US3552137A - Refrigeration compressor capacity control system - Google Patents

Refrigeration compressor capacity control system Download PDF

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Publication number
US3552137A
US3552137A US775788A US3552137DA US3552137A US 3552137 A US3552137 A US 3552137A US 775788 A US775788 A US 775788A US 3552137D A US3552137D A US 3552137DA US 3552137 A US3552137 A US 3552137A
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United States
Prior art keywords
nozzle
pressure
control valve
bellows
capacity control
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Expired - Lifetime
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US775788A
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English (en)
Inventor
Hans P Christensen
Alfred Frosley
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Johnson Controls Denmark ApS
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Thomas Ths Sabroe and Co
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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
    • 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
    • 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

  • a multi-cylinder refrigeration compressor capacity control system in which a plurality of compressor unloader mechanisms are operated by means of a capacity control valve having a displaceable valve member the position of which is adjustable in response to the compressor suction pressure in cooperation with an opposed valve actuating pressure.
  • the actuating pressure is varied by means of a pressure control valve in accordance with the required amount of cold, the pressure control valve connecting the compressor suction side to the actuating pressure side of the capacity control valve through a nozzle.
  • a nozzle-closing plate can be positioned in a more or less inclined position by a spring-loaded bellows, and the nozzle and nozzle-closing plate are rotationally adjustable in relation to one another.
  • the number of individual cylinders in service should correspond to the amount of cold required, and to this end an unloader mechanism oper'ates hydraulically on power from the oil pressure of the lubricating system to load and unload the cylinders in response to suction pressure variations.
  • the unloader mechanism provides automatic capacity control and also permits the compressor to start unloaded. Without oil pressure the unloader mechanism holds suction valves open so that the associated cylinders operate unloaded. Under oil pressure the unloader permits suction to function normally and cylinders to operate at full capacity.
  • the unloader mechanism comprises two distinct components one of which is a suction valve lifting device for each of the cylinders, and the other component is a capacity control valve which, in response to suction pressure variations, connects a suitable number of the unloader mechanisms to the oil pressure, or to the crankcase.
  • the position of the capacity control valve is determined by the suction pressure in the crankcase on one hand, and by the actuating oil pressure on the other 'hand, and to adjust the range of cold the oil pressure acting on the capacity control valve can be varied partly by a throttle valve in the oil supply line leading to the control valve, partly by a pressure control valve connected between the throttle valve and the capacity control valve.
  • the main object of the present invention is to provide a novel and improved pressure control valve for controlling the actuating pressure on the capacity control valve.
  • Another object is to indicate a capacity control system for continuous adjustment of the controlling range without the need for replacement of springs and/or displacement of lever fulcrums or the like.
  • a further object of the invention is the provision of a novel pressure control valve including a bellows, the expansion and contraction of which, in response to variation of the crankcase pressure against the action of spring means, serves to open and close a nozzle connected to the control oil pressure applied to the capacity control valve.
  • a still further object is to improve the continuous operation of the pressure control valve by varying the pressure around the bellows, hereinafter called the pilot pressure.
  • FIG. 1 shows a refrigeration compressor capacity control system embodying the present invention
  • FIG. 2 is a sectional view of a first embodiment of a pressure control valve according to the invention, said valve being also useful as a pressure transmitter for controlling the pilot pressure supplied to the pressure control valve,
  • FIG. 3 shows an alternative embodiment of the pressure control valve according to FIG. 1, in which the nozzle-closing plate is of a different construction
  • FIG. 4 shows a further embodiment of the pressure control valve of the invention, in which the discharge opening of the nozzle is radially displaceable
  • FIG. 5 is an alternative similar to FIG. 4 with the exception that the nozzle is adjustable along a circular arc
  • FIG. 6 shows a portion of the system as shown in FIG. 1, 'with a pressure transmitter being added
  • FIG. 7 is similar to FIG. 6, only the pressure transmitter being replaced by a thermostatic pressure transmitter,
  • FIG. 8 is similar to FIG. 6, except that the pressure transmitter and its connections are difierent, and
  • FIG. 9 is a sectional view of a pressure transmitter as used in the system according to FIG. 8, said pressure transmitter being mainly as the one shown in FIG. 2, only the arrangement of nozzle-closing plate being amended.
  • FIG. 1 a capacity control system of a multi-cylinder refrigeration compressor is shown, in which the unloader mechanisms of the compressor cylinders are of any suitable conventional kind.
  • the number of cylinders are four, indicated by 12, 13, 14 and 15, respectively, and the suction valves 16, 17, 18 and 19 are in the form of annular valve rings which are arranged to be lifted from their seats on the cylinders by lifter pins. Hydraulic pressure for operation of the unloader mechanisms is supplied from the oil pressure system of the compressor, preferably through a capacity control valve 20.
  • the capacity control valve 20 includes a slide valve 21 which is displaceable within a housing 22 and is provided with a pair of annular ribs 23 and 24 adjacent its opposite ends to define a chamber 25.
  • the axial length of said chamber 25 is sufficient to overlie all the openings of a plurality of conduits 26, 27, 28 and 29 connected to the side wall of the valve housing and leading to the respective unloader mechanisms of the compressor cylinders 12, 13, 14 and 15.
  • the openings of conduits 26, 27, 28 and 29 are longitudinally spaced in relation to one another so as to enable either of the annular ribs 23 and 24 to be positioned in engagement with the wall between subsequent conduit openings.
