US3184151A - Compressor capacity control - Google Patents

Compressor capacity control Download PDF

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Publication number
US3184151A
US3184151A US198854A US19885462A US3184151A US 3184151 A US3184151 A US 3184151A US 198854 A US198854 A US 198854A US 19885462 A US19885462 A US 19885462A US 3184151 A US3184151 A US 3184151A
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United States
Prior art keywords
pressure
valve
suction
compressor
discharge
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Expired - Lifetime
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US198854A
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English (en)
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David N Shaw
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Carrier Corp
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Carrier Corp
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Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Priority to US198854A priority Critical patent/US3184151A/en
Priority to GB16827/63A priority patent/GB983030A/en
Priority to CH638863A priority patent/CH404063A/de
Priority to SE06073/63A priority patent/SE329232B/xx
Application granted granted Critical
Publication of US3184151A publication Critical patent/US3184151A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • 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
    • F04B49/022—Stopping, starting, unloading or idling control by means of pressure
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2612—Common sensor for both bypass or relief valve and other branch valve

Definitions

  • This invention relates to a fluid compressor and to a method of controlling the capacity of the compressor, more particularly, to a refrigerant compressor having improved mechanism for controlling the capacity of the compressor and for reducing the cycling of the compressor during load fluctuations and to a method by which the capacity of a reciprocating compressor may be controlled responsive to pressure differences.
  • the load on the system in which the compressor is arranged may sometimes vary resulting in ineflicient operation of the compressor unless the capacity of the compressor can be varied to comply with the system variations.
  • One of the methods for varying the capacity of a reciprocating compressor operating at constant speed is to provide means for bypassing some or all of the cylinder entrapped vapor back to the suction side of the compressor from some point in the cylinder or the discharge manifold.
  • a variable capacity has been achieved by bypassing the full discharge of certain of the cylinders back to the suction side of the compressor.
  • one pair of cylinders may be manifolded together and arranged to deliver to the discharge side of the compressor at all times.
  • the other pair of cylinders is manifolded together and arranged to discharge to the suction side of the compressor or to the discharge side of the compressor according to the load. Suitable controls responsive to the load imposed on the compressor are normally employed.
  • a capacity reduction of fifty percent is possible with a four cylinder compressor when one pair of cylinders is unloaded.
  • the discharge of only one pair of cylinders may be directed to the suction side of the compressor to eiiectuate a one-third reduction in capacity or two pairs of cylinders may be directed to the suction side of the compressor to effectuate a two-thirds reduction in capacity.
  • present capacity control arrangements generally do not provide one hundred percent capacity when the compressor is fully loaded, as is desired. Further, there was a desire to replace the two-way and three-way solenoid valves often used in present bypass capacity control arrangements with a simpler, less expensive control arrangement.
  • An object of the present invention is to provide a refrigerant compressor having an improved capacity control in which the disadvantages and deficiencies of prior constructions are obviated.
  • Another object of the present invention is an improved method of controlling a multi-cylinder compressor by loading and unloading one or more cylinders in response to changes in load demand on the compressor whereby the capacity of the compressor is adjusted to meet changes in compressor load.
  • Another object of the present invention is to provide a compact, improved cylinder bypass type capacity con- 3,l8d,l5l Patented May 18, 1965 trol arrangement for unloading one or more cylinders of a refrigerant compressor.
  • a further object of the present invention is to provide a cylinder bypass type capacity control arrangement including a discharge side bleed arrangement responsive to compressor load to effectuate capacity control.
  • a still further object of this invention is to provide an apparatus for capacity control of a fluid compressor that is compact, less expensive and more reliable than present controls.
