EP1283364A1 - Compresseur a pistons - Google Patents

Compresseur a pistons Download PDF

Info

Publication number
EP1283364A1
EP1283364A1 EP00929775A EP00929775A EP1283364A1 EP 1283364 A1 EP1283364 A1 EP 1283364A1 EP 00929775 A EP00929775 A EP 00929775A EP 00929775 A EP00929775 A EP 00929775A EP 1283364 A1 EP1283364 A1 EP 1283364A1
Authority
EP
European Patent Office
Prior art keywords
pressure
refrigerant
low
compressor
chamber
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.)
Withdrawn
Application number
EP00929775A
Other languages
German (de)
English (en)
Inventor
Kunio Zexel Cold Systems Company MIYAZAKI
Susumu Zexel Cold Systems Company ECHIZEN
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.)
Zexel Cold Systems Co
Original Assignee
Zexel Cold Systems Co
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 Zexel Cold Systems Co filed Critical Zexel Cold Systems Co
Publication of EP1283364A1 publication Critical patent/EP1283364A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F04B25/00—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders

Definitions

  • the present invention relates to a reciprocating compressor in which pistons are reciprocated to compress fluid, and more particularly, to a reciprocating compressor for compressing a refrigerant circulated through a refrigeration cycle.
  • a refrigerated transport vehicle which has a chilled compartment and a frozen compartment set to different temperatures and in which a refrigerant is circulated through evaporators arranged in the respective compartments.
  • a system one-compressor two-way system
  • a plurality of refrigerant circuits connected to the respective evaporators are configured to supply the refrigerant to the individual evaporators and the refrigerant flowing through the individual refrigerant circuits is returned to one compressor and then circulated.
  • Examined Japanese Utility Model Publication (KOKOKU) No. 63-43132 discloses refrigerant circuits for circulating a refrigerant through two evaporators, the circuits being configured such that the refrigerant is delivered under pressure from one discharge port of a compressor, then allowed to flow separately through the refrigerant circuits connected to the respective two evaporators, and again returned to the compressor.
  • the compressor has one discharge port and one suction port formed therein such that the flows of refrigerant returning from the two refrigerant circuits meet each other at the suction port in the compressor.
  • the compressor is constructed so as to suck in the refrigerant from one suction port, then compress the refrigerant and discharge the compressed refrigerant from one discharge port.
  • a swash plate compressor is known as a compressor having multiple discharge ports and multiple suction ports.
  • the swash plate compressor in which a swash plate is driven to successively reciprocate a plurality of pistons, may be used in a refrigerated transport vehicle.
  • sliding parts connecting the swash plate and the respective pistons to actuate the pistons have a small area while the load acting on the sliding parts per unit area is large, so that the sliding parts often fail to make satisfactory sliding motion.
  • the present invention was created in view of the above circumstances, and an object thereof is to provide a reciprocating compressor which is capable of independently controlling a plurality of temperature zones connected to respective refrigerant circuits and which is also excellent in operation efficiency.
  • a reciprocating compressor is characterized in that a main body of the compressor is provided with a plurality of cylinders, pistons for reciprocating within the respective cylinders, a first low-pressure chamber for introducing low-pressure refrigerant into a pumping chamber of at least one of the cylinders, at least one second low-pressure chamber for introducing low-pressure refrigerant into a pumping chamber of another cylinder, and a high-pressure chamber for letting in high-pressure refrigerant discharged from the pumping chambers, the low-pressure chambers are connected to respective suction pipes of refrigerant circuits, and the high-pressure chamber is connected to a discharge pipe of the refrigerant circuits.
  • the flows of refrigerant circulated through the refrigerant circuits are guided along the respective suction pipes and returned to the compressor through separate suction ports. Accordingly, the refrigerant flows can be controlled separately from each other and variations in the load acting on one evaporator can be prevented from affecting the other evaporator, thus making it possible to efficiently control the temperatures of respective different temperature zones independently of each other. Also, the provision of multiple suction ports serves to reduce the flow resistance. Namely, the performance of the compressor as well as the operation efficiency of an overall system including the compressor and the refrigerant circuits can be improved.
  • the compressor further comprises a crank chamber in which a crankshaft for actuating the pistons is housed, and the main body has pressure equalizing passages formed therein for connecting the respective low-pressure chambers and the crank chamber to each other.
