EP0205670A1 - Kälte- oder Wärmepumpensystem - Google Patents

Kälte- oder Wärmepumpensystem Download PDF

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Publication number
EP0205670A1
EP0205670A1 EP85200969A EP85200969A EP0205670A1 EP 0205670 A1 EP0205670 A1 EP 0205670A1 EP 85200969 A EP85200969 A EP 85200969A EP 85200969 A EP85200969 A EP 85200969A EP 0205670 A1 EP0205670 A1 EP 0205670A1
Authority
EP
European Patent Office
Prior art keywords
bypass
valve member
compressor
refrigerating
electromagnet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP85200969A
Other languages
English (en)
French (fr)
Other versions
EP0205670B1 (de
Inventor
Lambert Johannes Maria Kuijpers
Martinus Johannes Petrus Janssen
Johannes Adrianus De Wit
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.)
Whirlpool International BV
Original Assignee
Philips Gloeilampenfabrieken NV
Whirlpool International BV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Philips Gloeilampenfabrieken NV, Whirlpool International BV filed Critical Philips Gloeilampenfabrieken NV
Priority to DE8585200969T priority Critical patent/DE3573951D1/de
Priority to EP85200969A priority patent/EP0205670B1/de
Priority to ES1986294801U priority patent/ES294801Y/es
Priority to JP61140410A priority patent/JPS61291789A/ja
Publication of EP0205670A1 publication Critical patent/EP0205670A1/de
Application granted granted Critical
Publication of EP0205670B1 publication Critical patent/EP0205670B1/de
Expired legal-status Critical Current

