WO2014106233A1 - Commande de compresseur pour défaillance de rotation inverse - Google Patents

Commande de compresseur pour défaillance de rotation inverse Download PDF

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Publication number
WO2014106233A1
WO2014106233A1 PCT/US2013/078438 US2013078438W WO2014106233A1 WO 2014106233 A1 WO2014106233 A1 WO 2014106233A1 US 2013078438 W US2013078438 W US 2013078438W WO 2014106233 A1 WO2014106233 A1 WO 2014106233A1
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WO
WIPO (PCT)
Prior art keywords
scroll
compressor
controller
scroll compressor
valve
Prior art date
Application number
PCT/US2013/078438
Other languages
English (en)
Inventor
Ryan J. DOTZENROD
YoungChan Ma
Cody A. KLEINBOEHL
Original Assignee
Thermo King Corporation
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 Thermo King Corporation filed Critical Thermo King Corporation
Publication of WO2014106233A1 publication Critical patent/WO2014106233A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/70—Safety, emergency conditions or requirements
    • F04C2270/72—Safety, emergency conditions or requirements preventing reverse rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/80—Diagnostics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/86—Detection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • the disclosure herein relates to a transport refrigeration unit (TRU). More specifically, the disclosure herein relates to control of a compressor to avoid reverse rotation failure, where the compressor may be a scroll compressor, and where the scroll compressor may be used in a TRU.
  • TRU transport refrigeration unit
  • a transport refrigeration system which has a transport refrigeration unit (TRU) is generally used to control an environmental condition (e.g., temperature, humidity, air quality, and the like) within a refrigerated transport unit (e.g., a container on a flat car, an intermodal container, etc.), a truck, a box car, or other similar transport unit (generally referred to as a "refrigerated transport unit").
  • the TRU can be configured to include a compressor, a condenser, an expansion valve and an evaporator, which form a refrigeration circuit. TRUs can experience component failure, such as with the compressor, and such ongoing issues continue to be studied.
  • a compressor of a TRU may experience risks or actual occurrences of reverse rotation, which can lead to compressor internal failure.
  • Reverse rotation in a compressor may occur due to a high discharge back pressure during compressor shutdown.
  • Reverse rotation is usually not desirable, as some compressors, such as some scroll compressors, may not be serviceable and would therefore need to be replaced upon such failure that may result from reverse rotation.
  • Embodiments and descriptions herein are to systems, methods, and components, such as in a compressor, which are designed to protect the compressor, such as a scroll compressor, when reverse rotation occurs and/or to avoid or at least reduce reverse rotation.
  • a valve is activated before shutdown to allow relatively high discharge back pressure to travel through a path into the suction chamber and not the compression chamber.
  • Leak path or leak paths may be employed to allow the relatively high discharge back pressure to travel into the suction chamber.
  • the leak path(s) may be employed components of the compressor, such as on the scroll set, for example on the non-orbiting scroll (e.g. fixed scroll) and/or the orbiting scroll.
  • the leak path(s) are in fluid communication with the path to the suction chamber, where the valve is controlled to open or close the path to the suction chamber.
  • a refrigeration system can employ the valve and leak path(s) to address reverse rotation in the compressor. It will be appreciated that the valve may be controlled by a unit controller of the system to activate and deactivate the valve as necessary.
  • the refrigeration system is a TRU.
  • a compressor can include appropriate suction and discharge componentry to allow for the use of the valve and leak path(s) to address reverse rotation in the compressor.
  • the compressor is a scroll compressor.
  • a method to protect a compressor from reverse rotation includes activating a valve. Activating the valve allows releasing of relatively high discharge pressure present in the scroll set to travel into a suction chamber and into the compression chamber. Releasing the relatively high discharge pressure into the suction chamber allows for unloading of the compressor, such as the scroll sets, including the orbiting and non- orbiting scroll, which can then be safely shutdown.
  • the method includes shutting down the compressor.
  • Fig. 1 illustrates an embodiment of a transport unit, with which embodiments disclosed herein can be practiced.
  • Fig. 2 illustrates a schematic diagram of a scroll compressor that may employed in a
  • Fig. 3 illustrates a flow chart of a method of controlling a valve, according to one embodiment.
  • Fig. 4 illustrates a graph showing a result of complication in a scroll compressor or failure due to the absence of the valve control.
  • Fig. 5 illustrates a graph of a scroll compressor operation in the presence of the valve control operation.