  • an oil pressure supply conduit 30 is connected at a position so as to be in communication with the chamber 25 at all times when the slide valve is moving in either direction.
  • oil pressure is supplied to one or more of the conduits 26, 27, 28 and 29 leading to the compressor cylinders when the respective conduit is in communication with chamber 25. As shown, oil pressure is supplied to cylinders 14 and while cylinders 12 and 13 are unloaded.
  • the supply conduit 30 is connected to the oil lubrication system of the compressor, not shown, through a main supply conduit 31 which is also connected, through a line 32 with a throttle valve 33, to the top of valve housing 22, whereby oil pressure upon being reduced in throttle valve 33 serves to urge the slide valve member 21 downwards against the action of a spring 34.
  • the lower end wall 35 of housing 22 is in communication, through a relief conduit 36, with the crankcase of the compressor, not shown, so that suction pressure prevails in the interior of the valve housing 22 beneath the slide valve member. As a result, the suction pressure will be connected through conduits 26 and 27 to the unloader mechanisms of cylinders 12 and 13.
  • the decreased oil pressure acting through conduit 32 on the top of slide valve member 21, can be varied by adding to the control system a pressure control valve 37.
  • Pressure control valve 37 is connected through a line 38 to the top of capacity control valve housing 22, and through a line 39 to the bottom of said housing 22.
  • the present invention concerns the arrangement and construction of the pressure control valve 37 which serves to control the actuating pressure in the capacity control valve 20.
  • the details of the pressure control valve 37 as shown in FIG. 1 will hereinafter be explained with reference to FIG. 2.
  • a bellows 40 is confined in a bellows housing 41 and with its ends it is hermetically attached to an end plate 42 as well as to a bellows mandrel 43 which is displaceable in the housing, said mandrel extending with one end through the end plate 42 and an end wall 44 of the bellows housing 41.
  • the bellows mandrel 43 is maintained in position by means of helical springs 45 and 46, the former abutting against the end wall 44 and the latter against an adjustable stop 47, which is guided axially in the end of the bellows housing and can be adjusted from without.
  • the bellows housing 41 is rotatable in an outer housing 48 for a purpose to be subsequently explained.
  • a bore 49 is provided in the outer housing for the admission of a pipe or duct, not shown, which is in connection with the actuating pressure on the capacity control valve of the compressor, said pressure determining the number of compressor cylinders to be engaged.
  • the outer housing 48 is closed with a cover 50, wherein a nozzle 51 is provided so as to be in connection with the bore 49 and to open out in the edge of the cover, and a nozzle-closing plate 52 is placed over the edge of the cover.
  • a hood 53 fitted on the cover surrounds the nozzle-closing plate, said hood having an aperture 54 which is in connection with the suction side of the compressor, e.g. the crankcase.
  • the nozzle-closing plate 52 is substantially shaped as a disc, provided with a number of holes 55, and which in the embodiment shown in FIG. 2 at its center has a projection 56 attached thereto and protruding towards the bellows mandrel, said projection being axially and rotationally in fixed connection with the bellows mandrel 43 through a spindle 57 protruding inwardly into the mandrel, said spindle being secured in the bellows mandrel by means of e.g. a pointed screw.
  • the space in the bellows housing 41 surrounding the bellows 40 is connected with a source of pilot pressure, which is primarily the atmospheric pressure, when the pressure control valve herein described is used without a pilot pressure governor.
  • the degree of opening of the nozzle 51 is determined by the angular position of the projections 58 and 59 in relation to the nozzle 51.
  • the nozzle-closing plate 52 When, as shown in FIG. 1, the projections 58 and 59 lie in an axial plane containing the nozzle 51, the nozzle-closing plate 52 will, when moved to the left, take up an oblique position due to the fact that the attachment points on projection 56 of the springs and 61 will tend to follow curves in opposed direction. Thereby, the plate 52 will be rocked about an axis which is perpendicular to the plane of the drawing at a place diametrically opposite the nozzle and farther away from the projection 56 than is the nozzle.
  • the nozzle 51 will, for the same rocking of the nozzle-closing plate, be in a position opposite a point of the edge portion of the nozzle-closing plate which has a smaller distance from the nozzle, and thereby its degree of opening will have been reduced.
  • the nozzle-closing plate 52 is rotated together with the bellows housing 41 on account of the rotationally fixed connection through the projections and the leaf springs.
  • the pressure control valve may be altered as shown in FIG. 3 by omitting the leaf springs and making the nozzle-closing plate itself resilient, in which case the nozzle-closing plate is connected to the bellows housing at a point on its marginal edge portion, more particularly the point which in FIG. 1 is nearest to the projection 58.
  • corresponding parts have the same references as similar parts in FIG. 2.
  • the projections are omitted, and the nozzle-closing plate 64 has a point of its marginal portion secured at 65 to a protruding part 66 of the bellows housing 41.
  • the plate 64 is of elastic material.
  • the part 66 and the point 65 of the plate 64 is rotatable with the bellows housing 41 relative to the stationary nozzle 51 so that the degree of opening of the nozzle will be decreased when turning the plate away from the plane of the drawing.
  • the nozzle-closing plate needs not be rotatable at all in the case of resilient or elastic material.
  • the nozzle-closing plate 67 is secured at 68 to a cover 69 and has a portion 70 which is urged towards the bellows by means of a spring 71.
  • the nozzle-closing plate 67 is rotationally stationary in relation to the bellows.
  • the nozzle is adjustable in relation to the plate 67 by being formed in an arm 73 which is longitudinally adjustable towards and away from the engagement point 70 between bellows and nozzle-closing plate.
  • the arm 73 is bored and has an aperture 74 in its side wall for communication with a chamber 75 in connection with bore 49.
  • FIG. The alternative embodiment as shown in FIG. is similiar to that in FIG. 4 except that the nozzle arm 76 is swinga'ble about the axis of an adjustment spindle 77.
