US3855836A - Device for controlling coolant pressure in evaporator - Google Patents

Device for controlling coolant pressure in evaporator Download PDF

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Publication number
US3855836A
US3855836A US00435971A US43597174A US3855836A US 3855836 A US3855836 A US 3855836A US 00435971 A US00435971 A US 00435971A US 43597174 A US43597174 A US 43597174A US 3855836 A US3855836 A US 3855836A
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United States
Prior art keywords
pressure
collector
coolant
control valve
pressure control
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Expired - Lifetime
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US00435971A
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English (en)
Inventor
R Takahashi
K Kanemoto
T Ito
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Hitachi Ltd
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Hitachi Ltd
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    • 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
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas

Definitions

  • ABSTRACT A mechanism for regulating pressure in an evaporator is provided integrally with a collecting chamber for collecting a coolant from an evaporator, which chamber is provided in a valve for controlling an expansion rate of a coolant, said valve being disposed in a heat cycle system for use in a car cooler or the like, thereby presenting ease in installation, ease in maintenance and ease in manufacture.
  • This invention relates to a coolant controlling device for use in an air conditioning apparatus, and more particularly to a mechanism for controlling a coolant pressure in an evaporator.
  • the minimum evaporating pressure in the evaporator be set to a level at which no growth of frost arises, so as to cause evaporation of the coolant usually at a pressure over the predetermined level. Hitherto, to prevent the freezing of an evaporator or the like, the coolant evaporating pressure controlling device has been used.
  • Such a coolant evaporating pressure controlling device because it is independent of the other units of cooling system, presents various problems and difficulties in that there have to be provided various pipings for connecting the units, such as heat sensitive pipes, pressure-equalizing pipes or the like, resulting in the complicate construction, the leakage of gas, lowering of the efficiency in installation, and increase in the manufacturing cost as well as in a space required for the unit.
  • Another object of the present invention is to provide a device for controlling a coolant pressure in the evaporator which is simple and easy in the maintenance and check.
  • a further object of the present invention is to provide a device for controlling a coolant pressure in an evaporator which is small in size and superior in the controlling capability.
  • the present invention is directed to providing a pressure controlling valve mechanically integral with a collecting chamber leading to an outlet port of an evaporator, said collector serving to collect the coolant from the evaporator.
  • FIG. 1 illustrates a cooling system relating to the present invention
  • FIG. 2 is a longitudinal cross-sectional view illustrating an expansion valve and a pressure control valve of FIG. 1.
  • FIG. 3 is a modification of FIG. 2.
  • FIG. 4 is-a plot representing heat load exerted on an evaporator and a characteristic of a diaphragm responsive to temperature and pressure of a coolant within the evaporator.
  • FIG. 5 is an enlarged view of a spindle of FIGS. 2 and 3, and
  • FIG. 6 is a further embodiment of the present invention.
  • FIG. 1 shows an embodiment of a cooling system according to the present invention
  • At 1 is a compressor for compressing a coolant into a gaseous coolant of high temperature and high pressure
  • at 2 is a condenser for cooling the gaseous coolant for liquidification
  • at 3 is a liquid receiver, in which the coolant is separated into gas and liquid
  • at 4 is an expansion valve control portion in which the liquid coolant from the liquid receiver 3 is subjected to expansion to be fed to an evaporator 6.
  • the coolant gas from the evaporator 6 returns via a pressure control valve portion 14 to the compressor 1 to control the pressure in the evaporator 6.
  • the expansion valve control portion 4 and the pressure control valve portion 14 are illustrated in detail in FIG. 2.
  • the expansion valve control portion 4 includes a distributor 7 for introducing the coolant from the expansion valve 5 into the evaporator 6, and a collector 8 for recovering same, said distributor 7 and collector 8 being constructed integrally with each other.
  • the collector 8 is partitioned by an expansion-valve actuating diaphragm 12 into a primary chamber 9 (a heat sensitive chamber) and a secondary chamber 10, both of which are communicated with each other by way of a connecting pipe 11 provided in a body proper of the device.
  • the aforesaid expansion-valve actuating diaphragm is provided therein with a heat sensitive member 20 which is sealingly filled therein, with its secondary chamber side being communicated by way of a connecting rod 13 with a valve body, such as a ball valve of the expansion valve 5.
  • the expansion valve 5 is so adapted as to control a flow rate of coolant from the liquid receiver 3 and to be closed by means of a spring or the like when the pressure in the primary chamber 9 becomes low.
  • the pressure control valve portion 14 includes a valve body 19 and a spindle 15, a bellows 16, a spring 17 and an adjusting screw 18.
  • the adjusting means which includes the aforesaid spring 17 and adjusting screw 18, to the pressure in the primary chamber 9, if the pressure in the primary chamber 9 relatively increases, the spindle 15 is forced downwardly, thereby bringing an outlet port 21 of pres sure control valve portion 14 into communication with the primary chamber 9. Accordingly, the pressure in the evaporator 6 may be maintained at a level above the pressure which has been set by said adjusting means.
  • the coolant gas of high pressure and high temperature from the compressor 1 is cooled in the condenser 2 to a liquid state then introduced into the liquid receiver 3, followed by the abrupt pressure-reduction in the expansion valve 5, then heatexchanged in the evaporator 6, and then returned by way of the pressure control valve portion 14 into the compressor 1.
  • the coolant in the embodiment described, is introduced from the liquid receiver 3 into the expansion valve control portion 4 as well as the pressure control valve portion 14 which are provided integrally with each other.
  • the expansion valve 5 in the expansion valve control portion 4 is so designed as to open or close its valve body, such as a ball, by means of the connecting rod 13, depending upon the pressure difference between the internal pressure which varies according to the change in temperature of heat sensitive member 20 sealingly filled in the diaphragm 12, which change is caused due to the coolant introduced in the collector 8 from the evaporator 6, and the pressure in the secondary chamber 10 of the collector 8 which is communicated by way of the communicating passage 11 with the primary chamber 9 thereof.
  • the coolant may be introduced in a proper amount accordingly, so that the breakage in the cooling system or reduction in the performance thereof due to freezing may be avoided, with the result of the stable performance.
  • the coolant collector 8 and the pressure control valve portion 14 are provided integrally with each other, with the pressure of the coolant in the collector 8 being exerted on the side of spindle 15 of the bellows 16, so that the movement of the spindle 15 may be controlled by ballancing the pressure in the collector 8 and the spring force of spring 17, thereby controlling the flow rate of coolant, thus controlling the internal pressure in the evaporator 6. It is natural that the critical pressure may be set up by exerting the spring pressure on the bellows 16 by turning the adjusting screw 18.