  • the pressure equalizing passages are each formed at a location close to a line intersecting perpendicularly with an axis of the crankshaft and passing through a midpoint of the axis between adjacent ones of the pistons coupled to the crankshaft.
  • the equalizing passages are formed at locations such that splashes of the oil caused in the crank chamber due to a centrifugal force produced by the rotary motion of driving parts such as the crankshaft do not reach the equalizing passages. This prevents the oil from escaping from the crank chamber to the low-pressure chambers through the equalizing passages.
  • the main body has a plurality of cylinder chambers arranged in a row, the low-pressure chambers and the high-pressure chamber are arranged on opposite sides of the row of the cylinder chambers, and a partition wall for separating the low-pressure chambers from each other is formed at a location shifted from a line which intersects perpendicularly with a line connecting axes of adjacent ones of the cylinders and which passes through a midpoint between the adjacent cylinders.
  • This arrangement permits the equalizing passages to be formed at locations such that splashes of the oil caused in the crank chamber due to the centrifugal force produced by the rotary motion of the driving parts such as the crankshaft do not reach the equalizing passages.
  • the pressure equalizing passages each have an inner diameter of 1.5 mm to 3 mm.
  • FIG. 6 there is illustrated a refrigerated transport vehicle 1 equipped with a refrigerating machine.
  • the refrigerated vehicle 1 has a driver's cab 2 and a bed 3.
  • a reciprocating compressor hereinafter merely referred to as compressor 4 according to the embodiment of the present invention.
  • the compressor 4 is driven, through an electromagnetic clutch 5, by an engine for moving the vehicle or an auxiliary engine installed in the vehicle, neither is shown.
  • a container 6 having an enclosed, insulated structure is mounted on the bed 3.
  • the interior of the container 6 is divided into a front-side frozen compartment 6a and a rear-side chilled compartment 6b by a partition wall 7 which is made of a heat insulating material and arranged at an intermediate portion of the container.
  • Evaporators 10 and 11 are placed in the compartments 6a and 6b, respectively, for cooling the interiors of the respective compartments.
  • FIG. 7 shows refrigerant circuits for circulating a refrigerant through the evaporators 10 and 11 arranged in the compartments 6a and 6b, respectively, and the compressor 4.
  • the compressor 4 has two suction ports 4a and 4b and one discharge port 4c.
  • a discharge pipe 9 extends from the discharge port 4c, and a condenser 8 is inserted midway in the discharge pipe 9.
  • the condenser 8 is attached to an upper portion of an outer front wall of the container 6.
  • the discharge pipe 9 branches on a downstream side of the condenser 8 into pipes 9a and 9b leading to the frozen and chilled compartments, respectively.
  • the first evaporator 10 is inserted midway in the frozen compartment-side pipe 9a.
  • a solenoid valve (SV) 21a as a flow control valve is inserted in a portion of the frozen compartment-side pipe 9a more upstream than the first evaporator 10.
  • the solenoid valve 21a is a normally-closed valve and accordingly, switches ON to open when energized. When the temperature inside the frozen compartment 6a has lowered to a preset temperature (in this embodiment, -18°C), the solenoid valve switches OFF and thus is closed.
  • the frozen compartment-side pipe 9a is connected through an accumulator 15 to a first suction pipe 18a, which in turn is connected to the first suction port 4a of the compressor 4.
  • the second evaporator 11 is inserted midway in the chilled compartment-side pipe 9b.
  • a solenoid valve (SV) 21b as a flow control valve is inserted in a portion of the chilled compartment-side pipe 9b more upstream than the second evaporator 11.
  • the solenoid valve 21b is a normally-closed valve and accordingly, switches ON to open when energized.
  • the solenoid valve switches OFF and thus is closed.
  • the chilled compartment-side pipe 9b is connected through an accumulator 16 to a second suction pipe 18b, which in turn is connected to the second suction port 4b of the compressor 4.
  • the accumulators 15 and 16 are mounted to one side of the bed 3. Also, the evaporators 10 and 11 are respectively provided with temperature detectors 19 and 20, each serving also as a temperature setting device.
  • reference numerals 22a and 22b denote expansion valves associated with the respective evaporators 10 and 11.
  • FIGS. 1 to 5 show the structure of the compressor 4 in detail.
  • the compressor 4 has three cylinder chambers 40, 41 and 42 formed in a main body 28 thereof.
  • the cylinder chambers 40, 41 and 42 are arranged in a row and have respective upper open ends closed with a valve plate 35.
  • the cylinders 40, 41 and 42 have pistons 50 respectively received therein for sliding motion (reciprocating motion).
  • pumping chambers 43 for compressing the circulating refrigerant are defined inside the respective cylinders 40, 41 and 42 between the valve plate 35 and the corresponding pistons 50.
  • crank chamber 44 in which a crankshaft 54, connecting rods 52, etc. for reciprocating the pistons 50 are arranged, is defined in the main body 28 of the compressor 4 in communication with the cylinder chambers 40, 41 and 42.