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Classifications

    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator

Definitions

  • the invention relates to a refrigerating or heat-pump system comprising an evaporator, a compressor, a condensor, and a throttle means, the compressor comprising an electric motor and a reciprocating pump, which pump comprises a cylinder in which a piston is reciprocated by the electric motor to work on a compression space above the piston, which compressor has an inlet and an outlet, which are connected to the evaporator and to the condensor, respectively by means of pipes, and further comprising a suction part and a bypass by means of which the suction part can be made to commnicate with the compression space by controlling a valve member in the bypass.
  • the invention relates to a system controlled in conformity with the last-mentioned method. It is known to open or close a connection between the cylinder space and the suction part by means of a valve.
  • the invention aims at improving the efficiency of the system by means of a simple and cheap control mechanism.
  • the system is characterized in that the valve member is controlled electromagnetically and the system comprises a control mechanism which reduces the power of the electric motor in an efficient manner when the bypass is opened.
  • Suction-gas control reduces the refrigerant mass being circulated, so that the evaporator temperature increases and the condensor temperature decreases, thereby reducing the work of compression.
  • cold is produced at a higher temperature than in an on/off controlled system.
  • the mass to be circulated by the compressor is smaller, so that the torque to be delivered by the electric motor is reduced and the efficiency decreases. Therefore, in order to maintain the efficiency of the electric motor at the same level, the power is reduced in an efficient manner during said period.
  • the combined control of the system in accordance with the invention results in a net reduction in power consumption of approximately 10%.
  • An on/off controlled system is to be understood to mean as a system in which during the off-period the condensor is disconnected from the evaporator. During the off-period the connection between the condenser and the evaporator should remain open (for example if the throttle means is a capillary), the power saved is even higher than the above 10%, namely of the order of 20%.
  • a preferred embodiment is characterized in that the suction part comprises a damper, a suction duct and a suction chamber, the bypass is situated between the suction duct and the compression space, and the valve member is coupled to the core of an electromagnet, which valve member opens the connecting duct when the electromagnet is energized and closes said duct by means of a return spring when said electromagnet is not energized.
  • the return spring ensures that the valve member is set to the position in which the compressor operates at the maximum capacity, that the system reverts to normal on/off control.
  • the cylinder is formed with a bore in which the valve member is movable and which intersects said bypass duct, which valve member has a bore such that, upon energization of the electromagnet, this bore is situated in line with the bypass.
  • the bore is situated at a small distance from the cylinder wall, in such a way that in the closed situation the additional clearance volume in the compression space, i.e. the volume in the bypass between the valve member and the compression space, is minimal.
  • the bypass can be closed by changing the position of the valve member in the bore, either by sliding it in the said direction of the bore or by rotating it through 90 0 in the bore. As there is hardly any pressure differential across the valve member, the leakage path need not be exceptionally large.
  • the system efficiency is improved because the flow resistance of the throttle means is increased when the bypass is opened.
  • the system comprises an evaporator 1, a compressor 2, a condensor 3, and a throttle valve 4, which are interconnected by pipes to form a closed circuit.
  • the compressor is mounted in a hermetically sealed housing 5, which also accommodates an electric motor 6 and a reciprocating pump 7.
  • the reciprocating pump comprises a cylinder 8 in which a piston 9 is reciprocated by the electric motor, a cover 10, and a valve plate 11 arranged between the cover and the cylinder.
  • the valve plate is formed with an inlet port 12 with an inlet valve 13 and an outlet port 14 with an outlet valve 15.
  • the housing 5 of the compressor has an inlet 16 and an outlet 17 which are connected to the evaporator 1 and the condensor 3, respectively by means of pipes.
  • the suction part comprising a suction damper 18, a suction duct 19 and a suction chamber 20 the refrigerant gas is drawn into the compression space 21 after which it is compressed and forced into the compression chamber and the compression damper 23 via the outlet port 14; subsequently, the gas is fed to the condensor via the outlet 17.
  • the system is controlled by providing the compressor with a bypass duct 24 between the compression duct space 21 and the suction/19.
  • this bypass may be situated between the compression space and the suction danmper 18 or between the compression space and the suction chamber 20.
  • the cylinder housing 8 is formed with a bore 25 in which a valve member 26 is slidable. The bore 25 intersects the bypass 24.
  • the valve member 26 is integral with the movable core 27 of an electromagnet 28.
  • the core 27 is surrounded by a coil 29 which is included in an electrical control loop of the system.
  • the electromagnet is provided with a return spring 30.
  • the pin- shaped valve member 26 is formed with a bore 31 which, depending on the position of the valve member, can be positioned in line or not in line with the bypass duct 24 to open or close the bypass.