  • This invention relates to a reciprocating compressor comprising a first cylinder, a second cylinder, at discharge manifold, the first cylinder being in communication with the discharge manifold, a first path placing the second cylinder in fluid flow communication with the discharge manifold, a second path of fluid flow between the discharge port of the second cylinder and the suction manifold of the second cylinder, pressure actuated means for opening and closing the second path, a third path of fluid flow between the discharge manifold and the suction manifold of the second cylinder, a portion of the third path communicating with said pressure actuated opening and closing means, and means responsive to load conditions to vary the fluid pressure in the third path whereby an increase in load increases fluid pressure in the third path to close the second path and a decrease in load decreases fluid pressure in the third path to open the second path.
  • This invention further relates to a method of unloading a cylinder of a reciprocating compressor, in which the steps consist in placing the discharge and suction sides of the cylinder in communication to thereby unload the cylinder in response to a predetermined first discharge pressure, increasing the predetermined first discharge pressure in response to a predetermined first suction pressure, preventing communication between the dis charge and suction sides of the cylinder to load the cylinder at a second predetermined discharge pressure, and changing the second predetermined discharge pressure to the predetermined first discharge pressure in response to a predetermined second suction pressure whereby the discharge and suction sides of the cylinder are placed in communication to unload the cylinder.
  • FIGURE 1 is a cross-sectional view of a four cylinder compressor including the apparatus of the present invention
  • FIGURE 2 is a view partly in section and partly in elevation of a portion of a compressor including the apparatus of the present invention, the components of the capacity control being shown in the unloaded condition;
  • FIGURE 3 is a view partly in section and partly in elevation of'a portion of the compressor including the apparatus of the present invention, the components of the capacity control being shown in the loaded condition;
  • FIGURE 4 is an enlarged view of a modified control valve arrangement.
  • the compressor 10 is a four-cylinder compressor having cylinder banks 3 and a. Each of the cylinder banks 3 and 4 includes a pair of cylinders 11 .discharged from the respective cylinders.
  • a suction manifold 22 is provided for introducing low pressure gas into the respective cylinders.
  • a discharge manifold 23 is provided for receiving the pressurized gas Discharge manifold 23 is provided with an outlet 7
  • cylinder bank 3 is provided with a discharge manifold check valve 24 to be more fully described hereinafter.
  • Cylinder bank 3 is also provided with a capacity control 40 of the present invention to be more fully described hereinafter.
  • compressor 10 is shown as a four cylinder compressor having two banks of paired cylinders 3 and 4, it is understood that additional cylinder banks may be provided, some or all of which may be provided with capacity controls.
  • additional cylinder banks may be provided, some or all of which may be provided with capacity controls.
  • a six-cylinder compressor having three banks of paired cylinders may be envisioned wherein two of the three pairs of cylinders may be capacity controls constructed according to the presentinvention. In this manner, a one-third and a two-thirds reduction in capacity of the six cylinder compressor may be effected.
  • the cylinder 11 includes a cylinder head 12 secured to the compressor 10 by bolts 13.
  • the piston 14 is disposed within the cylinder 11 and moves therein.
  • a valve plate 15 is placed between the cylinder head 12 and the compressor 19. Cylinder head gasket 17 and valve plate gasket 16 are disposed on opposite sides of valve plate 15 to prevent the escape of pressure from within the compressor.
  • the cylinder communicates with the cylinder head through the discharge port 18 and suction port 19 in the valve plate 15.
  • a discharge valve 20 and a suction valve 21 Affixed to the valve plate are a discharge valve 20 and a suction valve 21.
  • gases are drawn into the cylinder through the suction. port 19 and chamber 32 from the suction manifold 22.
  • the discharge stroke the compressed gas is forced into the discharge chamber 29 through the discharge port 18.
  • the cylinder discharge pres-sure will force open the discharge piston check valve 24 to permit the passage of the refrigerant gas into the discharge manifol-d 23.
  • Check valve 24 is urged toward closed position by spring 26 disposed between valve 24 and support 25.
  • a partition means 27 which divides the head into a discharge chamber 29 and a suction chamber 30.
  • the chambers 29 and can 'be considered to be merely extensions of the discharge manifold and the suction manifold, respectively.
  • valve 55 is provided with surface 59 adapted to engage valve seat 57 to thereby seal reduced valve chamber 47 from enlarged valve chamber 46.
  • a valve spring 58 urges valve 55 toward valve seat 57.
  • Guide 36 is attached to the lower end of control body 45 and delimits the end of enlarged valve chamber 46.
  • ' Guide 36 is provided with a central bore 48 communicatmeans 27 includes a wall 28 having an opening 33 to place the chambers 29 and 30 in communication with one another and a Wall 31 defining the chamber 32.
  • Chamber 32 is placed in communication with suction manifold 22 ta-ining ring 37 secured to piston 34 and the other end engages retaining lip 38 of the guide 3 6.