  • Fig. 6 illustrates a schematic diagram of a scroll compressor that may be employed in a TRU and showing an example of a valve employing digital control.
  • a transport refrigeration system which has a transport refrigeration unit (TRU) is generally used to control an environmental condition (e.g., temperature, humidity, air quality, and the like) within a refrigerated transport unit (e.g., a container on a flat car, an intermodal container, etc.), a truck, a box car, or other similar transport unit (generally referred to as a "refrigerated transport unit").
  • a refrigerated transport unit e.g., a container on a flat car, an intermodal container, etc.
  • a truck a box car, or other similar transport unit
  • Some TRUs may include a compressor, a condenser, an expansion valve and an evaporator, forming a refrigerant circuit. In operation, the compressor compresses refrigerant and drives the refrigerant through the refrigerant circuit.
  • Embodiments and descriptions herein are to systems, methods, and components, such as in a compressor, which are designed to protect the compressor, such as damage to a scroll set of a scroll compressor, from internal failures such as when reverse rotation occurs and/or to avoid or at least reduce reverse rotation.
  • a valve is activated before shutdown to allow relatively high discharge back pressure to travel through a path into the suction chamber and not the compression chamber.
  • Leak path or leak paths may be employed to allow the relatively high discharge back pressure to travel into the suction chamber.
  • the leak path(s) may be employed at/on components of the compressor, such as on the scroll set, for example on the non-orbiting and/or orbiting scroll.
  • the leak path(s) are in fluid communication with the path to the suction chamber, where the valve is controlled to open or close the path to the suction chamber.
  • a TRU is one type of refrigeration system that can employ the valve and leak path(s).
  • the compressor such as in a TRU,
  • the compressor can include appropriate suction and discharge componentry to allow for the use of the valve and leak path(s) to address reverse rotation in the compressor.
  • the compressor is a scroll compressor.
  • the scroll compressor can be, for example, a 25 Hp or less scroll unit, or in some examples about up to 30 Hp and/or up to 35 Hp. It will be appreciated that the specific scroll compressor is meant to be merely exemplary and non- limiting.
  • scroll compressors are described in the following descriptions, it will be appreciated that the embodiments, aspects, and concepts described herein may apply to compressors other than scroll compressors, for example, reciprocating, screw, positive displacement, centrifugal, or other suitable types of compressors where there is a need to avoid reverse rotation of compressor parts.
  • Fig. 1 illustrates a transport unit 100, with which the embodiments disclosed herein can be used.
  • the transport unit 100 (for example a trailer unit) is configured to be transported by a tractor unit 110.
  • a TRU 120 is configured to be attached to an end wall 102 of the transport unit 100.
  • the TRU 120 is configured to regulate a space temperature of an internal space 104 of the transport unit 100.
  • a refrigerated transport unit e.g., a container on a flat car, an intermodal container, etc.
  • a truck e.g., a box car, or other similar transport unit (generally referred to as a "refrigerated transport unit").
  • Fig. 2 illustrates a schematic diagram of a scroll compressor that may be employed in a
  • compressor 10 is shown as a horizontal scroll compressor, but it will be appreciated that the concepts herein may be implemented in scroll compressors in other orientations, and/or having one or more stages of compression. It will be appreciated that the compressor 10 can be a fixed drive compressor or an open drive compressor. It will also be appreciated that the compressor can be driven by an engine directly or by an electric motor (e.g. where the motor is in the compressor, or as a standby compressor motor, etc.).
  • the compressor 10 includes features of oil management having its oil passage system as well as axial displacement capability of the scroll set. It will be appreciated that the concepts herein can be applied to scroll compressors that may not include the oil passage system of Fig. 2 and/or the axial displacement of Fig. 2. It will be appreciated that the compressor 10 is merely exemplary such as for purposes of describing the valve and leak path features. The valve and leak path features are described below following the general description of the particular compressor 10.
  • compressor 10 may include a compressor housing assembly 12, a main bearing housing assembly 14, a drive shaft assembly 16, a compression mechanism 18, a retaining assembly 20, a seal assembly 22, a discharge valve assembly 24, an oil separator 26, and an oil feed mechanism 28.
  • Housing assembly 12 may include a cylindrical hermetic shell 30, an end cap 32, a transversely extending partition 34, a base assembly 36, a suction gas inlet fitting 38, and a refrigerant discharge fitting 40.