  • the degree of contraction of the bellows will be determined by the suction pressure in the interior of the bellows and the atmospheric pressure which is also present in the space defined by the housing 41 around the bellows.
  • a further regulation by means of the pressure control valve can be obtained by replacing the atmospheric pressure around the bellows by a pilot pressure which is controlled in a suitable manner, e.g. in dependence on the suction pressure in the compressor, i.e. corresponding to its load.
  • pilot pressure can suitably be provided by means of a pressure transmitter whose construction is identical with the pressure control valve herein described, only the connections being different.
  • FIG. 6 A first arrangement for this purpose is illustrated in FIG. 6, in which compressed air is used for the production of the pilot pressure.
  • the opening 63 in the pressure control valve 37 is connected to a compressed air pipe 78 which is also connected at 80 to the nozzle in a pressure transmitter 79 through a bore corresponding to bore 49 in the pressure control valve 37.
  • the aperture in the transmitter which corresponds to aperture 54 in valve 37, communicates with the atmosphere through a line 81, while the space surrounding the bellows in the pressure transmitter is connected through a line 82 to the suction side of the compressor.
  • a decreasing suction pressure Will keep the nozzleclosing plate in transmitter 79 closed, so that the pilot pressure at 80 rises.
  • the increasing pilot pressure is transmitted through opening 63 to the space surrounding the bellows in the pressure control valve 37 so that the bellows is compressed and the nozzle 51 is opened, thereby causing the capacity control valve 20 to unload one or more compressor cylinders until operational balance has been restored.
  • FIG. 7 An alternative method of controlling the pressure supplied to the capacity control valve 37 is illustrated in FIG. 7.
  • the varying demand for cold is made use of in a different way to adjust the actuating pressure at 63 of the capacity control valve 37.
  • a feeler 84 is disposed, and the varying temperature of the evaporator is transmitted through the capillary line 85 to a thermostatic valve 86 inserted in a conduit 87 leading to the capacity'control valve 37 from the pressure side of the compressor.
  • the pilot pressure in the capacity control valve 37 is supplied by gaseous coolant.
  • the gaseous coolant may also be utilized in a diflerent way as the source of pilot pressure in the capacity control valve.
  • the pressure transmitter is merely distinguished from FIG. 1 in that the nozzle-closing plate 52 opens in the opposite direction.
  • the coolant pressure is supplied through a conduit 89, as shown in FIG. 8, to serve as the pilot pressure at 63 for the capacity control valve 37, as well as at a nozzle 90 in the hood 91 of the pressure control transmitter 88.
  • the coolant will flow to the suction side of the compressor through the aperture 54 connected through a line 92 to the line 39 leading to the crankcase.
  • a multi-cylinder refrigeration compressor capacity control system which comprises an unloader mechanism for each compressor cylinder, a capacity control valve, conduit means connecting said capacity control valve to either of said unloader mechanisms, a crankcase in said compressor, passage means to communicate said crankcase with said capacity control valve, oil pressure supply means connected to said capacity control valve, a pressure control valve, conduit means connecting said pressure control valve to said capacity control valve and to said oil pressure supply means, passage means between said crankcase of the compressor and said pressure control valve, a bellows within said pressure control valve, a nozzle in said pressure control valve connected to said conduit means connecting said pressure control valve and said capacity control valve, said nozzle opening into the interior of said pressure control valve at a position in communication with the interior of said bellows, a discshaped nozzle-closing plate attached to said bellows for axial movement thereof in response to expansion and contraction of said bellows, spring means for biasing said bellows with said nozzle-closing plate in a direction for opening said nozzle against the action of said compressor crankcase pressure and of said
  • a capacity control system in which the center of said nozzle-closing plate is axially and rotationally movable with said bellows, and points on said plate spaced from the center thereof are non-rotationally connected through axially yielding spring means to a member rotatable with said bellows.
  • a capacity control system in which the center of said nozzle-closing plate is integrally attached to said bellows, said nozzle-closing plate being of resilient and springy material, and a point of said plate adjacent an edge thereof being attached to and rotatable with said bellows or a member rotatable with said bellows.
  • a capacity control system in which the nozzle-closing plate is resilient and elastic and is secured to a part of the pressure control valve casing at a point spaced from the point of engagement with the bellows whereby the nozzle-closing plate is capable of being inclined relative to the axial direction of the bellows upon axial expansion of the latter, a spring means being provided opposite said point of engagement to urge the nozzle-closing plate towards the bellows, a hollow nozzledefining arm being rotationally adjustable in a plane substantially at a right angle to the axial direction of said bellows about a point spaced from said point of engagement between said bellows and said nozzle-closing plate whereby upon rotation of said nozzle-defining arm the distance between the nozzle opening and said point of engagement can be adjusted.
  • nozzle-closing plate is resilient and elastic and is secured to a part of the pressure control valve casing at a point spaced from the point of engagement with said bellows whereby the nozzle-closing plate is capable of being inclined relative to the axial direction of the bellows upon axial expansion of the latter, a Spring means being provided opposite said point of engagement to urge the nozzle-closing plate towards said bellows, a hollow nozzledefining arm having a nozzle discharge opening facing said nozzle-closing plate at the same side thereof as is said bellows, said nozzle-defining arm being radially adjustable in a plane perpendicular to the longitudinal axis of said bellows.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Damping Devices (AREA)
  • Control Of Fluid Pressure (AREA)
US775788A 1967-11-16 1968-11-14 Refrigeration compressor capacity control system Expired - Lifetime US3552137A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DK573867A DK131647C (da) 1967-11-16 1967-11-16 Trykstyreventil til kolekompressorer