  • valve piston 34 is urged by spring 35 toward an open, that is, cylinder unloaded position.
  • a control assembly 40 is provided to load the cylinder a control assembly 40.
  • the body '45 of the control assembly 41) to secured to the cylinder head 12 by suitable means, such as bolts 41.
  • Control assembly gasket 42 is provided between the cylinder head 12 and the control assembly body 45 to prevent the leakage of the gases from the compressor.
  • Control assembly 41 ⁇ consists of a control body 45 having an enlarged valve. chamber ed and a reduced valve 'trol assembly body 45. One end of spring 35; abuts re- 7 ing enlarged valve chamber 46 with piston chamber 39.
  • a bleed passage 51 communicates enlarged valve chamber .6 with discharge passage 52.
  • Cylinder head passage 53 communicates discharge passage 52 with discharge manifold 23.
  • interconnecting suction manifold passages 49 and 51) in the cylinder head 12 and the control assembly body 45 respectively communicate reduced valve chamber 47 with the suction manifold 3%.
  • a diaphragm assembly is attached to the outer end of the control body 45 by suitable means such as threads 76.
  • Diaphragm assembly 65 includes diaphragm 66 abutting the end of valve stem 56.
  • a spring 67 acting through diaphragm 66 and valve stem 56, urges valve 55 in an open, that is, cylinder unloaded position. Spring '67 is capable of overriding valve spring 58.
  • Screw 68 is provided for the purpose of adjusting the bias of spring 67.
  • a diaphragm chamber 69 is provided in control body 45. Restricted orifice 7t) communicates diaphragm chamber 69 with suction manifold passage 51).
  • valve stem 55 is provided with two recesses 72 in the outer circumference thereof corresponding to open and closed positions respectively of valve 55.
  • Ball 71 located in control body 45, is adapted to cooperate with one or the other of the recesses 72 to releasably maintain valve 55 in open or closed position.
  • Spring 73 urges ball 71 into engagement with one or the other of recesses 72.
  • Screw 74 is provided to adjust the bias of spring 73. While the detent means has been shown as cooperating with valve stem 55, it is understood that the detent means may be provided on the valve 55 itself.
  • check valve 24 When the cylinder is loaded, that is, opening 33 is closed by control piston 34, the discharge pressurecf the loaded cylinder forces check valve 24 open to discharge pressurized gas into the'manifold 23. At all others times, check valve 24- is closed.
  • the purpose of check valve 24- is to prevent pressurized gas in discharge manifold 23 from flowing into the suction manifold 3% while permitting the pressurized gas obtained from the cylinder during the loaded condition thereof to discharge into thedischarge manifold 23.
  • Diaphragm chamber 69 communicating with suction manifold 39 via passages 4?, 5i) and 7t? reflects a similar pressure increase.
  • the increase of pressure in chamber 69 moves diaphragm (:5 against spring 67 whereby valve 55, under the influence of valve spring 5%, moves toward closed position.
  • the increase in suction manifold pressure required to overcome spring 67 may be varied by adjustment of screw 63.
  • valve 55 moves toward closed position, the rate of bleed of discharge gas into the suction manifold passage 59 through bleed passage 51 decreases thereby resulting in an increase in pressure in enlarged valve chamber 46, passage 48, and piston chamber 34. It is understood that the position of valve 55 controls the rate of bleed, the rate of bleed decreasing as valve 55 moves toward closed position.
  • valve 55 The increased pressure in enlarged valve chamber d6, acting on the lower surface of valve 55, speeds up closing movement of valve 55. As valve 55 closes, the rate of bleed is correspondingly reduced. The pressure accordingly builds up in areas 46, 48 and 39. As valve 55 approaches closed position, the increased pressure in areas 46, 48 and 39 moves control piston 34- against the urging of spring 35' to close bypass 33 thereby loading the cylinder. Surface 59 of valve 55 contact surface 57 of control body 45 thereby sealing enlarged valve chamber as from reduced valve chamber 47. Upon the closing by valve 55 of the bleed communication between the discharge manifold 23 and the suction manifold 38, the pressure in areas 46, and 39 equalizes with that of the discharge manifold 23.
  • a decrease in load is evidenced by a decrease in pressure in suction manifold 39.
  • Diaphragm chamber 69 communicating with the suction manifold 30 by means of interconnecting passages 49, 5t and 7t reflects a similar decrease.
  • the diaphragm 66 in response to this decrease, moves valve 55 open upon a predetermined pressure drop.
  • valve 55 opens, pressurized gas in areas as, 43 and 39 is bled around valve 55 through reduced valve chamber 47 into the suction passage 50.
  • the rate of bleed is rapid due to the pressure dirrerential between valve chambers 46 and 47, and due to the large elfective area of the port of the reduced valve chamber 47.
  • valve 55 the pressure in enlarged valve chamber 46 rapidly decreases, this decrease speeding up opening movement of valve 55.
  • the speeded up opening movement of valve 55 causes rapid pressure drop in chambers as, 48 and 39 whereupon control piston 34, under the urging of spring 35, moves to open bypass 33 thereby unloading the cylinder.
