EP0797000B1 - Dispositif de réduction de la charge de démarrage pour compresseur de réfrigérant - Google Patents

Dispositif de réduction de la charge de démarrage pour compresseur de réfrigérant Download PDF

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Publication number
EP0797000B1
EP0797000B1 EP97301697A EP97301697A EP0797000B1 EP 0797000 B1 EP0797000 B1 EP 0797000B1 EP 97301697 A EP97301697 A EP 97301697A EP 97301697 A EP97301697 A EP 97301697A EP 0797000 B1 EP0797000 B1 EP 0797000B1
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EP
European Patent Office
Prior art keywords
compressor
refrigerant
load reducing
starting load
evaporator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97301697A
Other languages
German (de)
English (en)
Other versions
EP0797000A1 (fr
Inventor
Masaaki c/o Sanden Corporation Fujita
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.)
Sanden Corp
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Sanden Corp
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Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP0797000A1 publication Critical patent/EP0797000A1/fr
Application granted granted Critical
Publication of EP0797000B1 publication Critical patent/EP0797000B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • 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
    • F04B49/225—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 with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/10—Inlet temperature
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle

Definitions

  • the present invention relates to an automotive air conditioning system generally, and more particularly, to a starting load reducing device for a refrigerant compressor.
  • a refrigerant circuit used in an automotive air conditioning system such as shown in Figure 1, is well known generally.
  • this refrigerant circuit includes a compressor 3, a condenser 4, receiver-dryer 5, an expansion valve 6, and an evaporator 7 connected with each other in series.
  • the compressor is started when the thermal load for the air conditioning system is large, i.e., when the refrigerant temperature at the outlet of the evaporator is high, the compressor is required to perform a compression of large amount of refrigerant immediately after the compressor is powered on.
  • the drive source for example an automotive engine
  • US Patent No. 4905477 is proposing a starting load reducing device equipped within a portion of a compressor.
  • the starting load reducing device according to that invention includes a portion in which a piston member is slid within a cylinder portion by the action of pressure in discharge chamber (high pressure)
  • the practice of the invention requires a high precision manufacturing process that must make both of tight sealing and low friction of the sliding portion compatible simultaneously.
  • a refrigerant circuit having a compressor, a condenser, an evaporator and starting load reducing means connected to each other in series, wherein:
  • Figure 1 is a general refrigerant circuit used for an automotive air conditioning system.
  • Figure 2 is a longitudinal cross sectional view of a variable displacement swash plate type compressor equipped with a starting load reducing device, according to one embodiment of the present invention.
  • Figure 3 is a magnified transversal cross sectional view of the starting load reducing device shown in Figure 2.
  • Figure 4 is a cross sectional view taken along line IV-IV' in Figure 3.
  • Figure 5 is a cross sectional view taken along line IV-IV' in Figure 3, being especially for explaining the operation of the starting load reducing device shown in Figure 2.
  • Compressor 3 includes a closed housing assembly formed by a cylindrical compressor housing 50, front end plate 60 and a rear end plate in the form of cylinder head 30. Cylinder block 70 and crank chamber 80 are located in compressor housing 50. Front end plate 60 is attached to one end surface of compressor housing 50, and cylinder head 30 is disposed on the opposite end surface of compressor housing 50 and is fixedly mounted on one end surface of cylinder block 70 through a valve plate 90. Opening is formed in the central portion of front end plate 60 to receive a drive shaft 100.
  • Drive shaft 100 is rotatably supported in front end plate 60 through bearing 110.
  • An inner end portion of drive shaft extends into central bore formed in the central portion of cylinder block 70, and is also rotatably supported therein by a bearing 120.
  • a rotor 130 disposed in the interior of crank chamber 80, is connected to drive shaft 100 to be rotatable therewith, and engages an inclined plate 140 through a hinge mechanism 150.
  • Wobble plate 160 is disposed on the opposite side surface of inclined plate 140 and bears against inclined plate through a bearing 170.
  • Hinge mechanism 150 comprises pin portion 135, formed on the inner end surface of rotor 130, and tab portion 145, having longitudinal hole 145h, formed on one end surface of inclined plate 140. The angle of inclination of inclined plate 140 with respect to drive shaft 100 can be adjusted by hinge mechanism 150.
  • a plurality of equiangularly spaced cylinder 180 are formed in cylinder block 70, and a piston 190 is reciprocatingly disposed within each cylinder 180.
  • Each piston 190 is connected to wobble plate 160 through a connecting rod 200, i.e., one end of each connecting rod 200 is connected to wobble plate 160 with a ball joint and the other end of each connecting rod is connected to one of pistons 190 with a ball joint.
  • a guide bar 210 extends within crank chamber of compressor housing 50. The lower end portion of wobble plate 160 engages guide bar 210 to enable wobble plate 160 to reciprocate along the guide bar while preventing rotational motion.
  • Pistons 190 are thus reciprocated in cylinders 180 by a drive mechanism formed of drive shaft 100, rotor 130, inclined plate 140, wobble plate 160 and connecting rods 200.
  • Drive shaft 100 and rotor 130 are rotated and inclined plate 140, wobble plate 160 and connecting rods 200 function as a coupling mechanism to convert the rotational motion of the rotor into reciprocating motion of the pistons 190.
  • Cylinder head 30 is provided with a suction chamber 30b and a discharge chamber 30c, which communicate with cylinder 180 through suction hole 90a and discharge hole 90b, respectively, formed through valve plate 90. Furthermore, on cylinder head 30, there are formed an inlet port 30a and an cutlet port (not shown in Figure 2) which place suction chamber 30b and discharge chamber 30c in fluid communication with an external refrigerant circuit respectively.
  • the capacity of the compressor is controlled by control valve 101 which regulates the pressure in the crank chamber 80.
  • Z is the inclination angle of the inclined plate 140 with respect to a plane perpendicular to the drive shaft 100.