  • Cylindrical hermetic shell 30 may include an opening 42 having suction gas inlet fitting 38 attached thereto.
  • End cap 32 and transversely extending partition 34 may generally define a discharge chamber 44. More specifically, transversely extending partition 34 may be fixed to a first end of shell 30 and end cap 32 may be fixed to transversely extending partition 34.
  • End cap 32 may include an opening 46 having refrigerant discharge fitting 40 fixed thereto.
  • Partition 34 may include an opening 48 to provide fluid communication between compression mechanism 18 and discharge chamber 44.
  • Discharge chamber 44 may generally form a discharge muffler for compressor 10. However, while compressor 10 is shown including discharge chamber 44, it is understood that the present teachings apply equally to direct discharge configurations.
  • Base assembly 36 may be fixed to shell 30 at an end generally opposite partition 34.
  • Base assembly 36 may include a base member 50, a bearing assembly 52, a seal housing 54, and a seal assembly 56.
  • Base member 50 may include a central opening 58 including first and second portions 60, 62 and a radially inwardly extending protrusion 64 disposed
  • Bearing assembly 52 may be located in first portion 60 of opening 58 and may include a ball bearing assembly.
  • Seal housing 54 may be located in second portion 62 of opening 58 and may be fixed to base member 50.
  • Seal assembly 56 may be located within seal housing 54 and may include a shaft seal 66.
  • Main bearing housing assembly 14 may include a main bearing housing 68 and a thrust member 70.
  • Main bearing housing 68 may be press fit into shell 30 and may abut a step 72 therein to locate main bearing housing 68 within shell 30.
  • Main bearing housing 68 may define a central bore 74, having a bearing 76 disposed therein.
  • An oil passage 78 may extend radially inwardly through main bearing housing 68.
  • a corresponding opening 80 may extend through bearing 76 to provide fluid communication between oil passage 78 and an interior portion of bearing 76.
  • Thrust member 70 may be fixed to an end of main bearing housing 68 and may form an annular flat thrust bearing surface 82 for engagement with compression mechanism 18, as discussed below. More specifically, fasteners 84 may extend through thrust member 70 and main bearing housing 68 to couple thrust member 70 thereto.
  • Drive shaft assembly 16 may include a drive shaft 86, a first counterweight 88 and a second counterweight 90.
  • Drive shaft 86 may include first and second ends 92, 94 and first and second journal portions 96, 98 disposed therebetween.
  • First end 92 may include an eccentric crank pin 200 having a flat 202 thereon.
  • Second end 94 may extend axially past base assembly 36 and may be disposed external to housing assembly 12.
  • a drive mechanism (not shown) may engage second end 94 to power rotation of drive shaft 86.
  • First and second journal portions 96, 98 may be rotatably disposed within bearing 76 and bearing assembly 52, respectively.
  • Shaft seal 66 may be sealingly engaged with drive shaft 86 at a location between second end 94 and second journal portion 98 to prevent leakage of oil from housing assembly 12.
  • First counterweight 88 may be fixed to drive shaft 86 at a location between first end 92 and first journal portion 96 and second counterweight 90 may be fixed to drive shaft 86 at a location between first journal portion 96 and second journal portion 98.
  • Compression mechanism 18 may include an orbiting scroll 204 and a non-orbiting scroll 106.
  • Orbiting scroll 204 may include an end plate 108 having a spiral vane or wrap 210 on the upper surface thereof and an annular flat thrust surface 112 on the lower surface. Thrust surface 112 may interface with thrust bearing surface 82 on main bearing housing 68.
  • a cylindrical hub 114 may project downwardly from thrust surface 112 and may have a drive bushing 116 rotatably disposed therein.
  • Drive bushing 116 may include an inner bore in which crank pin 200 is drivingly disposed.
  • Crank pin flat 202 may drivingly engage a flat surface in a portion of the inner bore of drive bushing 116 to provide a radially compliant driving arrangement.
  • Non-orbiting scroll 106 may include an end plate 118 having a spiral wrap 220 on a lower surface thereof. Spiral wrap 220 may form a meshing engagement with wrap 210 of orbiting scroll 204, thereby creating an inlet pocket 122, intermediate pockets 124, 126, 128, 130 and an outlet pocket 132.