  • diaphragm 66 abuts the upper surface of control body 45, which serves as a stop therefor. Further opening movement of valve 55 is restrained by valve spring 58. With the establishment of equilibrium reduced pressure is maintained in chamber 39 whereby control piston 34 is held in retracted position.
  • Orifice '75 communicating diaphragm chamber 69 with suction manifold passage 5% serves to prevent any rapid surge of pressure, such as occurs during opening movement of valve 55, from affecting diaphragm 66.
  • the high pressure in areas 46, 43 and 3h bleeds around valve 55 into reduced valve chamber area 47 into suction passage Sit. This bleeding is rapid, resulting in a surge of pressure in suction passage 50.
  • the restricted size of orifice 7t) effectively prevents this pressure surge from aiiecting diaphragm 66.
  • FIG. 4 The operation of the embodiment shown in FIGURE 4 is the same as disclosed in connection with FIGURES l3.
  • control valve 55 With the control valve 55 open, as shown in FIG- URE 4, an increase in load on the compressor is reflected by an increase in pressure in suction manifold 36, passages 49, 50 and '70, and diaphragm chamber 69.
  • This increased pressure moves diaphragm 66 against spring 67 permitting control spring 58 to overcome the detent effected by cooperating ball 71 and recess 72 to move control valve 55 toward closed position.
  • control valve 55 closed a decrease in load is reflected by a decrease in pressure in suction manifold 3i passages 49, S9 and 7t and diaphragm 69.
  • This decreased pressure moves diaphragm 6d against valve stem 56 to overcome the detent eliected by cooperating ball 71 and recess 72 to open control valve 55 to unload the compressor.
  • the pressure required to load and unload the compressor is influenced by the adjustment of spring 6'7 through screw 68 and by the adjustment of detent spring '73 through screw 74.
  • a reciprocating compressor the combination of a cylinder including a movable piston therein, a suction manifold, a discharge manifold, a cylinder head for the compressor, said cylinder head including a partition separating a discharge chamber from a suction chamber, aid partition having an opening therein, normally open pressure actuated means for closing said partition opening, a bleed passage communicating said discharge manifold with said pressure actuated means and said suction manifold, means for controlling the pressure in said bleed passage including means to regulate flow through said bleed passage, and means responsive to changes in suction manifold pressure to actuate said flow regulating means to control pressure in said bleed passage including a pressure powered operator engageable with said flow regulating means, whereby upon a predetermined increase in suction pressure said operator actuates said flow regulating means to decrease flow through said bleed passage so that said pressure actuated means closes said partition opening to load said compressor, and upon a predetermined decrease in suction pressure said operator act-uates said how regulating means to increase flow through
  • Apparatus according to claim 1 including detent means to releasably retain said flow regulating means in flow increasing and decreasing positions.
  • a reciprocating compressor the combination of a cylinder including a movable piston therein, a suction manifold, a discharge manifold, a cylinder head for the compressor, said cylinder head including a partition separating a di charge chamber from a uction chamber, said partition having an opening therein, pressure actuated means comprising a piston for closing said partition opening, means biasing said piston to open aid partition opening, a bleed passage communicating said discharge manifold with said pressure actuated means and said suction manifold, means for controlling the pressure in said bleed passage including a control valve adapted to regulate flow through said bleed passage, and means responsive to a predetermined change in suction manifold pressure to effect movement of said control valve including a pressure act-u- 7 ated operato-r engageable with said control valve and an orifice communicating said pressure actuated operator wit-h said suction manifold whereby, upon a predetermined increase in suction pressure, said pressure actuated operator moves said control valve to decrease flow through said
  • Apparatus according to claim 3 including means for maintaining said control valve in open or closed position.
  • said maintaining means includes detent means comprising at least one recess in said control valve corresponding to control valve increased or decreased regulating position, and an adjustable spring biased ball means cooperating with said recess to releasably maintain said control valve in position.
  • a reciprocating compressor having a cylinder including a movable piston therein, a suction manifold, a cylinder head, a discharge manifold, a