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US3552137A true US3552137A (en) 1971-01-05

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US775788A Expired - Lifetime US3552137A (en) 1967-11-16 1968-11-14 Refrigeration compressor capacity control system

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US (1) US3552137A (de)
CH (1) CH501173A (de)
DE (1) DE1808591A1 (de)
DK (1) DK131647C (de)
ES (1) ES360295A1 (de)
FR (1) FR1593212A (de)
GB (1) GB1248979A (de)
NL (1) NL145663B (de)
NO (1) NO122928B (de)
SE (1) SE338331B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4040259A (en) * 1972-12-15 1977-08-09 Phillips Petroleum Company Recovery of natural gas liquids by partial condensation
US4369633A (en) * 1981-09-03 1983-01-25 Snyder David A Multiple stage compressor with flash gas injection assembly
US4519750A (en) * 1982-12-20 1985-05-28 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable-delivery refrigerant compressor
US4951475A (en) * 1979-07-31 1990-08-28 Altech Controls Corp. Method and apparatus for controlling capacity of a multiple-stage cooling system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4040259A (en) * 1972-12-15 1977-08-09 Phillips Petroleum Company Recovery of natural gas liquids by partial condensation
US4951475A (en) * 1979-07-31 1990-08-28 Altech Controls Corp. Method and apparatus for controlling capacity of a multiple-stage cooling system
US4369633A (en) * 1981-09-03 1983-01-25 Snyder David A Multiple stage compressor with flash gas injection assembly
US4519750A (en) * 1982-12-20 1985-05-28 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable-delivery refrigerant compressor

Also Published As

Publication number Publication date
DE1808591A1 (de) 1969-08-07
ES360295A1 (es) 1970-10-16
DK131647B (da) 1975-08-11
CH501173A (de) 1970-12-31
DK131647C (da) 1976-01-12
SE338331B (de) 1971-09-06
NO122928B (de) 1971-09-06
GB1248979A (en) 1971-10-06
NL145663B (nl) 1975-04-15
NL6816297A (de) 1969-05-20
FR1593212A (de) 1970-05-25

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