  • the crankshaft 54 is rotatably supported by bearings 83 and is coupled to a driving gear 84 which is driven by the power of an engine, not shown.
  • the crankshaft 54 is coupled to the pistons 50 through the respective connecting rods 52. Namely, the rotary motion of the crankshaft 54 is converted into reciprocating motions of the pistons 50 through the respective connecting rods 52.
  • oil is fed as lubricant to driving parts such as the crankshaft 54 and the connecting rods 52, to suppress wear of the driving parts.
  • oil as such lubricant is circulated by a gear pump 80 such that the oil discharged from the gear pump 80 is supplied to individual sliding portions through an oil passage (in FIG. 10 referred to later, indicated at 90), not shown, formed in the crankshaft 54.
  • two low-pressure chambers 30A and 30B for introducing low-pressure refrigerant into the pumping chambers 43 are formed in the main body 28 of the compressor 4 on one side of the row of the cylinder chambers 40, 41 and 42.
  • the first and second low-pressure chambers 30A and 30B are separated from each other by a partition wall 36 and are also separated from the high-pressure chamber 32 by a partition wall 37.
  • the first low-pressure chamber 30A communicates with the pumping chamber 43 of the first cylinder 40 through a through hole 61 formed in the valve plate 35.
  • the second low-pressure chamber 30B communicates with the pumping chambers 43 of the second and third cylinders 41 and 42 through respective through holes 61 formed in the valve plate 35.
  • the high-pressure chamber 32 communicates with the pumping chambers 43 of all cylinders 40, 41 and 42 through respective through holes 62 formed in the valve plate 35.
  • Each of the through holes 61 is provided with a check valve 48 which opens to allow the refrigerant to flow only in the direction from the low-pressure chamber 30A, 30B to the pumping chamber 43, and each of the through holes 62 is provided with a check valve 49 which opens to allow the refrigerant to flow only in the direction from the pumping chamber 43 to the high-pressure chamber 32.
  • the main body 28 of the compressor 4 has two suction chambers 39 and one discharge chamber 38 defined therein, which chambers are closed with the valve plate 35 and are located below the two low-pressure chambers 30A and 30B and the high-pressure chamber 32, respectively.
  • One of the suction chambers 39 is connected to the first suction pipe 18a through the suction port 4a formed in the valve plate 35.
  • This suction chamber 39 communicates with the second low-pressure chamber 30B through a through hole 60 formed in the valve plate 35.
  • the other suction chamber 39 is connected to the second suction pipe 18b through the suction port 4b formed in the valve plate 35.
  • This suction chamber 39 communicates with the first low-pressure chamber 30A through a through hole 60 formed in the valve plate 35. Consequently, the low-pressure chambers 30A and 30B are connected to the suction pipes 18b and 18a through the respective suction chambers 39.
  • the discharge chamber 38 is connected to the discharge pipe 9 through the discharge port 4c formed in the valve plate 35.
  • the discharge chamber 38 also communicates with the high-pressure chamber 32 through a through hole 63 formed in the valve plate 35.
  • the high-pressure chamber 32 is connected to the discharge pipe 9 through the discharge chamber 38.
  • a pressure equalizing passage 70 is formed through a bottom wall 39a of each suction chamber 39 to connect the suction chamber 39 and the crank chamber 44 to each other.
  • the equalizing passages 70 have the effect (pressure equalizing effect) of relieving high pressure in the crank chamber 44 to maintain the pressures in the chambers 39 and 44 at an approximately equal level, and also allow oil M collecting in the suction chambers 39 to drop down into, or return to, the crank chamber 44.
  • the inner diameter of the equalizing passages 70 is set to 1.5 to 3 mm, preferably, 2 mm. If the inner diameter of the equalizing passages 70 is greater than 3 mm, too much oil flows out into the crank chamber. If, on the other hand, the inner diameter of the equalizing passages 70 is smaller than 1.5 mm, a satisfactory pressure equalizing effect possibly fails to be achieved.
  • the equalizing passages are formed at locations such that splashes of the oil caused in the crank chamber 44 due to the centrifugal force produced by the rotary motion of the crankshaft 54 and the connecting rods 52 do not reach the equalizing passages 70.
  • the equalizing passages are each formed on a line passing through approximately the midpoint between two adjacent connecting rods 52. To permit the equalizing passages 70 to be formed at such locations, the partition wall 36 separating the low-pressure chambers 30A and 30B from each other is shifted so as not to interfere with the equalizing passages 70.
  • the set temperatures for the frozen and chilled compartments 6a and 6b are -18°C and 2°C, respectively.
  • the compressor 4 is driven (crankshaft 54 is rotated) through the electromagnetic clutch 5 by the power of the engine, whereupon the refrigerant starts to circulate through the refrigerant circuits.