  • partition in said cylinder head including an opening for communicating said discharge manifold with said suction manifold whereby said cylinder is unloaded, means responsive to discharge pressure for closing said opening, means for controlling the pressure imposed on said closing means including a restricted passage communicating said discharge manifold with said discharge pressure responsive closing means and said suction manifold whereby said discharge pressure at said discharge pressure responsive closing means is reduced, control valve means in said passage, pres-sure actuated means including a restricted orifice engageable with said control valve means and responsive to a predetermined increase in suction pressure to move said control valve means toward a closing posi tion to apply discharge pressure to said closing means whereby 'said partition opening is closed to load said cylinder.
  • a reciprocating compressor having a cylinder including a movable piston therein, a uction manifold, a cylinder head, a discharge manifold, a partition in said cylinder head including an opening for communicating said discharge manifold with said suction manifold whereby said cylinder is unloaded, pressure actuated'reciprocating piston means adapted to selectively close said opening, said piston means being biased toward open position and including a pressure chamber, a first restricted passage communicating said discharge manifold with said pressure chamber whereby said discharge pressure is applied to said pressure chamber, said discharge pressure being sufiicient to move said piston means against said bias'to close said opening to load said cylinder, and means for reducing said dischargepressure'in said pressure chamber including a second passage communicating said suction manifold and said pressure chamber whereby said discharge pressure i reduced to permit said piston'rneans to open said opening and unload said cylinder, valve means for controlling flow through said second passage, and diaphragm means including a restricted orifice, said dia
  • a reciprocating compressor the'combination of a'cylinder having a movable piston therein, a'suction chamber communicating with the cylinder, a discharge chamber communicating withtthe cylinder, means for" placing the suction chamber in communication with the discharge chamber to unload the cylinder, meansfor clos- 7 ing said communication means including a member movable in one direction responsive to discharge pressure and yieldable means for moving said member in the opposite direction and means for controlling movement of said member, said control means including a first passage through which discharge pressure is applied against said movable member, 'a bypass passage communicating with the first passage and the suction manifold, and means for preventing communication between the first passage and the bypass passage, said communication preventing means including a closure and a pressure responsive member to move said closure in one direction, a pressure chamber adjacent said pressure responsive member, a restricted passage placing the chamber in communication with the bypass passage whereby pressure in the bypass passage is reflected in the chamber, and yieldable means opposing the pressure applied against the pressure responsive member.
  • a reciprocating compressor the combination of a first cylinder having a movable piston therein, a second cylinder having a movable piston therein, a suction manifold communicating with said first and second cylinders, a first discharge manifold communicating with said first cylinder, a second discharge manifold communicating with said second cylinder and aid first discharge manifold, closure means for closing said second discharge manifold in response to a first discharge manifold pressure less than said second discharge manifold pressure, first means for placing the suction manifold in communication With said first discharge manifold whereby said first cylinder is unloaded, second means for preventing communication between the suction manifold and the first discharge manifold, said second means including a member movable in one direction in response to discharge pressure, yieldable means for moving said movable member in the opposite direction, and means for controlling movement'of said member, said movement controlling means including a first passage communicating with the second discharge manifold through which discharge pressure is applied against said movable member, a second passage communicating with the
  • a reciprocating compressor the combination of a cylinder including a movable piston therein, a suction manifold, a discharge manifold, a cylinder head for the compressor, said cylinder head including a partition ep arating a discharge chamber from a suction chamber, said partition having an opening therein, pressure actuated means comprising a piston for closing aid partition opening, means biasing said piston to open said partition opening, a bleed passage communicating said discharge manifold with said pressure actuated means and said suction manifold, means for controlling the pressure in said bleed passage including a control valve adapted to regulate flow through said bleed passage, and means including a restricted orifice responsive to a predetermined change in suction manifold pressure to effect movement of said control valve whereby, upon a predetermined increase in suction pressure, said moving means actuates said control valve to decrease flow through said bleed passage toactuate said piston to close said partition opening to load aid compressor and, upon' a predetermined decrease in suction pressure, said moving means actuates

