US20160138594A9 - Compressor system including a flow and temperature control device - Google Patents
Compressor system including a flow and temperature control device Download PDFInfo
- Publication number
- US20160138594A9 US20160138594A9 US13/580,291 US201013580291A US2016138594A9 US 20160138594 A9 US20160138594 A9 US 20160138594A9 US 201013580291 A US201013580291 A US 201013580291A US 2016138594 A9 US2016138594 A9 US 2016138594A9
- Authority
- US
- United States
- Prior art keywords
- coolant
- lubricant
- flow
- inlet
- sleeve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002826 coolant Substances 0.000 claims abstract description 112
- 239000000314 lubricant Substances 0.000 claims abstract description 77
- 230000004044 response Effects 0.000 claims abstract description 14
- 239000000203 mixture Substances 0.000 claims description 15
- 238000004891 communication Methods 0.000 claims description 13
- 238000000034 method Methods 0.000 claims description 11
- 239000012530 fluid Substances 0.000 claims description 7
- 238000001816 cooling Methods 0.000 claims description 4
- 238000007599 discharging Methods 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 28
- 239000003570 air Substances 0.000 description 20
- 239000012080 ambient air Substances 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 238000009833 condensation Methods 0.000 description 5
- 230000005494 condensation Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 239000000356 contaminant Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- 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
- F04B49/06—Control using electricity
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/021—Control systems for the circulation of the lubricant
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
- F01M5/005—Controlling temperature of lubricant
- F01M5/007—Thermostatic control
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
-
- 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/01—Control of temperature without auxiliary power
- G05D23/02—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature
- G05D23/021—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature the sensing element being a non-metallic solid, e.g. elastomer, paste
- G05D23/023—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature the sensing element being a non-metallic solid, e.g. elastomer, paste the sensing element being placed outside a regulating fluid flow
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/19—Control of temperature characterised by the use of electric means
- G05D23/1927—Control of temperature characterised by the use of electric means using a plurality of sensors
- G05D23/193—Control of temperature characterised by the use of electric means using a plurality of sensors sensing the temperaure in different places in thermal relationship with one or more spaces
- G05D23/1931—Control of temperature characterised by the use of electric means using a plurality of sensors sensing the temperaure in different places in thermal relationship with one or more spaces to control the temperature of one space
-
- 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
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7737—Thermal responsive
Definitions
- the present invention relates to compressors. More particularly, the present invention relates to a mechanism for managing the flow and temperature of lubricant/coolant in a compressor system.
- a compressor system including, for example a contact-cooled rotary screw airend, injects a lubricating coolant (referred to herein as lubricant, coolant, oil, etc.) such as oil into the compression chamber to absorb the heat created by the compression of air and lubrication.
- a lubricating coolant referred to herein as lubricant, coolant, oil, etc.
- the temperature of the oil must be maintained within a range to maximize its life and to minimize the formation of condensation within the compressor system.
- the amount and temperature of the injected oil also has an effect on the overall performance of the airend.
- the invention provides a compressor system including a compressor including a gas inlet and a lubricant inlet, the compressor operable to compress a gas and discharge a mixed flow of compressed gas and lubricant.
- a valve housing includes a hot lubricant inlet, a cooled lubricant inlet, and a lubricant outlet connected to the lubricant inlet of the compressor and a sleeve is disposed within the valve housing and is movable between a first position and a second position.
- the sleeve selectively uncovers the hot lubricant inlet to selectively direct a hot lubricant to the lubricant outlet and selectively uncovers the cooled lubricant inlet to selectively direct a cooled lubricant to the lubricant outlet.
- the hot lubricant and cooled lubricant mixes at the lubricant outlet to define a bulk lubricant that is directed to the lubricant inlet of the compressor.
- a controller is operable to sense a parameter and generate a control signal at least partially in response to the sensed parameter and a motor is coupled to the sleeve and is operable to move the sleeve in response to the control signal. The movement of the sleeve is operable to vary the amount of hot lubricant admitted through the first aperture and to vary the amount of cooled lubricant admitted through the second aperture to control a temperature of the bulk lubricant.
- the invention provides a thermal control valve for use in a lubricant flooded compressor system including a controller that generates a control signal.
- the thermal control valve includes a valve body including a hot coolant inlet, a cooled coolant inlet, a mixed coolant outlet, an actuator space, and a cylinder bore.
- a sleeve is positioned within the cylinder bore and is movable between a first position, a second position, and a third position, and an electrical actuator is at least partially disposed within the actuator space and is operable in response to the control signal to move the sleeve between the first position, the second position, and the third position.
- the invention provides a method of controlling the temperature and quantity of a bulk flow of coolant to a lubricant flooded compressor in a compressor system.