  • Non-orbiting scroll 106 may be axially displaceable relative to main bearing housing 68, housing assembly 12, and orbiting scroll 204. More specifically, non- orbiting scroll 106 may include a series of flanges 134 including bores (not shown) extending therethrough. Flanges 134 may cooperate with retaining assembly 20 to provide for axial displacement of non-orbiting scroll 106, as discussed below.
  • Non-orbiting scroll 106 may include a discharge passageway 138 in communication with outlet pocket 132 and upwardly open recess 140 which may be in fluid communication with discharge chamber 44 via opening 48 in partition 34.
  • Non-orbiting scroll 106 may additionally include an annular recess 142 in the upper surface thereof defined by parallel coaxial inner and outer side walls 144, 146.
  • Annular recess 142 may provide for axial biasing of non-orbiting scroll 106 relative to orbiting scroll 204, as discussed below. More specifically, a passage 148 may extend through end plate 118 of non-orbiting scroll 106, placing recess 142 in fluid communication with intermediate pocket 126. While passage 148 is shown extending to intermediate pocket 126, it is understood that passage 148 may alternatively be placed in communication with any of the other intermediate pockets.
  • Retaining assembly 20 may couple non-orbiting scroll 106 to main bearing housing assembly 14 for axial displacement relative thereto.
  • Retaining assembly 20 may include a fastener 150 such as a bolt. Fastener 150 may extend through the bore in flange 134 and may be threadingly engaged with main bearing housing assembly 14.
  • Seal assembly 22 may include a floating seal assembly. Seal assembly 22 may sealingly engage partition 34 to isolate the discharge pressure region from the suction pressure region and may sealingly engage non- orbiting scroll 106 to isolate annular recess 142 from the suction and discharge pressure regions.
  • Discharge valve assembly 24 may be fixed to non-orbiting scroll 106 and may generally prevent reverse flow through discharge passageway 138 during shut-down of compressor 10.
  • An oil sump 152 may be in communication with discharge chamber 44.
  • Oil separator 26 may be located downstream of discharge valve assembly 24. Oil separator 26 may provide separation of oil entrained within discharge gas exiting compression mechanism 18. Oil removed from the discharge gas by oil separator 26 may return to oil sump 152.
  • oil sump 152 is shown defined within discharge chamber 44 generally opposite discharge fitting 40.
  • compressor 10 is not limited to internal oil sump arrangements and the present teachings apply equally to alternate oil sump arrangements.
  • oil sump 152 and oil separator 26 may be located in a separate housing external to compressor 10 and in communication with discharge chamber 44.
  • Oil feed mechanism 28 may include an oil feed tube 154 in communication with oil sump 152.
  • Oil feed tube 154 may pass through partition 34 and provide fluid communication between oil sump 152 and main bearing housing assembly 14. More specifically, a first end 156 of oil feed tube 154 may extend into oil sump 152 and a second end 158 of oil feed tube 154 may be fixed to main bearing housing 68 and may be in communication with oil passage 78 therein.
  • Drive shaft 86 may include a central oil passage 160, and first, second, and third radially extending oil passages 162, 164, 166.
  • Central oil passage 160 may extend longitudinally within drive shaft 86 through first end 92 of drive shaft 86 and may terminate at a location before second end 94.
  • Central oil passage 160 may extend at an angle of less than 3 degrees relative to a rotational axis of drive shaft 86. More specifically, central oil passage 160 may extend at an angle radially outwardly in a direction from first end 92 to second end 94 of drive shaft 86.
  • central oil passage 160 proximate first radially extending oil passage 162 may be disposed radially outwardly relative to an end of central oil passage 160 proximate first end 92 of drive shaft 86.
  • Central oil passage 160 may therefore pump oil to first radially extending oil passage 162.
  • First radially extending oil passage 162 may intersect central oil passage 160 at a location proximate bearing assembly 52. More specifically, first radially extending oil passage 162 may be located longitudinally between bearing assembly 52 and seal assembly 56 and may extend at approximately a 90 degree angle relative to the rotational axis of drive shaft 86. First radially extending oil passage 162 may have a diameter of between 2.0 mm and 3.0 mm, and more specifically, approximately 2.5 mm to meter an oil flow therethrough.