  • the control valve 101 functions so as to increase the inclination angle Z of the inclined plate 140 with respect to a plane perpendicular to the axis of drive shaft when the thermal load of the refrigerant circuit is high, i.e., when the refrigerant temperature at the outlet of the evaporator is high, and on the contrary, to decrease the inclination angle Z when the thermal load is low, i.e., when the refrigerant temperature is low.
  • Inlet port 30a is formed within the cylinder head 30, having cylindrical vacancy 301 in its interior.
  • the central axis of the inlet port 30a is approximately parallel with the central axis of the drive shaft 100.
  • a piston 10 being capable of reciprocating motion in the axial direction.
  • Cap like member 11 is disposed in the proximity of rear portion of the inlet port 30a (right side in Figure 4).
  • the cap like member 11 has a plurality of rectangular projections 11b, and is fixedly disposed within the inlet port 30a by having the rectangular projections 11b fixed on the interior wall near rear portion of the inlet port 30a by a snap ring 14.
  • the outer diameter of the lateral wall 11a of the cap like member 11 is designed to be slightly less than the inner diameter of the piston 10, so the lateral wall lla of the cap like member 11 is accepted within the rear part of the piston 10 (right side in Figure 4). Furthermore, there are formed a plurality of holes 11c in the lateral wall lla.
  • the tension coil spring 12 is suspended between the piston 10 and the cap like member 11 so that an attracting force Fs is always exerting on both.
  • the transformation temperature Tc of the shape memory alloy used for the tension coil spring 12 is selected from between 10 Centi degrees Celsius to 30 Centi degrees Celsius, where 30 Centi degrees Celsius is representative temperature of refrigerant passing through the inlet port 30a corresponding to rest condition of the compressor, and 10 Centi degrees Celsius is the representative temperature corresponding to normal running condition of compressor.
  • the tension coil spring 12 is made of shape memory alloy, the spring constant varies rather drastically upon its transformation temperature Tc.
  • the spring constant is large, and on the contrary, when the refrigerant temperature is less than the transformation temperature Tc the spring constant is small.
  • the shape memory alloy-made tension coil spring 12 changes its elastic property sharply upon the transformation temperature Tc, that is, changes from a elastically stiff spring to a elastically soft spring.
  • the starting load reducing device 1 is composed of inlet port 30a, piston 10, cap like member 11, and tension coil spring 12.
  • a semi-completed assembly can be made from piston 10, cap like member 11, and tension coil spring 12.
  • the operation of the starting load reducing device 1 thus composed is explained as follows.
  • the thermal load of the air conditioning system is large, that is, when the refrigerant temperature at the outlet of evaporator is high, then the refrigerant temperature in the inlet port 30a is higher than the transformation temperature Tc.
  • the spring constant k of the tension coil spring is large, and also the attracting force Fs is large.
  • the piston 10 is pulled to right direction in the figure, so that the right side end surface of the piston 10 is impinging upon the rectangular projections 11b.
  • the piston 10 is maintained at the position shown in Figure 5 by a force Fd which occurs due to the dynamic pressure of refrigerant flow from the outlet of the evaporator into the suction chamber 30b.
  • Fd the force which occurs due to the dynamic pressure of refrigerant flow from the outlet of the evaporator into the suction chamber 30b.
  • the compressor 3 is started by a control mechanism of the automotive air conditioning system when the thermal load of the air conditioning system is small, i.e., when the refrigerant temperature at the outlet of the evaporator is low, the pressure difference (Pe-Ps) between the outlet of the evaporator and the suction chamber 30b does not grow to a large value.
  • the pressure difference (Pe-Ps) between the outlet of the evaporator and the suction chamber 30b does not grow to a large value.
  • the refrigerant temperature in the suction port 30a is lower than the transformation temperature Tc, the spring constant k is small. Therefore the tension coil spring 12 is in a state in which the attracting force Fs is small before the compressor is started up.
  • the piston 10 moves leftward with ease, and the surface contact between the outer surface of the lateral wall 11a of the cap like member 11 and inner surface of the piston 10 is removed as shown in Figure 5.
  • the suction chamber 30b of the compressor 3 can communicate with the outlet of the evaporator, and the refrigerant can flow from the outlet of the evaporator into the suction chamber 30b.
  • the function of restricting the amount of refrigerant sucked into the cylinder 180 does not operate immediately after the compressor 3 is started in this case. But in this circumstance, even though the function of restricting the amount of refrigerant sucked into the cylinder 180 does not operate, there is no problem because the thermal load for the air conditioning system is small.
  • the starting load reducing device of the present invention when the compressor is started under high thermal load condition for the air conditioning system, the starting load reducing device acts so as to throttle the amount of refrigerant which is compressed immediately after the compressor is started.
  • the starting load reducing device acts so as to throttle the amount of refrigerant which is compressed immediately after the compressor is started.
  • large amount of energy is not consumed in the starting operation of the compressor, so that the phenomenon that the rotational frequency of the drive shaft of the engine falls down immediately after the starting of the compressor(what is called a torque shock), can be eliminated.
  • a torque shock an uncomfortable drive feeling which will be given to the car driver otherwise is also eliminated.
  • the device attains the above purpose by controlling the communication between the outlet of the evaporator and the suction chamber which are both low pressure, it does not require a high precision manufacturing process that must make both of low friction and tight sealing of the sliding portion of communication control mechanism compatible simultaneously.
  • the starting load reducing device of the present invention it is possible to assemble a semi-completed product composed of piston 10, cap like member 11, and tension coil spring 12 in a production line other than the main production line for the compressor 3, so that a freedom of production control increases.
  • the suction port 30a formed within the cylinder head 30 is used as a casing for the starting load reducing device 1, the casing may be provided separately and disposed anywhere between the outlet of the evaporator and the suction chamber 30b of the compressor 3.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (6)