- the method includes dividing a flow of hot coolant into a first flow of coolant and a second flow of coolant, cooling the first flow of coolant to produce a third flow of coolant, and directing the second flow of coolant and the third flow of coolant to a valve and discharging the bulk flow of coolant from the valve.
- the method also includes sensing a parameter of the compressor system and delivering the measured parameter to a controller, generating a control signal at least partially in response to the sensed parameter, and operating an electrical actuator at least partially in response to the control signal to configure the valve between a first position, a second position, and a third position.
- the bulk flow of coolant includes only coolant from the second flow of coolant when the valve is in the first position
- the bulk flow of coolant includes only coolant from the third flow of coolant when the valve is in the second position
- the bulk flow of coolant includes a mixture of coolant from the second flow of coolant and the third flow of coolant when the valve is between the first position and the second position.
- FIG. 1 is a schematic illustration of a compressor system including a flow and temperature control device
- FIG. 2 is a section view of the flow and temperature control device of FIG. 1 , in which a sleeve of the device is in a first position;
- FIG. 3 is a section view of the flow and temperature control device of FIG. 1 , in which the sleeve is in a second position;
- FIG. 4 is a section view of the flow and temperature control device of FIG. 1 , in which the sleeve is in a third position;
- FIG. 5 is a schematic illustration of another compressor system including a flow and temperature control device
- FIG. 6 is a section view of the flow and temperature control device of FIG. 5 in a first position
- FIG. 7 is a section view of the flow and temperature control device of FIG. 5 in a second position.
- FIG. 8 is a section view of the flow and temperature control device of FIG. 5 in a third position.
- FIG. 1 illustrates a compressor system 20 including a compressor airend (referred to herein simply as the compressor 24 , an oil separator 28 , a filter 32 , an oil cooler 36 , and a control valve 40 .
- the compressor 24 compresses air and oil to produce an air/oil mixture having an elevated pressure compared to the air and oil supplied to the compressor 24 .
- air and “oil”
- the specific type of gas being compressed and the specific type of lubricating coolant injected for compression with the gas is not critical to the invention, and may vary based on the type of compressor, the intended usage, or other factors.
- the air and oil compressed within the compressor 24 undergoes an increase in pressure and also temperature.
- the air/oil mixture is directed from the compressor 24 to the oil separator 28 along an air/oil or “compressor outlet” flow path 44 as shown in FIG. 1 .
- the oil separator 28 separates the air/oil mixture into two separate flows, a flow of compressed air that exits the oil separator 28 along a first outlet flow path 48 , and a flow of oil that exits the oil separator 28 along a second outlet flow path 52 .
- the compressed air in the first outlet flow path 48 can be supplied to any point-of-use device or to additional processing components or assemblies (not shown) of the compressor system 20 , such as a cooler, dryer, additional compressor(s), etc.
- the flow of oil in the second outlet flow path 52 from the oil separator 28 is directed to the filter 32 , which filters the oil of contaminants before it is returned to the compressor 24 .
- the oil can be directed along one of two separate flow paths to the control valve 40 .
- the first flow path 56 directs oil directly from the filter 32 to the control valve 40 without cooling the oil.
- the second flow path 60 between the filter 32 and the control valve 40 directs oil through the oil cooler 36 that is positioned along the second flow path 60 .
- a first portion 60 A of the second flow path 60 is an oil cooler inlet flow path, and a second portion 60 B of the second flow 60 is an oil cooler outlet flow path.
- Both of the flow paths 56 , 60 from the filter 32 lead to the control valve 40 , which has a single outlet leading to an oil supply flow path 64 which supplies the oil back to the compressor 24 .
- the valve 40 controls how much of the oil flowing through the filter 32 is directed through the cooler 36 and how much is passed directly from the filter 32 to the valve 40 .
- the first outlet flow path 56 from the filter 32 is an inlet flow path to a first inlet 70 A of the valve 40 ( FIG. 2 ).
- the second outlet flow path 60 from the filter 32 is an inlet flow path to a second inlet 70 B of the valve 40 ( FIG. 2 ).
- the control valve 40 includes a body 74 , a sleeve 76 movable within a chamber 78 formed in the body 74 , and a thermal element or actuator 80 positioned at an end of the sleeve 76 .
- the first inlet 70 A of the valve 40 is in communication with a first annular passage 84 A that surrounds the sleeve 76 .
- the second inlet 70 B of the valve 40 is in communication with a second annular passage 84 B that surrounds the sleeve 76 .
- the first and second annular passages 84 A, 84 B are spaced from each other along an axis 88 of the valve 40 defined by the chamber 78 and the sleeve 76 .