  • Second and third radially extending oil passages 164, 166 may intersect central oil passage 160 at a location proximate bearing 76 of main bearing housing 68. More specifically, second and third radially extending oil passages 164, 166 may be longitudinally aligned with opening 80 in bearing 76. Second and third radially extending oil passages 164, 166 may be disposed generally opposite one another, or approximately 180 degrees apart. Second and third radially extending oil passages 164, 166 may each extend at approximately a 90 degree angle relative to the rotational axis of drive shaft 86. Second and third radially extending oil passages 164, 166 may be sized to meter an oil flow into central oil passage 160.
  • second and third radially extending oil passages 164, 166 may have diameters of 3.0 mm to 4.0 mm.
  • Drive shaft 86 may include a flat 167 that forms a recess between drive shaft 86 and bearing 76 to lubricate bearing 76.
  • compression mechanism 18 may provide a fluid flow to oil sump 152.
  • the fluid flow may include a combination of discharge gas and entrained oil.
  • the discharge gas pressures generated by compression mechanism 18 may act on the oil volume within oil sump 152 to force oil into oil feed tube 154.
  • Oil may be supplied to main bearing housing 68 and bearing 76 through opening 80 to provide lubrication between bearing 76 and first journal portion 96 of drive shaft 86.
  • the discharge gas pressures acting on oil sump 152 may be sufficient to overcome any centrifugal pressures generated by rotation of second and third radially extending oil passages 164, 166.
  • discharge gas pressures may be more than 10 times the centrifugal pressure generated by rotation of second and third radially extending oil passages 164, 166, and more specifically greater than 25 times the centrifugal pressure generated by rotation of second and third radially extending oil passages 164, 166.
  • the discharge gas pressure may generally be the pressure within discharge chamber 44.
  • the pressure acting upon oil in discharge chamber 44 may therefore force oil into second and third radially extending oil passages 164, 166 and into central oil passage 160.
  • the angular orientation of central oil passage 160 may pump oil to first radially extending oil passage 162 to provide lubrication between bearing assembly 52 and second journal portion 98 of drive shaft 86. Oil may return to oil sump 1 2 by being drawn into compression mechanism 18 with suction gas and forced into discharge chamber 44.
  • the first radially extending oil passage 162 may be sized to maintain an oil pressure within central oil passage 160 sufficient to force an oil flow from first end 92 of drive shaft 86 toward main bearing housing 68.
  • the oil flow from first end 92 may collect in a region of main bearing housing 68 adjacent to first counterweight 88.
  • Rotation of first counterweight 88 may displace oil toward annular flat thrust bearing surface 82, providing lubrication for annular flat thrust bearing surface 82, as well as for orbiting and non-orbiting scrolls 204, 106.
  • Fig. 2 also shows a valve 206 which may be employed as part of the compressor piping.
  • the valve 206 can be controlled by a unit controller 208, e.g.
  • the unit controller 208 can include a processor, a memory, and an input/output (I/O) interface as suitable and/or desired to carry out the control of the valve 206.
  • I/O input/output
  • Various leak paths indicated by circles on the non-orbiting scroll 106 can access intermediate pressure pockets, such as 124, 126, 128, and 130 and be in fluid communication with the valve 206, which may be a solenoid valve or other suitable valve which may be controlled by the unit controller.
  • the valve 206 can be a "digital" valve, such as known for example, in Copeland Scroll DigitalTM compressor controller.
  • valve 206 can be any pressure relief and/or unloading device suitable for use in a compressor, such as a scroll compressor, that can implement the concepts of unloading before start-up as described herein, and it will also be appreciated that the leak paths are merely exemplary as other configurations and arrangements to fluidly access the pressure relief and/or unloading device, e.g. valve 206 are possible.
  • the valve 206 is also in fluid communication with the suction side such as at inlet 42 and fitting 38 or in a chamber of the suction side of the compressor 10. It will be appreciated that the valve may be outside of the compressor shell 30 or inside as shown by the exemplary valves 206 placed inside the shell. It will be appreciated that suitable piping can connect the leak path to the valve 206 and the valve to the suction side, e.g. using appropriate discharge valves as necessary.
  • Fig. 3 illustrates a flow chart of a method 300 to protect a compressor, such as a scroll compressor, from reverse rotation.
  • the TRU is configured to determine whether there is a compressor shutdown event to occur, which can be obtained for example from various data in the TRU, including for example temperature readings, pressure readings, load readings, operational mode(s), and/or operational capacity.
  • the method 300 proceeds to 320.
  • the valve can be activated.