  • the high-temperature, high-pressure refrigerant discharged from the discharge port 4c of the compressor 4 flows through the discharge pipe 9 into the condenser 8, in which the refrigerant is turned into high-temperature, high-pressure liquid refrigerant by the action known in the art, and the liquid refrigerant then flows separately into the frozen compartment-side and chilled compartment-side pipes 9a and 9b.
  • the liquid refrigerant introduced into the frozen compartment-side pipe 9a flows through the solenoid valve (SV) 21a into the first evaporator 10.
  • SV solenoid valve
  • the interior of the frozen compartment 6a is cooled by the evaporator 10 by the action known in the art, so that the internal temperature gradually decreases down to the set temperature (-18°C).
  • the refrigerant flowing out of the first evaporator 10 passes through the first accumulator 15 into the first suction pipe 18a and then is introduced to the first suction port 4a of the compressor 4.
  • the liquid refrigerant introduced into the chilled compartment-side pipe 9b flows through the solenoid valve (SV) 21b into the second evaporator 11.
  • SV solenoid valve
  • the interior of the chilled compartment 6b is cooled by the evaporator 11 by the action known in the art, so that the internal temperature gradually lowers to the set temperature (2°C).
  • the refrigerant flowing out of the second evaporator 11 passes through the second accumulator 16 into the second suction pipe 18b and then is introduced to the second suction port 4b of the compressor 4.
  • the refrigerant introduced to the first suction port 4a from the frozen compartment 6a flows into the corresponding suction chamber 39 and then to the second low-pressure chamber 30B through the through hole 60, as indicated by the arrows in FIG. 5.
  • the oil M separated from the refrigerant collects in the bottom 39a of the suction chamber 39 and then drops down into, and thus returns to, the crank chamber 44 through the equalizing passage 70.
  • the refrigerant flowing into the second low-pressure chamber 30B is then introduced into the pumping chambers 43 of the second and third cylinders 41 and 42 through the through holes 61 and compressed by the respective pistons 50.
  • the resulting high-temperature, high-pressure refrigerant is discharged into the high-pressure chamber 32 through the through holes 62, then introduced into the discharge chamber 38 through the through hole 63, and delivered again to the discharge pipe 9 from the discharge port 4c.
  • the refrigerant introduced to the second suction port 4b from the chilled compartment 6b flows into the corresponding suction chamber 39, in which the oil M separated from the refrigerant collects in the bottom 39a of the suction chamber 39 and then drops down into, and thus returns to, the crank chamber 44 through the equalizing passage 70.
  • the refrigerant flowing into the first low-pressure chamber 30A is then introduced into the pumping chamber 43 of the first cylinder 40 through the through hole 61 and compressed.
  • the resulting high-temperature, high-pressure refrigerant is discharged into the high-pressure chamber 32 through the through holes 62, whereby the refrigerant discharged from the first cylinder chamber 40 and that discharged from the second and third cylinder chambers 41 and 42 meet each other in the high-pressure chamber.
  • the refrigerant is then introduced into the discharge chamber 38 through the through hole 63 and delivered again to the discharge pipe 9 from the discharge port 4c.
  • a circulation system (hereinafter referred to as one-compressor two-suction system) is employed in which one compressor 4 has separate suction ports 4a and 4b associated with the respective evaporators 10 and 11 and not communicating with each other inside the compressor 4, and the refrigerant from the compressor 4 is caused to flow through separate routes to be supplied to the respective evaporators 10 and 11, the refrigerant flows from which are collected through the respective suction ports 4a and 4b.
  • the refrigerant flows can be controlled separately from each other and variations in the load acting on one evaporator can be prevented from affecting the other evaporator, thus making it possible to efficiently control the temperatures of the respective different temperature zones (frozen and chilled compartments 6a and 6b) independently of each other.
  • the provision of the two suction ports 4a and 4b serves to reduce the flow resistance.
  • FIG. 8 illustrates the experimental data showing temperature changes of the respective compartments 6a and 6b under various traveling conditions and operating states of the solenoid valves (SV) 21a and 21b associated with the respective compartments 6a and 6b.
  • L1 indicates the temperature change of the outside air with time
  • L2 indicates the temperature change of the rear-side chilled compartment 6b
  • L3 indicates the temperature change of the front-side frozen compartment 6a
  • L4 indicates the open/closed state of the solenoid valve 21a associated with the frozen compartment (front compartment) 6a
  • L5 indicates the open/closed state of the solenoid valve 21b associated with the chilled compartment (rear compartment) 6b.
  • SA denotes a service area
  • CR denotes the refrigerating machine.
  • FIG. 9(a) shows the data obtained with the one-compressor two-suction system according to the embodiment
  • FIG. 9(b) shows the data obtained with the conventional one-compressor two-way system.