- the sleeve 76 includes a first aperture 92 A in selective communication with the first annular passage 84 A and a second aperture 92 B in selective communication with the second annular passage 84 B.
- the second aperture 92 B is larger than the first aperture 92 A.
- Both of the apertures 92 A, 92 B are in communication with a mixing chamber 96 defined by the inside of the sleeve 76 , which is substantially hollow and cylindrical in the illustrated construction.
- the mixing chamber 96 is in communication with the valve outlet (and thus, the oil supply flow path 64 ) so that all of the oil supplied to the mixing chamber 96 (whether from the first inlet 70 A or the second inlet 70 B, or both) is directed to the oil supply flow path 64 .
- the oil transferred from the mixing chamber 96 to the oil supply flow path 64 through the valve outlet is referred to as the “bulk” flow of oil (or “combined” flow if oil that is received from both inlets 70 A, 70 B).
- first aperture 92 A is illustrated as the only aperture for admitting oil into the mixing chamber 96 from the first inlet 70 A and the second aperture 92 B is illustrated as the only aperture for admitting oil into the mixing chamber 96 from the second inlet 70 B
- first and second apertures 92 A, 92 B can be one of a plurality of apertures spaced around the sleeve 76 to admit oil into the mixing chamber 96 from multiple angles about the respective annular passages 84 A, 84 B.
- the first and second apertures 92 A, 92 B are the only two apertures or are each a part of a respective plurality of apertures, the functional characteristics described below are equally applicable.
- the flow of oil to the compressor 24 should not exceed a predetermined desired flow rate for maximum performance of the compressor 24 .
- the sleeve 76 is in a first position as shown in FIG. 2 . In the first position, the first aperture 92 A is fully exposed to the first annular passage 84 A and the second aperture 92 B is fully blocked from communication with the second annular passage 84 B. Thus, none of the flow of oil from the filter 32 is supplied to the valve 40 through the oil cooler 36 .
- the first flow path 56 which is a flow path between the filter 32 and the valve 40 along which the oil is not actively cooled.
- the flow path may be a direct flow path between the filter 32 and the valve 40 as shown in FIG. 1 .
- the first aperture 92 A in the sleeve 76 is sized to provide a minimum required flow of oil when the sleeve 76 is in the first position. If the first aperture 92 A is one of a plurality of apertures in communication with the first annular passage 84 A, the plurality of apertures as a whole are sized to provide a minimum required flow of oil when the sleeve 76 is in the first position.
- the sleeve 76 When the compressor 24 is operating at a temperature from the first predetermined set point up to a second predetermined set point, the sleeve 76 is gradually moved by the actuator 80 from the first position toward a second position ( FIG. 3 ) as described in further detail below. In the second position, the second aperture 92 B is partially exposed to the second annular passage 84 B and the first aperture 92 A is fully blocked from communication with the first annular passage 84 A. Thus, none of the flow of oil from the filter 32 is supplied to the valve 40 directly through the first flow path 56 . Rather, all of the flow of oil from the filter 32 to the valve 40 is provided through the second flow path 60 , which directs the flow of oil through the oil cooler 36 before delivering it to the valve 40 .
- the exposed portion of the second aperture 92 B in the sleeve 76 provides a flow of cooled oil about equal to the minimum required flow (i.e., about equal to the flow of oil provided through the first aperture 92 A when the sleeve 76 is in the first position).
- portions of both apertures 92 A, 92 B are exposed to the respective annular passages 84 A, 84 B so that a mix of “hot” oil (i.e., un-cooled by the oil cooler 36 ) and cooled oil is provided to the oil supply flow path 64 .
- the remaining portions of both apertures 92 A, 92 B are blocked.
- the overall flow i.e., “combined flow” or “bulk flow”
- the overall flow remains the same (i.e., about equal to the minimum required flow provided by the first aperture 92 A in the first position) as the combined size of the portions of the apertures 92 A, 92 B that are exposed is about equal to the size of the first aperture 92 A.
- the second aperture 92 B in the sleeve 76 is sized to provide a maximum flow of cooled oil when fully open (i.e., fully exposed to the second annular passage 84 B and the second inlet 70 B when the sleeve 76 is in the third position). If the second aperture 92 B is one of a plurality of apertures in communication with the second annular passage 84 B, the plurality of apertures as a whole are sized to provide a maximum flow of cooled oil when fully open.
- the actuator 80 includes a sensor portion 80 A and a prime mover portion 80 B.
- the sensor portion 80 A is positioned in a chamber 100 of the valve body 74 that is remote from the chamber 78 that houses the sleeve 76 .