  • the compressor can go to an unloaded state and release the relatively high discharge pressure toward suction, e.g. to the suction chamber, through a path from the scroll set for example from one or more leak paths from one of the non-orbiting and/or orbiting scrolls and through the valve.
  • shutdown of the compressor or TRU can occur safely once there has been sufficient relief of the discharge pressure to an unloaded state.
  • a method to protect a compressor from reverse rotation, such as a scroll compressor includes unloading the compressor, such as by activating a valve.
  • Activating the valve allows releasing of relatively high discharge pressure present in the scroll set to travel into a suction chamber and into the compression chamber. Releasing the relatively high discharge pressure into the suction chamber allows for unloading of the compressor, which in some cases includes allowing the scroll sets to separate slightly. When the compressor has been appropriately unloaded it can safely shutdown. In some embodiments, the method includes shutting down the compressor.
  • valve or other pressure relief and/or unloading device can be energized, such as in response to a controller of the TRU (e.g. TRS controller), which opens a flow path, such as one or more leak path(s) to suction. This can relieve pressure from the relatively high discharge pressure side, e.g. which may be present for example as intermediate pressures built up in the scroll set. The relief of pressure unloads the compressor, so that shut down can safely occur, and reverse rotation can be avoided.
  • a controller of the TRU e.g. TRS controller
  • the controller can also deenergize the valve to load the compressor.
  • a cycle time may be employed to achieve a certain compressor capacity and operation mode, which may be desired.
  • the TRU can operate with a loaded state time and an unloaded state time, based on deactivation/activation of the valve.
  • the valve may be a solenoid valve.
  • a duty cycle could be 15 seconds within which certain loaded state times and unloaded state times could be used to obtain certain modulation, and to obtain certain capacity such as between 10% and 100%. It will be appreciated that the duty cycle modulation could be fixed or varied.
  • Fig. 4 illustrates a graph showing a result of complication in a scroll compressor or failure due to the absence of the valve control.
  • the graph shows compressor speed over time where the engine is observed for example after a shut off event.
  • the dashed line NRPM is the engine speed, e.g. RPM and the solid line CRPM is compressor speed, e.g. RPM.
  • NRPM is the engine speed
  • CRPM compressor speed
  • Fig. 5 illustrates a graph of a scroll compressor operation in the presence of the valve control operation.
  • the graph shows compressor speed over time where the engine is observed for example after a shut off event.
  • the dashed line NRPM is the engine speed, e.g. RPM, and the solid line CRPM compressor speed, e.g. RPM.
  • NRPM is the engine speed, e.g. RPM
  • CRPM compressor speed e.g. RPM
  • Fig. 6 illustrates a schematic diagram of a scroll compressor 400 that may be employed in a TRU and showing an example of a valve 406 employing digital control.
  • the compressor 400 is similarly constructed as the compressor 10 of Fig. 2, where like features are not further described.
  • Fig. 6 is for illustrative purposes only of a "digital" valve referred to above such as may be known.
  • the scroll compressor 400 can have the valve 406 that may employ digital control to unload the scroll sets and allow for the release of relatively high pressure to the suction side of the scroll compressor 400.
  • a suitable line 416 is in communication with the valve 406 to allow the relatively high pressure fluid to enter the valve 406 and the valve 406 has a port 418 to release the fluid to the suction side of the scroll compressor 400.
  • a method to prevent reverse rotation in a scroll compressor prior to shutdown of the scroll compressor comprising:
  • the unloading includes separating the orbiting scroll from the non-orbiting scroll and releasing relatively higher pressure fluid to a suction side;
  • the unloading further comprises activating an unloading device to open a flow path to the suction side.
  • releasing further comprises releasing the relatively high pressure fluid from one or more of a discharge chamber and of one or more portions of intermediate pressure built up in one or more of the scroll sets.
  • determining includes determining from data obtained by a controller one or more of a temperature reading, a pressure reading, a load reading, an operational mode, and an operational capacity.
  • a system to prevent reverse rotation in a scroll compressor prior to shutdown of the scroll compressor comprising:
  • a scroll compressor having scroll sets including an orbiting scroll and a non-orbiting scroll, the scroll compressor having a suction side and having a portion at relatively higher pressure than the suction side during operation of the scroll compressor;
  • an unloading device in fluid communication with the suction side and with the portion at relatively higher pressure than the suction side;
  • the controller is configured to determine through data obtained thereby the presence of a shutdown event of the scroll compressor and, in the presence of the shutdown event, the controller is configured to unload the scroll sets to separate the orbiting scroll from the non-orbiting scroll, and to release relatively higher pressure fluid to the suction side, and the controller is configured to shut down the scroll compressor after the scroll sets have been unloaded.