  1. Circuit de réfrigérant comportant un compresseur (3), un condenseur (4), un évaporateur (7) et un dispositif de réduction de la charge de démarrage (1) connectés les uns aux autres en série, dans lequel :
    le dispositif de réduction de la charge de démarrage est disposé entre une sortie de l'évaporateur et une chambre d'aspiration (30b) du compresseur pour servir à commander la communication entre les deux en réponse à la température du gaz réfrigérant arrivant de l'évaporateur,
    caractérisé en ce que
    le dispositif de réduction de la charge de démarrage fonctionne pour limiter la communication en réponse à une température de réfrigérant élevée correspondant à l'état de repos du compresseur (3), et fonctionne pour permettre une communication complète en réponse à une basse température du réfrigérant correspondant à l'état de fonctionnement normal du compresseur.
  2. Circuit de réfrigérant selon la revendication 1,
    dans lequel
    le dispositif de réduction de la charge de démarrage (1) comprend un mécanisme d'étranglement à piston cylindrique comprenant un piston cylindrique (10) pouvant glisser dans la direction de l'écoulement du réfrigérant, un élément en forme de capuchon (11) percé de trous auxiliaires et recevant le piston, et un ressort hélicoïdal (12) tirant le piston et l'élément en forme de capuchon l'un vers l'autre.
  3. Circuit de réfrigérant selon la revendication 1 ou la revendication 2,
    dans lequel
    le ressort hélicoïdal (12) du dispositif de réduction de la charge de démarrage (1) est réalisé dans un alliage à mémoire de forme dont la température de transformation se situe entre la température du réfrigérant correspondant à un état de fonctionnement stable du compresseur (3), et la température du réfrigérant correspondant à l'état de repos du compresseur.
  4. Circuit de réfrigérant selon la revendication 1, 2 ou 3,
    dans lequel
    le dispositif de réduction de la charge de démarrage (1) est logé dans le port d'entrée du compresseur.
  5. Circuit de réfrigérant selon la revendication 1, 2 ou 3,
    dans lequel
    le dispositif de réduction de la charge de démarrage (1) est logé dans le port de sortie de l'évaporateur (7).
  6. Circuit de réfrigérant selon la revendication 1, 2 ou 3,
    dans lequel
    le dispositif de réduction de la charge de démarrage (1) est logé dans un boítier séparé qui est disposé entre la sortie de l'évaporateur (7) et le port d'entrée du compresseur (3).
EP97301697A 1996-03-21 1997-03-13 Dispositif de réduction de la charge de démarrage pour compresseur de réfrigérant Expired - Lifetime EP0797000B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP8064448A JPH09256958A (ja) 1996-03-21 1996-03-21 圧縮機の起動負荷低減装置
JP64448/96 1996-03-21
JP6444896 1996-03-21