- the chamber 100 and thus the sensor portion 80 A of the actuator 80 , is in fluid communication with the oil or the air/oil mixture.
- FIG. 1 illustrates three possible paths A, B, C for fluidly coupling the chamber 100 with oil or the air/oil mixture.
- Each of the paths A, B, C represents a potential tubing or piping conduit for fluidly coupling the chamber 100 and the sensor portion 80 A with a fluid of the compressor system 20 .
- the first path A couples the chamber 100 to the oil supply flow path 64 at a position just upstream of the compressor 24 .
- the sensor portion 80 A of the actuator 80 senses and reacts to the temperature of the oil just prior to injection into the compressor 24 .
- the second path B couples the chamber 100 to the air/oil mixture just downstream of the compressor 24 .
- the sensor portion 80 A of the actuator 80 senses and reacts to the temperature of the air/oil mixture just after ejection from the compressor 24 .
- the third path C couples the chamber 100 to the oil just downstream of the oil separator 28 .
- the sensor portion 80 A of the actuator 80 senses and reacts to the temperature of the oil just after separation from the compressed air/oil mixture.
- the valve 40 may be physically coupled to the compressor 24 or positioned directly adjacent the oil inlet of the compressor 24 where the oil supply flow path 64 injects oil into the compressor 24 so that the sensor portion 80 A may be positioned directly in or adjacent to the compressor's oil inlet.
- the valve 40 may be physically coupled to the compressor 24 or positioned directly adjacent the outlet of the compressor 24 where the compressed air/oil mixture is ejected from the compressor 24 to the outlet flow path 44 so that the sensor portion 80 A may be positioned directly in or adjacent to the compressor's outlet.
- the valve 40 may be physically coupled to or positioned directly adjacent the outlet of the oil separator 28 or the inlet of the filter 32 so that the sensor portion 80 A may be positioned directly in or adjacent to the separator outlet or the filter inlet.
- the sensor portion 80 A is remotely located and fluid is directed along one of the paths A, B, or C to the sensor portion 80 A to allow the sensor portion 80 A to sense the fluid temperature.
- the operation of the valve 40 can be calibrated to control the temperature and the flow of oil based on the use of any one of the possible paths A, B, C.
- the actuator 80 may be a diaphragm-type thermal actuator available from Caltherm Corporation of Columbus, Ind.
- the sensor portion 80 A of the actuator 80 can include an expansion material 104 contained within a cup 108 and configured to move the prime mover portion 80 B in a predetermined linear manner within the operating temperature range of the compressor 24 (i.e., the temperature range of the oil or air/oil mixture).
- the expansion material 104 is wax which changes phase from solid to liquid within the operating temperature range of the compressor 24 .
- the prime mover portion 80 B of the actuator 80 can include a piston 112 that is coupled to a diaphragm 116 with a plug 120 .
- the diaphragm 116 cooperates with the cup 108 to define a chamber that contains the expansion material 104 .
- a housing or piston guide 124 of the actuator 80 at least partially encloses the piston 112 and the plug 120 , and cooperates with the cup 108 to sandwich the diaphragm 116 in position.
- the exterior of the piston guide 124 includes male threads 128 for engaging the actuator 80 with a threaded aperture 132 of the valve body 74 .
- the actuator 80 is illustrated to include a linearly traveling prime mover portion 80 B which actuates the sleeve 76 in a linear manner
- a rotary type actuator can be substituted.
- the valve 40 can be reconfigured to selectively establish and terminate fluid communication between the inlets 70 A, 70 B and the apertures 92 A, 92 B upon rotative movement of the sleeve 76 within the chamber 78 or a transmission device can be provided to convert rotative movement to linear movement.
- the actuator 80 may be an electro-mechanical actuator.
- the sensor portion 80 A of the actuator 80 can be an electrical sensor configured to output an electrical signal.
- the prime mover portion 80 B can be an electrical motor that is configured to move the sleeve 76 back and forth in a calibrated manner between the positions described above, based on the fluid temperature sensed by the sensor portion 80 A.
- the sensor portion 80 A and the prime mover portion 80 B can be located remotely from each other or adjacent each other.
- the valve 40 operates to control the quantity and temperature of the oil delivered to the compressor 24 to assure that the minimum and most efficient quantity of oil is delivered to the compressor 24 unless the oil temperature demands additional flow.
- the compressor 24 and the oil are both cold.
- the oil does not perform optimally at this lower temperature and it is desirable to heat the oil to a desired temperature range as quickly as possible.
- the valve 40 senses this low oil temperature and maintains the sleeve in the position illustrated in FIG. 2 . When in this position, none of the oil passes through the oil cooler 36 . Rather, the oil continues to circulate through the compressor 24 , thereby heating the oil.