  • the electromagnet 26 is energized and the bore 31 is disposed in line with the bypass duct 24.
  • the piston has passed the opening of the bypass 24 in the cylinder wall.
  • the residual gas in the compression space 21 is then compressed to the condensor pressure.
  • the compressor then operates at a reduced capacity. This capacity depends on the level of the apening of the bypass 24 in the cylinder 8.
  • the compression pressure acts on the wall of the bore 31, so that no resultant forces act on the valve member and have to be compensated by the electromagnet.
  • the return spring 30 urges the valve member upwards, thereby closing the bypass duct.
  • the force exerted on the valve member by the compression pressure does not act in the direction of movement, i.e. not on the spring, so that no fatigue problems will occur.
  • the compressor operates at maximum capacity (Fig. 2).
  • the system in accordance with the invention also comprises a control mechanism which reduces the power of the electric motor in an efficient manner when the bypass 24 is connected.
  • Fig. 4 shows two efficiency/torque curves of the electric motor. In curve I the rotor power is higher than in curve II. During the period in which the compressor operates with a closed bypass the operating range of the electric motor is situated between points A and B of curve I. If the bypass 24 between the pipe 19 and the compression space 21 is now opened, the torque T will decrease, and hence the efficiency will decrease. The electric motor then operates for example between points C and D. The efficiency can be increased by reducing, for example, the voltage. The electric motor then operates, for example, in the range E-F of curve II, in which the efficiency is high.
  • An efficient reduction of the power for torque control is preferably effected by means of a loss-free power controller.
  • a transformer may be used in order to reduce the voltage.
  • a transformer is expensive.
  • the power controller 40 shown in Fig. 5, which is also loss-free, is cheaper.
  • the network comprising two different resistors R 1 and R 2 ( R1 R2 ), a capacitor C , a diac D, a triac T and a voltage-dependent resistor VDR controls the phase angle of the mains sinewave.
  • the setting of the switch S1 is governed by a variable thermostat 41.
  • the switch S1 At a maximum evaporator temperature (for example 3°C) the switch S1 is set to the right-hand position (full power) and at a variable minimum evaporator temperature (for example -16 to -24°C) to the left-hand position (reduced power). If the compressor operates at full power (S1 in the right-hand position) switch S2 is open and the coil 29 of the electromagnet 28 for the actuation of the valve member 26 is not energized. However, in the case of reduced conpressor power switch S2 is closed and the electromagnet is energized, so that the valve member 26 opens the bypass duct 24 between the suction duct 19 and the compression space 21.
  • Fig. 6 illustrates the thermal behaviour of the evaporator and the condenser, both for a known on/off control and for the two-position control in accordance with the invention.
  • the plotted temperatures have been measured on the refrigerant side.
  • the broken-line curves relate to the on/off control and the solid curves relate to the control in accordance with the invention.
  • the condensor temperature increases from 25°C (ambient temperature) to approximately 50°C (a1) during the on-period of the compressor, while in the same period the evaporator temperature decreases from 9°C (refrigerator temperature) to -24°C (b1).
  • the condensor temperature again decreases to approximately 25°C (a2) and the evaporator temperature rises to approximately 9°C (b2).
  • This control gives rise to a temperature fluctuation (c) of approximately 8°C in, for example, the refrigerating compartment (air) of a refrigerator.
  • the condensor temperature increases from approximately 32°C to approximately 45°C(d1) during the short period of full compressor capacity, the evaporator temperature decreasing fram -5°C to -20°C (e1) in the same period.
  • the next long period with reduced compressor capacity i.e.
  • the condenser temperature decreases to approximately 32°C (d2) and the evaporator temperature increases to approximately to -5°C (e2). Consequently, the temperature fluctuations of the evaporator and the condensor are reduced substantially if the novel control method is employed.
  • the temperature fluctuation (f) in, for example, the refrigerating compartment (air) of a refrigerator is also substantially smaller (approximately 3°C).
  • Fig. 7 shows an example of how the flow resistance can be switched to either of two valves.
  • the capillaries 4a and 4b are arranged in series, the capillary 4a being bypassed by opening the valve 42 when the compressor operates at full power.
  • the valve is closed and the two capillaries are operative.
  • the valve 42 is operated electromagnetically.
  • the location of the electromagnetic coil 33 in the circuit is indicated by a broken line.
  • the switch S3 is closed, coil 43 of the electromagnet is energized, and the valve 42 is closed.
  • Heat pumps generally employ a temperature-controlled expansion valve. Such an expansion valve is opened automatically to the correct extent in order to maintain the pressure differential.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP85200969A 1985-06-19 1985-06-19 Kälte- oder Wärmepumpensystem Expired EP0205670B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE8585200969T DE3573951D1 (en) 1985-06-19 1985-06-19 Refrigerating or heat-pump system
EP85200969A EP0205670B1 (de) 1985-06-19 1985-06-19 Kälte- oder Wärmepumpensystem
ES1986294801U ES294801Y (es) 1985-06-19 1986-06-16 Una disposicion de refrigeracion o de bomba de calor
JP61140410A JPS61291789A (ja) 1985-06-19 1986-06-18 冷却又は熱ポンプ装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP85200969A EP0205670B1 (de) 1985-06-19 1985-06-19 Kälte- oder Wärmepumpensystem