  • the pressure control valve portion 14 may be integrally formed under the collector 8, considering the fluidity of the internal liquid within the expansion valve control portion 4 and pressure control valve portion 14, then the circulation of the coolant to the compressor will be facilitated, without causing a trouble in the compressor due to oil shortage.
  • this brings about another advantage that no oil return passage is required, although such a passage is essential where the expansion valve control portion 4 and the constant pressure control valve portion 14 are separately provided, and that no oil sump is required in the piping.
  • FIG. 3 shows a modification of the device of FIG. 2.
  • a communicating passage 11 is provided in the body proper 19 of the device, which comprises the expansion valve control mechanism and pressure control valve mechanism, in a manner to communicate the secondary chamber 10 of collector 8 with the outlet port 2] of pressure control valve, and the actuation of the expansion valve 5 is effected by a pressure difference caused between the aforesaid output port 21 of pressure control valve (the pressure in the secondary chamber 10) and the diaphragm portion.
  • This is most advantageous where the characteristics in the heat sensitive members of diaphragm and that of the secondary pressure portion do not present the equlibrium in temperature and pressure such as shown in FIG. 4.
  • FIG. 4 shows a communicating passage 11 in the body proper 19 of the device, which comprises the expansion valve control mechanism and pressure control valve mechanism, in a manner to communicate the secondary chamber 10 of collector 8 with the outlet port 2] of pressure control valve, and the actuation of the expansion valve 5 is effected by a pressure difference caused between the aforesaid
  • Fe is representative of the secondary pressure in the diaphragm, Pt a heat sensitive pressure in the diaphragm, Q a heat load in the evaporator 6, and AP a critical pressure difference, and if the pressure difference becomes larger than the critical pressure difference, then the expansion valve 5 is brought into its fully open position.
  • the valve rod of expansion valve 5 it is required that the valve rod of expansion valve 5 be forced downwardly so as to keep opening the orifice by overcoming the evaporating pressure, i.e., the critical pressure, or the pressure control valve pressure.
  • the pressure lower than the pressure of the low pressure control valve acts on the diaphragm, the relationship as plotted in FIG. 4 is not required in a strict sense. Accordingly, if the controlling valve actuating range is set to a point just above the critical freezing point, no accurate control means is required, and thus the ready manufacture of the control valve will result.
  • FIG. 4 represented by Fe is the secondary pressure of the coolant, which is the pressure in the secondary chamber 10 of FIGS. 2 and 3.
  • Pt is the pressure corresponding to the change in the coolant temperature in the primary chamber 9 or the collector 8.
  • P6 and Pt act on the expansion valve in a manner that the pressure Pt acts to open the valve and the pressure Pe acts to close the valve.
  • the pressure difference AP between Pt and Fe may be referred to as an open angle of the expansion valve.
  • the pressure control valve When the heat load is decreased to less than O1, in other words, when ambient temperature is dropped, the pressure control valve will be brought into actuation. By the action of the pressure control valve, the pressure Pe remains at a given pressure level. Depending upon the operational conditions, the pressures Pt and Pe will have a close access to each other. At this time, hunting may occure, with the accompanying vibration of the constant pressure controlling valve. To avoid such a phenomenon, the difference between Pt and Fe should be large. It is preferable from this viewpoint that the outlet port 21 of pressure control valve be communicated with the secondary chamber as shown in FIG. 3.
  • FIG. 5 is an enlarged view of the spindle of FIGS. 2 and 3.
  • the spindle 15 has a cylindrical bore provided centrally thereof and communicating by way of orifices 31 with space 33.
  • the pressure of coolant is transmitted through said orifices, via the outside of a flange 35 serving as a resistor, and via the outside of a stopper 37 or through a cut-away portion 39, and eventually to the bellows 16.
  • the reason why the pressure of the coolant introduced in the collector 8 from the evaporator is applied via the resistor means to the bellows 16 is that the bellows 16 may be controlled for its responsiveness, and the vibration of the spindle 15 may be prevented.
  • FIG. 6 illustrates a further embodiment of the present invention.
  • the expansion valve control portion is provided independently, likewise in the conventional device, while the collector 8 for collecting the coolant from the evaporator and the pres sure control valve portion 14 are formed integrally with each other.
  • Such a construction is also advantageous from the viewpoint of performance.
  • the efficacy of the device will be greatly increased by providing the expansion valve integrally with the pressure control valve portion, as shown in FIGS. 2 or 3.
  • the distributors for supplying the coolant to the expansion valve and the evaporator are separately provided one from another.
  • the spindle 15 is the same in construction as that of FIG. 5.
  • expansion valve and the pressure control valve in FIGS. 2 and 3 are formed integrally, it is recommendable that the manufacture and the testing be individually carried out, after which those members be assembled together, with mechanical sealing rings being interposed therebetween for preventing the leakage of the coolant therefrom.
  • a condenser for condensing the coolant compressed in said compressor into a liquid
  • a liquid receiver for separating the coolant from the condenser into liquid and gas
  • a pressure control valve for maintaining the pressure in the evaporator at a level higher than a predetermined level
  • said evaporator includes a plurality of coolant gas passages arranged in parallel and a collector for collecting the coolant flowing through said plurality of the coolant gas passages;
  • biasing means provided in said housing, said biasing means having one side, to which is exerted the gas pressure in the collector;
  • valve means provided between the collector and the means for returning the coolant to the compressor and having an opening capable for varying its size.
  • valve means has a substantially cylindrical bore communicating with said collector, and a substantially cylindrical movable means retained within said cylindrical bore and adapted to be moved by said biasing means;
  • said substantially cylindrical bore communicating with said collector and having a diametrically enlarged space at a predetermined distance apart from said collector;
  • said movable means actuated by said biasing means being provided with a notched portion near to the collector;
  • said biasing means consists of a bellows, and a passage communicating the bellows with the collecting chamber having a cylindrical central bore provided in the movable means, and a resistive passage crossing said movable means and formed between said movable means and an inner wall of said cylindrical bore of said housing which is adjacent to the bellows.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
US00435971A 1973-01-24 1974-01-23 Device for controlling coolant pressure in evaporator Expired - Lifetime US3855836A (en)