- the sleeve 76 begins moving to the right toward the position illustrated in FIG.
- FIGS. 5-8 illustrate a compressor system 110 that includes a flow and temperature control device 115 that includes an electromechanical or electrical actuator 120 .
- the system of FIGS. 5 and 6 includes an oil-flooded compressor 125 (e.g., an oil-flooded screw compressor) that operates to produce a flow of compressed air. Oil is injected or drawn into the compressor 125 to improve the seals within the compressor 125 , to lubricate the moving parts of the compressor 125 , and to remove some of the heat of compression generated during the compression process.
- the system 110 also includes an oil separator 130 and an oil cooler 135 that are similar to those described with regard to FIGS. 1-4 and will not be described in detail.
- the flow and temperature control device 115 includes a flow divider 140 , a thermal control valve 145 , a controller 150 , and various sensors 155 .
- the flow divider 140 is positioned to receive a flow of hot oil 160 from the oil separator 130 and operates to divide that flow into a first flow 165 directed to the oil cooler 135 and a second flow 170 directed to the thermal control valve 145 .
- the first flow 165 is cooled in the oil cooler 135 and discharged from the oil cooler 135 as a third flow 175 .
- the thermal control valve 145 is positioned to receive the second flow 170 or hot coolant flow, and the third flow 175 or cooled coolant flow and to discharge a fourth flow 180 or bulk flow of coolant at a desired mixed temperature.
- the fourth flow of coolant 180 is injected into or drawn into the compressor 125 through an oil filter to complete the oil flow cycle.
- the thermal control valve 145 of FIG. 5 is illustrated as including a valve body 185 , a sleeve 190 , and the electromechanical or electrical actuator 120 .
- the valve body 185 includes a cooled coolant inlet 195 , a hot coolant inlet 200 , and a mixed coolant outlet 205 .
- the cooled coolant inlet 195 includes a larger flow area than the hot coolant inlet 200 .
- the valve body 185 also defines a cylinder bore 210 sized to receive the sleeve 190 and an actuator space 215 sized to receive a portion of the electro/mechanical actuator 120 .
- a cover 220 attaches to the valve body 185 to seal at least a portion of the electromechanical actuator 120 within the valve 185 and to inhibit oil leakage from the valve body 185 .
- the sleeve 190 includes an outer cylindrical surface 225 sized to closely fit within the cylinder bore 210 .
- the sleeve 190 is movable axially (as indicated by the arrow in FIG. 6 ) along the cylinder bore 210 and provides a seal there between.
- the sleeve 190 includes a central aperture 230 that receives a threaded nut 235 and at least one flow passage 240 that allows for the flow of oil through the sleeve 190 .
- the electromechanical actuator 120 includes a motor 245 that is positioned within the actuator space 215 and that is operable to rotate a lead screw 250 connected to the motor 245 .
- a stepper motor 245 is used to allow for the precise positioning of the lead screw 250 .
- other constructions could employ a standard DC motor or other type of motor as required.
- the lead screw 250 threadably engages the nut 235 such that rotation of the lead screw 250 produces axial movement of the sleeve 190 .
- a clutch mechanism (not shown) is positioned between the motor 245 and the lead screw 250 to reduce the likelihood of damage should movement of the sleeve 190 be inhibited.
- a pin 255 is fixedly positioned with respect to the valve body 185 and engages the sleeve 190 to inhibit rotation of the sleeve 190 while still allowing free axial movement of the sleeve 190 in response to rotation of the lead screw 250 .
- a signal 260 is provided to the motor 245 that results in operation of the motor 245 .
- the valve 145 With the valve 145 in the first position illustrated in FIG. 6 , only hot oil entering the valve body 185 via the hot coolant inlet 200 flows out of the valve 145 via the mixed coolant outlet 205 . This position represents one end of travel for the sleeve 190 .
- the motor 245 operates and rotates the lead screw 250 , the sleeve 190 begins to move toward a second position (shown in FIG. 7 ). As the sleeve 190 moves to the right of the position in FIG. 6 , the cooled coolant inlet 195 begins to uncover.
- Cooled oil is now able to flow into the space to the left of the sleeve 190 and through the sleeve 190 to the mixed coolant outlet 205 .
- the hot coolant inlet 200 begins to cover.
- the area of the cooled coolant inlet 195 that is exposed or opened is equal to the area of the hot coolant inlet 200 that is covered or closed.
- a substantially equal amount of oil flows from the valve body 185 via the mixed coolant outlet 205 .
- 100 percent of that oil is hot oil
- 100 percent of that oil is cooled oil
- the flow is a mixture of hot coolant and cooled coolant.