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US198854A 1962-05-31 1962-05-31 Compressor capacity control Expired - Lifetime US3184151A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US198854A US3184151A (en) 1962-05-31 1962-05-31 Compressor capacity control
GB16827/63A GB983030A (en) 1962-05-31 1963-04-29 Compressor capacity control
CH638863A CH404063A (de) 1962-05-31 1963-05-22 Verfahren zum Entlasten und Belasten eines Zylinders eines Kolbenkompressors und Kolbenkompressor zur Durchführung des Verfahrens
SE06073/63A SE329232B (de) 1962-05-31 1963-05-31

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US198854A US3184151A (en) 1962-05-31 1962-05-31 Compressor capacity control

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US3184151A true US3184151A (en) 1965-05-18

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CH (1) CH404063A (de)
GB (1) GB983030A (de)
SE (1) SE329232B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3360186A (en) * 1965-09-27 1967-12-26 Carrier Corp Compressor capacity control
US3361068A (en) * 1966-08-18 1968-01-02 Allis Chalmers Mfg Co Double hydraulic pump with built-in unloading valve
US3385508A (en) * 1964-03-25 1968-05-28 Carrier Corp Compressor capacity control
US20220154707A1 (en) * 2019-03-15 2022-05-19 Zf Cv Systems Europe Bv Electric vacuum pump for braking system on passenger cars with v-twin piston arrangement
EP4276311A2 (de) * 2016-10-07 2023-11-15 BITZER Kühlmaschinenbau GmbH Halbhermetischer kältemittelverdichter

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2522762A (en) * 1947-11-15 1950-09-19 Chrysler Corp Compressor unloading mechanism
US2673025A (en) * 1949-11-14 1954-03-23 Trane Co Compressor unloading means
US2715992A (en) * 1951-06-26 1955-08-23 Robert W Wilson Compressor unloader
US3021790A (en) * 1958-05-23 1962-02-20 Blackmer Pump Company Pump delivery control mechanism
US3119550A (en) * 1961-02-09 1964-01-28 Carrier Corp Compressor capacity control

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2522762A (en) * 1947-11-15 1950-09-19 Chrysler Corp Compressor unloading mechanism
US2673025A (en) * 1949-11-14 1954-03-23 Trane Co Compressor unloading means
US2715992A (en) * 1951-06-26 1955-08-23 Robert W Wilson Compressor unloader
US3021790A (en) * 1958-05-23 1962-02-20 Blackmer Pump Company Pump delivery control mechanism
US3119550A (en) * 1961-02-09 1964-01-28 Carrier Corp Compressor capacity control

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3385508A (en) * 1964-03-25 1968-05-28 Carrier Corp Compressor capacity control
US3360186A (en) * 1965-09-27 1967-12-26 Carrier Corp Compressor capacity control
US3361068A (en) * 1966-08-18 1968-01-02 Allis Chalmers Mfg Co Double hydraulic pump with built-in unloading valve
EP4276311A2 (de) * 2016-10-07 2023-11-15 BITZER Kühlmaschinenbau GmbH Halbhermetischer kältemittelverdichter
US20220154707A1 (en) * 2019-03-15 2022-05-19 Zf Cv Systems Europe Bv Electric vacuum pump for braking system on passenger cars with v-twin piston arrangement

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Publication number Publication date
GB983030A (en) 1965-02-10
SE329232B (de) 1970-10-05
CH404063A (de) 1965-12-15

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