  • the unloading device comprises a valve configured to be activated to open a flow path to the suction side.
  • the unloading device comprises a valve configured to be activated to open a flow path to the suction side.
  • the unloading device comprises a valve configured to be activated to open a flow path to the suction side.
  • the system of any of aspects 6 to 8 further comprising one or more leak paths on one or more of the scroll sets, the one or more leak paths configured to allow the relatively higher pressure fluid to travel through the one or more leak paths to the suction side.
  • controller configured to obtain data, including one or more of a temperature reading, a pressure reading, a load reading, an operational mode, and an operational capacity, the controller configured to determine the presence of the shutdown event from the obtained data.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne des systèmes, des procédés et des éléments, tels que dans un compresseur, qui sont conçus pour protéger le compresseur, tel qu'un compresseur à spirales, lorsqu'une rotation inverse se produit et/ou afin d'éviter ou au moins de réduire une rotation inverse. Une soupape peut être activée avant l'arrêt pour permettre qu'une contre-pression de refoulement relativement élevée se déplace à travers un trajet dans la chambre d'aspiration et non pas dans la chambre de compression. Un ou plusieurs trajets de fuite peuvent être utilisés pour permettre à la contre-pression de refoulement relativement élevée de se déplacer dans la chambre d'aspiration. Le ou les trajets de fuite peuvent utiliser des éléments du compresseur, comme sur l'ensemble de spirales, par exemple sur la spirale non orbitale et/ou sur la spirale orbitale. Le ou les trajets de fuite se trouvent en communication fluidique avec le trajet vers la chambre d'aspiration, où la soupape est commandée de sorte à ouvrir ou à fermer le trajet vers la chambre d'aspiration.
PCT/US2013/078438 2012-12-31 2013-12-31 Commande de compresseur pour défaillance de rotation inverse WO2014106233A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201261747722P 2012-12-31 2012-12-31
US61/747,722 2012-12-31
US201361794594P 2013-03-15 2013-03-15
US61/794,594 2013-03-15

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WO2014106233A1 true WO2014106233A1 (fr) 2014-07-03

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108474377A (zh) * 2016-07-15 2018-08-31 翰昂汽车零部件有限公司 压缩装置以及控制质量流的分离方法
US11499767B2 (en) 2018-04-09 2022-11-15 Carrier Corporation Reverse rotation prevention in centrifugal compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6042344A (en) * 1998-07-13 2000-03-28 Carrier Corporation Control of scroll compressor at shutdown to prevent unpowered reverse rotation
US6213731B1 (en) * 1999-09-21 2001-04-10 Copeland Corporation Compressor pulse width modulation
JP2003193983A (ja) * 2001-12-13 2003-07-09 Lg Electronics Inc 遠心型圧縮機の逆回転防止構造
US20060056989A1 (en) * 2004-09-10 2006-03-16 Taras Michael F Valve for preventing unpowered reverse run at shutdown
US20120085117A1 (en) * 2009-06-05 2012-04-12 Makoto Ikemiya Trailer refrigerating apparatus

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6042344A (en) * 1998-07-13 2000-03-28 Carrier Corporation Control of scroll compressor at shutdown to prevent unpowered reverse rotation
US6213731B1 (en) * 1999-09-21 2001-04-10 Copeland Corporation Compressor pulse width modulation
JP2003193983A (ja) * 2001-12-13 2003-07-09 Lg Electronics Inc 遠心型圧縮機の逆回転防止構造
US20060056989A1 (en) * 2004-09-10 2006-03-16 Taras Michael F Valve for preventing unpowered reverse run at shutdown
US20120085117A1 (en) * 2009-06-05 2012-04-12 Makoto Ikemiya Trailer refrigerating apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108474377A (zh) * 2016-07-15 2018-08-31 翰昂汽车零部件有限公司 压缩装置以及控制质量流的分离方法
CN108474377B (zh) * 2016-07-15 2019-12-13 翰昂汽车零部件有限公司 压缩装置以及控制质量流的分离方法
US11499767B2 (en) 2018-04-09 2022-11-15 Carrier Corporation Reverse rotation prevention in centrifugal compressor

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