- additional cooled coolant is able to flow through the valve 145 .
- the sleeve 190 reaches the third position (shown in FIG. 8 ).
- valve 145 is operable to deliver a first quantity of coolant to the compressor when the sleeve 190 is positioned between the first position and the second position.
- the first quantity of coolant is substantially the same no matter the position of the sleeve 190 between the first position and the second position. However, the temperature of the coolant is varied.
- a second quantity of coolant is delivered to the compressor 125 . The second quantity is greater than the first quantity.
- the available cooled coolant flow area continues to increase.
- the quantity of coolant delivered to the compressor 125 varies between the first quantity and the second quantity as the sleeve 190 moves from the second position to the third position.
- the controller 150 employs a number of inputs or sensors 155 that can be monitored and used to determine what control signal 260 to provide to the motor 245 .
- the motor 245 can receive detailed positional signals that drive the motor 245 and lead screw 250 to a particular position, while other constructions employ a feedback loop to move the sleeve 190 in a desired direction between the first position and the third position.
- the controller 150 includes sensors 155 that monitor, among other parameters, compressor discharge temperature, oil inlet temperature, discharge air temperature, oil cooler discharge temperature, ambient air temperature and ambient air relative humidity. Any or all of these parameters can be used by the controller 150 to generate the control signal 260 that is then transmitted to the motor 245 .
- the signal 260 can move the motor 245 to position the sleeve 190 in a desired position or can simply move the sleeve 190 a desired distance in a desired direction. In this arrangement precise control of the position of the sleeve 190 and the temperature of the coolant leaving the valve 145 is possible.
- the arrangement of FIGS. 5 and 6 can measure ambient air conditions such as temperature, pressure, and/or relative humidity.
- the arrangement can also measure system pressure (e.g., at the oil separator, or compressor discharge pressure) and can use this data to calculate the minimum required temperature of the compressed mixture (i.e., the target airend/compressor discharge temperature) within the compressor 125 to inhibit the formation of condensation.
- This value is calculated at specific time intervals and is compared with the actual airend/compressor discharge temperature with any variation between the two being used to generate a signal to move the valve 145 in a required direction in an effort to nullify the difference.
- the valve 145 can than be adjusted to maintain the optimum required airend/compressor discharge temperature to assure that condensation does not form within the compressor 125 .
- the controller 150 controls the control valve 145 by first determining a target airend discharge temperature.
- the target airend discharge temperature is the minimum temperature at which condensation will not form in the compressor 125 . It is most efficient and cost effective to operate the compressor 125 using oil (coolant, lubricant, etc.) at a temperature as close to the target airend temperature as possible without going below the target airend temperature.
- This target temperature can be determined by using the inlet temperature and sump pressure.
- the target pressure set point is used instead of sump pressure because sump pressure is always changing, thereby making the target temperature less stable. To compensate for this, some constructions add a few degrees (e.g., 10 F) to the target airend discharge temperature.
- the relative humidity of the ambient air can be factored into the equation to calculate the target airend temperature.
- a constant relative humidity e.g. 90 percent
- the controller 150 operates to position the control valve 145 to maintain the airend discharge temperature at the target airend temperature.
- a PID control system is employed.
- the PID loop calculates the error between actual airend discharge temperature and target airend discharge temperature and uses that error with the rate of change to determine the number of steps and direction to move the control valve 145 .
- the controller 150 can make several comparisons between the airend discharge temperature and the target airend discharge temperature to determine how much to move the control valve 145 . This would be similar to a fuzzy logic control. The controller 150 would also look at the rate of change to calculate where the airend discharge temperature will be in the future (e.g., 5 seconds later).
- the controller 150 can maintain the current valve position.
- the controller 150 will make a series of comparisons to determine how much to move the valve 145 and in what direction to move the valve 145 .
- the controller 150 calculates a target injected coolant temperature (target airend discharge temp ⁇ (airend discharge temp ⁇ inlet coolant temp)).
- the controller 150 checks for the need to make an extreme movement in the control valve 145 .
- An extreme movement would be a move to the full third position (maximum flow of oil from the oil cooler to the airend) or a move to the first position (no flow of oil from the cooler, hot oil being bypassed directly to the airend). If the target injected coolant temperature is less than the temperature of the oil in the cooler, the control valve 145 will move to the third position. If the target injected coolant temperature is greater than the airend discharge temperature, the control valve 145 will move to the first position. If neither of the extreme movements is required, the controller 150 will calculate a normal movement of the valve 145 . The controller 150 will calculate a percentage of travel (e.g., 100 percent would move the valve 145 from the first position to the third position or vice/versa).