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JP48009542A JPS5740423B2 (enrdf_load_stackoverflow) 1973-01-24 1973-01-24

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4227380A (en) * 1979-11-09 1980-10-14 Frick Company Single casing, multiple duty valve
US4476691A (en) * 1982-06-04 1984-10-16 Tokyo Shibaura Denki Kabushiki Kaisha Refrigeration cycle apparatus
EP0148503A3 (en) * 1983-12-28 1986-06-04 Kabushiki Kaisha Saginomiya Seisakusho Differential pressure valve
EP0147855A3 (en) * 1983-12-28 1986-06-11 Kabushiki Kaisha Saginomiya Seisakusho Refrigerating system
US5127237A (en) * 1990-01-26 1992-07-07 Tgk Co. Ltd. Expansion valve
US5182920A (en) * 1991-07-15 1993-02-02 Mitsubishi Denki Kabushiki Kaisha Refrigeration cycle system
US5423480A (en) * 1992-12-18 1995-06-13 Sporlan Valve Company Dual capacity thermal expansion valve
EP1382920A2 (en) 2002-07-17 2004-01-21 Fujikoki Corporation Expansion valve
US20060005556A1 (en) * 2003-03-06 2006-01-12 Tgk Co., Ltd. Flow rate control valve
WO2006002880A1 (de) * 2004-07-02 2006-01-12 Behr Gmbh & Co. Kg Klimaanlage für ein kraftfahrzeug
US20090241633A1 (en) * 2008-03-26 2009-10-01 National Machinery Llc Slide with segmented tooling held closed by stationary remote spring
US20140298840A1 (en) * 2011-08-25 2014-10-09 Valeo Systemes Thermiques Device For Controlling The Flow Of A Coolant, And Circuit Including Such A Device
US20150135749A1 (en) * 2012-05-14 2015-05-21 Denso Corporation Flow rate adjustment valve for refrigeration cycle
CN105531550B (zh) * 2013-09-11 2017-05-31 株式会社电装 膨胀阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61240059A (ja) * 1985-04-17 1986-10-25 株式会社日立製作所 自動車用空気調和装置の蒸発器凍結防止装置
DE102018124755A1 (de) * 2018-10-08 2020-04-09 Denso Automotive Deutschland Gmbh Dual-Expansionsventil