Publications (2)

Publication Number Publication Date
EP0205670A1 true EP0205670A1 (de) 1986-12-30
EP0205670B1 EP0205670B1 (de) 1989-10-25

Family

ID=8194034

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85200969A Expired EP0205670B1 (de) 1985-06-19 1985-06-19 Kälte- oder Wärmepumpensystem

Country Status (4)

Country Link
EP (1) EP0205670B1 (de)
JP (1) JPS61291789A (de)
DE (1) DE3573951D1 (de)
ES (1) ES294801Y (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0575880A1 (de) * 1992-06-22 1993-12-29 Bendix Heavy Vehicle Systems Italia S.P.A. Verdrängerverdichter, insbesondere für pneumatische Bremssysteme
EP0722667A1 (de) * 1994-12-21 1996-07-24 CARPIGIANI GROUP-ALI S.p.A. Kombinierte Maschine zur Doppeltherstellung von Brucheis oder Eiskrem

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2007388A (en) * 1931-09-15 1935-07-09 Westinghouse Electric & Mfg Co Valve construction
US2074911A (en) * 1930-05-30 1937-03-23 Gen Motors Corp Refrigerating apparatus
US2364038A (en) * 1941-12-06 1944-11-28 Touborg Jens Hermetic refrigeration compressor
GB1158371A (en) * 1966-06-28 1969-07-16 Trane Co Capacity Controlled Refrigeration System
US3942912A (en) * 1974-10-04 1976-03-09 Lennox Industries Inc. Method for controlling the operation of two-speed, refrigerant motor compressors
FR2347819A1 (fr) * 1976-04-10 1977-11-04 Bosch Siemens Hausgeraete Machine de travail a demande variable de couple moteur, notamment compresseur pour groupes frigorifiques de refrigerateurs menagers ou analogues, entrainee par un moteur asynchrone
FR2452012A1 (fr) * 1979-03-21 1980-10-17 Bosch Gmbh Robert Compresseur frigorifique
EP0087838A1 (de) * 1982-02-25 1983-09-07 Grasso's Koninklijke Machinefabrieken N.V. Mengensteuerventil für einen Kompressor
GB2121994A (en) * 1982-05-04 1984-01-04 Tokyo Shibaura Electric Co Control of air conditioning apparatus

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2074911A (en) * 1930-05-30 1937-03-23 Gen Motors Corp Refrigerating apparatus
US2007388A (en) * 1931-09-15 1935-07-09 Westinghouse Electric & Mfg Co Valve construction
US2364038A (en) * 1941-12-06 1944-11-28 Touborg Jens Hermetic refrigeration compressor
GB1158371A (en) * 1966-06-28 1969-07-16 Trane Co Capacity Controlled Refrigeration System
US3942912A (en) * 1974-10-04 1976-03-09 Lennox Industries Inc. Method for controlling the operation of two-speed, refrigerant motor compressors
FR2347819A1 (fr) * 1976-04-10 1977-11-04 Bosch Siemens Hausgeraete Machine de travail a demande variable de couple moteur, notamment compresseur pour groupes frigorifiques de refrigerateurs menagers ou analogues, entrainee par un moteur asynchrone
FR2452012A1 (fr) * 1979-03-21 1980-10-17 Bosch Gmbh Robert Compresseur frigorifique
EP0087838A1 (de) * 1982-02-25 1983-09-07 Grasso's Koninklijke Machinefabrieken N.V. Mengensteuerventil für einen Kompressor
GB2121994A (en) * 1982-05-04 1984-01-04 Tokyo Shibaura Electric Co Control of air conditioning apparatus

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENTS ABSTRACTS OF JAPAN, vol. 6, no. 263 (M-181) [1141], 22nd December 1982; & JP - A - 57 157 084 (MITSUBISHI JUKOGYO K.K.) 28-09-1982 *
PATENTS ABSTRACTS OF JAPAN, vol. 7, no. 9 (M-185) [1154], 14th January 1983; & JP - A - 57 168 077 (MITSUBISHI DENKI K.K.) 16-10-1982 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0575880A1 (de) * 1992-06-22 1993-12-29 Bendix Heavy Vehicle Systems Italia S.P.A. Verdrängerverdichter, insbesondere für pneumatische Bremssysteme
EP0722667A1 (de) * 1994-12-21 1996-07-24 CARPIGIANI GROUP-ALI S.p.A. Kombinierte Maschine zur Doppeltherstellung von Brucheis oder Eiskrem
US5653118A (en) * 1994-12-21 1997-08-05 Ali S.P.A. - Carpigiani Group Combined machine for the dual production of crushed-ice or of ice-cream

Also Published As

Publication number Publication date
EP0205670B1 (de) 1989-10-25
DE3573951D1 (en) 1989-11-30
JPS61291789A (ja) 1986-12-22
ES294801U (es) 1987-01-01
ES294801Y (es) 1987-08-16

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