  • the opening/closing of the door of the chilled compartment 6b does not affect the temperature in the frozen compartment 6a.
  • the opening/closing of the door of the chilled compartment 6b exerts an influence on the frozen compartment 6a side. Specifically, the temperature in the frozen compartment 6a rises by S with a certain time lag after the temperature rise of the chilled compartment 6b.
  • the internal temperature (L3) of the frozen compartment 6a shows a rise at point D, but this temperature rise was caused by a defrosting (DEF) operation and does not indicate an influence exerted by the chilled compartment 6b.
  • DEF defrosting
  • Table 1 below shows the comparison between the conventional one-compressor two-way system and the one-compressor two-suction system according to the embodiment in respect of the rate of operation (ratio of the compressor operating time to the total time).
  • Present Invention Conventional System Front compartment -18 °C Front compartment 57.6% Front compartment 76.2% Rear compartment 2°C Rear compartment 26.9% Rear compartment 35.0% Front compartment 2°C Front compartment 11.8% Front compartment 27.5% Rear compartment -18°C Rear compartment 69.4% Rear compartment 90.0%
  • the one-compressor two-suction system is lower in the rate of operation than the one-compressor two-way system, proving that the former system has excellent operation efficiency. Consequently, according to the embodiment, a sufficient cooling effect can be obtained at a lower rate of operation.
  • the compressor 4 has separate suction ports 4a and 4b associated with the respective evaporators 10 and 11 and not communicating with each other.
  • the refrigerant from the compressor 4 is caused to flow through separate routes to be supplied to the respective evaporators 10 and 11, and the refrigerant flows therefrom are collected through the respective suction ports 4a and 4b.
  • the refrigerant flows can be controlled separately from each other and variations in the load acting on one evaporator can be prevented from affecting the other evaporator, thus making it possible to efficiently control the temperatures of the respective different temperature zones (frozen and chilled compartments 6a and 6b) independently of each other.
  • the provision of the two suction ports 4a and 4b serves to reduce the flow resistance. Namely, the performance of the compressor 4 as well as the operation efficiency of the overall system can be improved.
  • the pressure equalizing passages 70 are formed through the bottom walls 39a of the suction chambers 39 to connect the suction chambers 39 and the crank chamber 44 to each other, high-pressure gas (pressure) can be relieved from the crank chamber 44 to maintain the pressures in the chambers 39 and 44 at an equal level, and also the oil M collecting in the suction chambers 39 can be returned to the crank chamber 44. Accordingly, the oil can be retained in the compressor 4 without the need to provide a mechanism for returning the oil, such as an oil separator, thus making it possible to provide a high-reliability compressor.
  • the inner diameter of the equalizing passages 70 is set to 1.5 to 3 mm, it is possible to increase the quantity of return or recovery of the oil flowing through the refrigerant circuits together with the refrigerant, without spoiling the pressure equalizing effect.
  • the equalizing passages 70 are formed at locations such that splashes of the oil caused in the crank chamber 44 due to the centrifugal force produced by the rotary motion of the crankshaft 54 and the connecting rods 52 do not reach the equalizing passages. This arrangement prevents the oil in the crank chamber 44 from escaping to the suction chambers 39 through the equalizing passages 70.
  • the present invention is not limited to the foregoing embodiment alone and may be modified in various ways without departing from the scope and spirit of the invention.
  • advantages similar to those of the foregoing embodiment can be obtained also with a reciprocating compressor 4 having two cylinder chambers 40 and 41, as shown in FIG. 10.
  • identical reference numerals are used to denote elements identical with those of the foregoing embodiment, and detailed description of the elements is omitted.
  • two low-pressure chambers 30A and 30B are provided for the respective two suction ports 4a and 4b.
  • three low-pressure chambers corresponding to the respective cylinder chambers 40, 41 and 42 may be formed and selectively connected to the two suction ports 4a and 4b.
  • compressors having three or two cylinder chambers, by way of example, but the number of cylinder chambers may be more than three. Also, the number of suction ports is not limited to two and may be three or more corresponding to the number of refrigerant circuits.
  • the reciprocating compressor according to the present invention is applied to a refrigerated transport vehicle etc. having frozen and chilled compartments, and is used to compress the refrigerant sucked in from the frozen and chilled compartment sides and to deliver the compressed refrigerant again to the frozen and chilled compartment sides.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP00929775A 2000-05-17 2000-05-17 Compresseur a pistons Withdrawn EP1283364A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2000/003158 WO2001088374A1 (fr) 2000-05-17 2000-05-17 Compresseur a pistons