- the percentage can be calculated using the following formula:
- valves described and illustrated herein utilized linear or axial movement to move between the first position, the second position, and the third position.
- rotary valves or other valve arrangements could also be employed if desired.
- one construction employs a rotary valve that rotates a valve element to expose and cover two inlet ports.
- the stepper motor can directly drive the valve element or a gear train or other transmission arrangement can be employed.
- the invention should not be limited to the valve arrangements illustrated herein.
- the invention provides, among other things, a compressor system 20 including a control valve 40 operable to mechanically control the temperature and the flow of oil to a compressor 24 .
- a sleeve 76 of the valve 40 is provided with multiple apertures to provide cooled, non-cooled, or mixed oil in variable predetermined flow amounts to the compressor 24 based on a sensed condition of the compressor 24 .
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Remote Sensing (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
- The present invention relates to compressors. More particularly, the present invention relates to a mechanism for managing the flow and temperature of lubricant/coolant in a compressor system.
- A compressor system including, for example a contact-cooled rotary screw airend, injects a lubricating coolant (referred to herein as lubricant, coolant, oil, etc.) such as oil into the compression chamber to absorb the heat created by the compression of air and lubrication. The temperature of the oil must be maintained within a range to maximize its life and to minimize the formation of condensation within the compressor system. The amount and temperature of the injected oil also has an effect on the overall performance of the airend.
- In one construction, the invention provides a compressor system including a compressor including a gas inlet and a lubricant inlet, the compressor operable to compress a gas and discharge a mixed flow of compressed gas and lubricant. A valve housing includes a hot lubricant inlet, a cooled lubricant inlet, and a lubricant outlet connected to the lubricant inlet of the compressor and a sleeve is disposed within the valve housing and is movable between a first position and a second position. The sleeve selectively uncovers the hot lubricant inlet to selectively direct a hot lubricant to the lubricant outlet and selectively uncovers the cooled lubricant inlet to selectively direct a cooled lubricant to the lubricant outlet. The hot lubricant and cooled lubricant mixes at the lubricant outlet to define a bulk lubricant that is directed to the lubricant inlet of the compressor. A controller is operable to sense a parameter and generate a control signal at least partially in response to the sensed parameter and a motor is coupled to the sleeve and is operable to move the sleeve in response to the control signal. The movement of the sleeve is operable to vary the amount of hot lubricant admitted through the first aperture and to vary the amount of cooled lubricant admitted through the second aperture to control a temperature of the bulk lubricant.
- In another construction, the invention provides a thermal control valve for use in a lubricant flooded compressor system including a controller that generates a control signal. The thermal control valve includes a valve body including a hot coolant inlet, a cooled coolant inlet, a mixed coolant outlet, an actuator space, and a cylinder bore. A sleeve is positioned within the cylinder bore and is movable between a first position, a second position, and a third position, and an electrical actuator is at least partially disposed within the actuator space and is operable in response to the control signal to move the sleeve between the first position, the second position, and the third position.
- In yet another construction, the invention provides a method of controlling the temperature and quantity of a bulk flow of coolant to a lubricant flooded compressor in a compressor system. The method includes dividing a flow of hot coolant into a first flow of coolant and a second flow of coolant, cooling the first flow of coolant to produce a third flow of coolant, and directing the second flow of coolant and the third flow of coolant to a valve and discharging the bulk flow of coolant from the valve. The method also includes sensing a parameter of the compressor system and delivering the measured parameter to a controller, generating a control signal at least partially in response to the sensed parameter, and operating an electrical actuator at least partially in response to the control signal to configure the valve between a first position, a second position, and a third position. The bulk flow of coolant includes only coolant from the second flow of coolant when the valve is in the first position, the bulk flow of coolant includes only coolant from the third flow of coolant when the valve is in the second position, and the bulk flow of coolant includes a mixture of coolant from the second flow of coolant and the third flow of coolant when the valve is between the first position and the second position.
-
FIG. 1 is a schematic illustration of a compressor system including a flow and temperature control device; -
FIG. 2 is a section view of the flow and temperature control device ofFIG. 1 , in which a sleeve of the device is in a first position; -
FIG. 3 is a section view of the flow and temperature control device ofFIG. 1 , in which the sleeve is in a second position; -
FIG. 4 is a section view of the flow and temperature control device ofFIG. 1 , in which the sleeve is in a third position; -
FIG. 5 is a schematic illustration of another compressor system including a flow and temperature control device; -
FIG. 6 is a section view of the flow and temperature control device ofFIG. 5 in a first position; -
FIG. 7 is a section view of the flow and temperature control device ofFIG. 5 in a second position; and -
FIG. 8 is a section view of the flow and temperature control device ofFIG. 5 in a third position. - Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. The use of “including,” “comprising,” or “having” and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items. Unless specified or limited otherwise, the terms “mounted,” “connected,” “supported,” and “coupled” and variations thereof are used broadly and encompass both direct and indirect mountings, connections, supports, and couplings. Further, “connected” and “coupled” are not restricted to physical or mechanical connections or couplings.
