EP0300884A1 - Hermetische oder halbhermetische Motorkühlkompressoreinheit zur Kälteerzeugung - Google Patents

Hermetische oder halbhermetische Motorkühlkompressoreinheit zur Kälteerzeugung 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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EP
European Patent Office
Prior art keywords
pressure
engine
compressor
hole
piston
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Granted
Application number
EP88401839A
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English (en)
French (fr)
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EP0300884B1 (de
Inventor
Bernard Zimmern
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Individual
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Individual
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Classifications

    • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP88401839A 1987-07-21 1988-07-15 Hermetische oder halbhermetische Motorkühlkompressoreinheit zur Kälteerzeugung Expired - Lifetime EP0300884B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8710273 1987-07-21
FR8710273A FR2618494A1 (fr) 1987-07-21 1987-07-21 Compresseur de refrigeration hermetique avec economiseur

Publications (2)

Publication Number Publication Date
EP0300884A1 true EP0300884A1 (de) 1989-01-25
EP0300884B1 EP0300884B1 (de) 1990-05-09

Family

ID=9353351

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88401839A Expired - Lifetime EP0300884B1 (de) 1987-07-21 1988-07-15 Hermetische oder halbhermetische Motorkühlkompressoreinheit zur Kälteerzeugung

Country Status (6)

Country Link
US (1) US4890461A (de)
EP (1) EP0300884B1 (de)
JP (1) JP2582128B2 (de)
DE (1) DE3860134D1 (de)
ES (1) ES2015988B3 (de)
FR (1) FR2618494A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103635760A (zh) * 2011-02-22 2014-03-12 惠而浦股份有限公司 使用热交换器预冷凝器的压缩机冷却系统和设置有冷却系统的压缩机
EP2280172A4 (de) * 2008-05-30 2018-06-27 Mitsubishi Heavy Industries Thermal Systems, Ltd. Kühlkompressor und ventileinheit dafür

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7156624B2 (en) * 2004-12-09 2007-01-02 Carrier Corporation Compressor sound suppression

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3698839A (en) * 1970-10-14 1972-10-17 Borg Warner Pressure equalizer for unloading a compressor during start-up
US3898862A (en) * 1973-07-23 1975-08-12 Carrier Corp Economizer pressure regulating system
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
US4553399A (en) * 1983-04-14 1985-11-19 Bernard Zimmern Method of lubricating bearings of a refrigeration or the like compressor
US4573324A (en) * 1985-03-04 1986-03-04 American Standard Inc. Compressor motor housing as an economizer and motor cooler in a refrigeration system

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3192735A (en) * 1961-09-12 1965-07-06 American Radiator & Standard Cooling coil for hermetic motor using system refrigerant
FR1331998A (fr) * 1962-05-08 1963-07-12 Perfectionnements aux compresseurs rotatifs à vis globique et à joints liquides
US3232074A (en) * 1963-11-04 1966-02-01 American Radiator & Standard Cooling means for dynamoelectric machines
US3379033A (en) * 1966-08-10 1968-04-23 Vilter Manufacturing Corp Refrigeration system and apparatus
US3618337A (en) * 1970-06-22 1971-11-09 Carrier Corp Hermetic refrigeration compressor
US3805547A (en) * 1972-11-21 1974-04-23 Trane Co Refrigeration machine with liquid refrigerant cooled motor
US3866438A (en) * 1973-10-29 1975-02-18 Carrier Corp Motor cooling apparatus utilizing a refrigerant flow circuit
US3838581A (en) * 1973-10-29 1974-10-01 Carrier Corp Refrigerator apparatus including motor cooling means
US3885402A (en) * 1974-01-14 1975-05-27 Dunham Bush Inc Optimized point of injection of liquid refrigerant in a helical screw rotary compressor for refrigeration use
US3913346A (en) * 1974-05-30 1975-10-21 Dunham Bush Inc Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor
GB1555330A (en) * 1978-03-21 1979-11-07 Hall Thermotank Prod Ltd Rotary fluid machines
FR2541437B1 (fr) * 1982-05-13 1985-08-23 Zimmern Bernard Economiseur centrifuge pour refrigeration

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
US3698839A (en) * 1970-10-14 1972-10-17 Borg Warner Pressure equalizer for unloading a compressor during start-up
US3898862A (en) * 1973-07-23 1975-08-12 Carrier Corp Economizer pressure regulating system
US4553399A (en) * 1983-04-14 1985-11-19 Bernard Zimmern Method of lubricating bearings of a refrigeration or the like compressor
US4573324A (en) * 1985-03-04 1986-03-04 American Standard Inc. Compressor motor housing as an economizer and motor cooler in a refrigeration system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2280172A4 (de) * 2008-05-30 2018-06-27 Mitsubishi Heavy Industries Thermal Systems, Ltd. Kühlkompressor und ventileinheit dafür
CN103635760A (zh) * 2011-02-22 2014-03-12 惠而浦股份有限公司 使用热交换器预冷凝器的压缩机冷却系统和设置有冷却系统的压缩机

Also Published As

Publication number Publication date
DE3860134D1 (de) 1990-06-13
FR2618494A1 (fr) 1989-01-27
EP0300884B1 (de) 1990-05-09
US4890461A (en) 1990-01-02
ES2015988B3 (es) 1990-09-16
JP2582128B2 (ja) 1997-02-19
JPS6441681A (en) 1989-02-13

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