mounted in an extension (13) of said line (10) connecting the interior of the engine to the economizer hole (9) this extension (13) extending between the economizer hole (9) and a low pressure space (19) provided at the end of the compressor remote from the engine. 6. Moto-compresseur selon la revendication 5, caractérisé en ce que le compresseur est un compresseur à vis ayant une région d'admission (20) adjacente au moteur, et en ce que ladite région basse pression (19) est reliée à la région d'admission (20) à travers un palier (3) du compresseur et à travers un passage longitudinal (21) traversant un rotor à vis du compresseur à vis.6. A motor compressor according to claim 5, characterized in that the compressor is a screw compressor having an intake region (20) adjacent to the engine, and in that said low pressure region (19) is connected to the region intake (20) through a bearing (3) of the compressor and through a longitudinal passage (21) passing through a screw rotor of the screw compressor. 7. Moto-compresseur frigorifique selon la revendication 2, caractérisé en ce que le piston (12) est monté dans un alésage (39) pratiqué transversalement à ladite conduite (10) reliant l'intérieur du moteur au trou d'économiseur (9), cet alésage (39) s'étendant entre ladite conduite (10) et une région d'admission (20) du compresseur.7. Refrigerating motor-compressor according to claim 2, characterized in that the piston (12) is mounted in a bore (39) formed transversely to said pipe (10) connecting the interior of the engine to the economizer hole (9) , this bore (39) extending between said pipe (10) and an inlet region (20) of the compressor. 8. Moto-compresseur frigorifique selon la revendication 7, caractérisé en ce que ladite conduite (10) comprend deux parties (10a, 10b) de la conduite, communiquant entre elles à travers un épaulement (16) de l'alésage (39), cet épaulement (16) étant conçu pour coopérer avec le piston (12) pour créer ledit étranglement.8. Refrigerating motor-compressor according to claim 7, characterized in that said pipe (10) comprises two parts (10a, 10b) of the pipe, communicating with each other through a shoulder (16) of the bore (39), this shoulder (16) being designed to cooperate with the piston (12) to create said constriction.
EP88401839A 1987-07-21 1988-07-15 Hermetic or semi-hermetic refrigeration motor compressor unit Expired - Lifetime EP0300884B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8710273A FR2618494A1 (en) 1987-07-21 1987-07-21 HERMETIC REFRIGERATION COMPRESSOR WITH ECONOMIZER
FR8710273 1987-07-21

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EP (1) EP0300884B1 (en)
JP (1) JP2582128B2 (en)
DE (1) DE3860134D1 (en)
ES (1) ES2015988B3 (en)
FR (1) FR2618494A1 (en)

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CN103635760A (en) * 2011-02-22 2014-03-12 惠而浦股份有限公司 Compressor cooling system using heat exchanger pre-condenser, and compressor provided with cooling system

Also Published As

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JPS6441681A (en) 1989-02-13
EP0300884B1 (en) 1990-05-09
JP2582128B2 (en) 1997-02-19
ES2015988B3 (en) 1990-09-16
DE3860134D1 (en) 1990-06-13
FR2618494A1 (en) 1989-01-27
US4890461A (en) 1990-01-02

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