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2409661A (en) * 1943-11-15 1946-10-22 Detroit Lubricator Co Refrigerant distributing means
US2463951A (en) * 1945-05-25 1949-03-08 Detroit Lubricator Co Refrigeration expansion valve
US2642724A (en) * 1949-07-20 1953-06-23 Detroit Controls Corp Insert type thermostatic expansion valve
US3640086A (en) * 1970-02-27 1972-02-08 American Standard Inc Refrigerant flow control employing plural valves
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2409661A (en) * 1943-11-15 1946-10-22 Detroit Lubricator Co Refrigerant distributing means
US2463951A (en) * 1945-05-25 1949-03-08 Detroit Lubricator Co Refrigeration expansion valve
US2642724A (en) * 1949-07-20 1953-06-23 Detroit Controls Corp Insert type thermostatic expansion valve
US3640086A (en) * 1970-02-27 1972-02-08 American Standard Inc Refrigerant flow control employing plural valves
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4227380A (en) * 1979-11-09 1980-10-14 Frick Company Single casing, multiple duty valve
US4476691A (en) * 1982-06-04 1984-10-16 Tokyo Shibaura Denki Kabushiki Kaisha Refrigeration cycle apparatus
EP0148503A3 (en) * 1983-12-28 1986-06-04 Kabushiki Kaisha Saginomiya Seisakusho Differential pressure valve
US4593535A (en) * 1983-12-28 1986-06-10 Kabushiki Kaisha Saginomiya Seisakusho Differential pressure valve
EP0147855A3 (en) * 1983-12-28 1986-06-11 Kabushiki Kaisha Saginomiya Seisakusho Refrigerating system
US5127237A (en) * 1990-01-26 1992-07-07 Tgk Co. Ltd. Expansion valve
US5182920A (en) * 1991-07-15 1993-02-02 Mitsubishi Denki Kabushiki Kaisha Refrigeration cycle system
US5423480A (en) * 1992-12-18 1995-06-13 Sporlan Valve Company Dual capacity thermal expansion valve
EP1382920A3 (en) * 2002-07-17 2004-04-21 Fujikoki Corporation Expansion valve
US20040011078A1 (en) * 2002-07-17 2004-01-22 Kazuto Kobayashi Expansion valve
EP1382920A2 (en) 2002-07-17 2004-01-21 Fujikoki Corporation Expansion valve
US6942160B2 (en) 2002-07-17 2005-09-13 Fujikoki Corporation Expansion valve
US20060005556A1 (en) * 2003-03-06 2006-01-12 Tgk Co., Ltd. Flow rate control valve
WO2006002880A1 (de) * 2004-07-02 2006-01-12 Behr Gmbh & Co. Kg Klimaanlage für ein kraftfahrzeug
US20090241633A1 (en) * 2008-03-26 2009-10-01 National Machinery Llc Slide with segmented tooling held closed by stationary remote spring
US8024952B2 (en) * 2008-03-26 2011-09-27 National Machinery Llc Slide with segmented tooling held closed by stationary remote spring
US20140298840A1 (en) * 2011-08-25 2014-10-09 Valeo Systemes Thermiques Device For Controlling The Flow Of A Coolant, And Circuit Including Such A Device
US9897366B2 (en) * 2011-08-25 2018-02-20 Valeo Systemes Thermiques Device for controlling the flow of a coolant, and circuit including such a device
US20150135749A1 (en) * 2012-05-14 2015-05-21 Denso Corporation Flow rate adjustment valve for refrigeration cycle
US9696070B2 (en) * 2012-05-14 2017-07-04 Denso Corporation Flow rate adjustment valve for refrigeration cycle
CN105531550B (zh) * 2013-09-11 2017-05-31 株式会社电装 膨胀阀

Also Published As

Publication number Publication date
JPS49108657A (enrdf_load_stackoverflow) 1974-10-16
JPS5740423B2 (enrdf_load_stackoverflow) 1982-08-27

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