Publications (1)

Publication Number Publication Date
EP1283364A1 true EP1283364A1 (fr) 2003-02-12

Family

ID=11736040

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00929775A Withdrawn EP1283364A1 (fr) 2000-05-17 2000-05-17 Compresseur a pistons

Country Status (2)

Country Link
EP (1) EP1283364A1 (fr)
WO (1) WO2001088374A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010097542A1 (fr) * 2009-02-27 2010-09-02 Danfoss Commercial Compressors Compresseur frigorifique à pistons
WO2022243201A1 (fr) * 2021-05-18 2022-11-24 thyssenkrupp Presta Ilsenburg GmbH Compresseur à pistons, en particulier compresseur à pistons radiaux

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014054092A1 (fr) * 2012-10-01 2014-04-10 株式会社前川製作所 Compresseur à piston

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5459607A (en) * 1977-10-19 1979-05-14 Tama Seisakushiyo Kk Compressor for car cooler
JPS6343132Y2 (fr) * 1984-12-27 1988-11-10
JPS63100681U (fr) * 1986-12-19 1988-06-30

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0188374A1 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010097542A1 (fr) * 2009-02-27 2010-09-02 Danfoss Commercial Compressors Compresseur frigorifique à pistons
FR2942655A1 (fr) * 2009-02-27 2010-09-03 Danfoss Commercial Compressors Compresseur frigorifique a pistons
CN102325998A (zh) * 2009-02-27 2012-01-18 丹佛斯商业压缩机公司 活塞制冷压缩机
US8512015B2 (en) 2009-02-27 2013-08-20 Danfoss Commercial Compressors Piston refrigeration compressor
WO2022243201A1 (fr) * 2021-05-18 2022-11-24 thyssenkrupp Presta Ilsenburg GmbH Compresseur à pistons, en particulier compresseur à pistons radiaux

Also Published As

Publication number Publication date
WO2001088374A1 (fr) 2001-11-22

Similar Documents

Publication Publication Date Title
KR101386469B1 (ko) 냉장고
CN102947652B (zh) 冰箱的冷却系统和用于压缩机流体的吸入系统
US5531078A (en) Low volume inlet reciprocating compressor for dual evaporator refrigeration system
JP2000080983A (ja) 圧縮機
EP1283364A1 (fr) Compresseur a pistons
KR100361787B1 (ko) 냉장고
KR20030032121A (ko) 사판식 압축기
KR100312780B1 (ko) 압축기 내장형 오일분리기
KR20100087492A (ko) 냉장냉동시스템
JP2000283045A (ja) レシプロ型圧縮機
CN107477904B (zh) 制冷系统
KR100461657B1 (ko) 다수개의 증발기를 구비한 냉동사이클
US20130094984A1 (en) Variable displacement compressor shaft oil separator
KR100776075B1 (ko) 오일분리기 일체형 응축기
KR102295156B1 (ko) 냉장고
KR100747845B1 (ko) 냉장고
JP2001074325A (ja) 二段圧縮冷凍冷蔵装置
CN216812096U (zh) 压缩机及制冷设备
JP4406275B2 (ja) 冷蔵庫
KR20100035018A (ko) 차량용 냉각시스템의 압축기
KR20050077605A (ko) 멀티형 냉장고
KR100753920B1 (ko) 압축기의 액 압축 방지구조
KR100461656B1 (ko) 다수개의 증발기를 구비한 냉동사이클
JPH08110103A (ja) 冷蔵庫用冷凍サイクル
JPH0311167A (ja) 往復動型圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20010913

AK Designated contracting states

Designated state(s): DE ES FR GB IT

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20040228