Publications (2)

Publication Number Publication Date
EP0797000A1 EP0797000A1 (fr) 1997-09-24
EP0797000B1 true EP0797000B1 (fr) 2001-05-30

Family

ID=13258555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97301697A Expired - Lifetime EP0797000B1 (fr) 1996-03-21 1997-03-13 Dispositif de réduction de la charge de démarrage pour compresseur de réfrigérant

Country Status (3)

Country Link
EP (1) EP0797000B1 (fr)
JP (1) JPH09256958A (fr)
DE (1) DE69704977T2 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000145629A (ja) * 1998-11-11 2000-05-26 Tgk Co Ltd 容量可変圧縮機
JP3933369B2 (ja) * 2000-04-04 2007-06-20 サンデン株式会社 ピストン式可変容量圧縮機
WO2004061306A1 (fr) * 2002-12-27 2004-07-22 Zexel Valeo Climate Control Corporation Compresseur a cylindree variable de type a plateau oscillant concu pour un cycle de refrigeration supercritique
JP4924464B2 (ja) 2008-02-05 2012-04-25 株式会社豊田自動織機 斜板式圧縮機
FR2938050B1 (fr) * 2008-11-06 2013-01-18 Valeo Systemes Thermiques Branche Thermique Habitacle Boucle de climatisation comprenant une vanne en entree du compresseur
DK2823239T3 (da) 2012-03-09 2021-03-01 Carrier Corp Intelligent håndtering af en druknet start af en kompressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2366188A (en) * 1943-08-20 1945-01-02 Gen Motors Corp Refrigerating apparatus
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve
US4330999A (en) * 1977-07-27 1982-05-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerant compressor
AU615200B2 (en) * 1987-06-30 1991-09-26 Sanden Corporation Refrigerant circuit with passageway control mechanism

Also Published As

Publication number Publication date
JPH09256958A (ja) 1997-09-30
DE69704977D1 (de) 2001-07-05
DE69704977T2 (de) 2002-04-04
EP0797000A1 (fr) 1997-09-24

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