-
FIG. 1 illustrates acompressor system 20 including a compressor airend (referred to herein simply as thecompressor 24, anoil separator 28, afilter 32, anoil cooler 36, and acontrol valve 40. Thecompressor 24 compresses air and oil to produce an air/oil mixture having an elevated pressure compared to the air and oil supplied to thecompressor 24. Although referred to throughout as “air” and “oil”, the specific type of gas being compressed and the specific type of lubricating coolant injected for compression with the gas is not critical to the invention, and may vary based on the type of compressor, the intended usage, or other factors. - The air and oil compressed within the
compressor 24 undergoes an increase in pressure and also temperature. The air/oil mixture is directed from thecompressor 24 to theoil separator 28 along an air/oil or “compressor outlet”flow path 44 as shown inFIG. 1 . Theoil separator 28 separates the air/oil mixture into two separate flows, a flow of compressed air that exits theoil separator 28 along a firstoutlet flow path 48, and a flow of oil that exits theoil separator 28 along a secondoutlet flow path 52. The compressed air in the firstoutlet flow path 48 can be supplied to any point-of-use device or to additional processing components or assemblies (not shown) of thecompressor system 20, such as a cooler, dryer, additional compressor(s), etc. The flow of oil in the secondoutlet flow path 52 from theoil separator 28 is directed to thefilter 32, which filters the oil of contaminants before it is returned to thecompressor 24. - From the
filter 32, the oil can be directed along one of two separate flow paths to thecontrol valve 40. Thefirst flow path 56 directs oil directly from thefilter 32 to thecontrol valve 40 without cooling the oil. Thesecond flow path 60 between thefilter 32 and thecontrol valve 40 directs oil through theoil cooler 36 that is positioned along thesecond flow path 60. Afirst portion 60A of thesecond flow path 60 is an oil cooler inlet flow path, and asecond portion 60B of thesecond flow 60 is an oil cooler outlet flow path. - Both of the
flow paths filter 32 lead to thecontrol valve 40, which has a single outlet leading to an oilsupply flow path 64 which supplies the oil back to thecompressor 24. By selective restriction of the flow through thevalve 40 from each of theflow paths valve 40 controls how much of the oil flowing through thefilter 32 is directed through thecooler 36 and how much is passed directly from thefilter 32 to thevalve 40. The firstoutlet flow path 56 from thefilter 32 is an inlet flow path to afirst inlet 70A of the valve 40 (FIG. 2 ). The secondoutlet flow path 60 from thefilter 32 is an inlet flow path to asecond inlet 70B of the valve 40 (FIG. 2 ). - As illustrated by
FIGS. 2-4 , thecontrol valve 40 includes abody 74, asleeve 76 movable within achamber 78 formed in thebody 74, and a thermal element oractuator 80 positioned at an end of thesleeve 76. Thefirst inlet 70A of thevalve 40 is in communication with a firstannular passage 84A that surrounds thesleeve 76. Thesecond inlet 70B of thevalve 40 is in communication with a secondannular passage 84B that surrounds thesleeve 76. The first and secondannular passages axis 88 of thevalve 40 defined by thechamber 78 and thesleeve 76. Thesleeve 76 includes afirst aperture 92A in selective communication with the firstannular passage 84A and asecond aperture 92B in selective communication with the secondannular passage 84B. Thesecond aperture 92B is larger than thefirst aperture 92A. Both of theapertures mixing chamber 96 defined by the inside of thesleeve 76, which is substantially hollow and cylindrical in the illustrated construction. Themixing chamber 96 is in communication with the valve outlet (and thus, the oil supply flow path 64) so that all of the oil supplied to the mixing chamber 96 (whether from thefirst inlet 70A or thesecond inlet 70B, or both) is directed to the oilsupply flow path 64. The oil transferred from themixing chamber 96 to the oilsupply flow path 64 through the valve outlet is referred to as the “bulk” flow of oil (or “combined” flow if oil that is received from bothinlets - Although the
first aperture 92A is illustrated as the only aperture for admitting oil into themixing chamber 96 from thefirst inlet 70A and thesecond aperture 92B is illustrated as the only aperture for admitting oil into themixing chamber 96 from thesecond inlet 70B, either one or both of the first andsecond apertures sleeve 76 to admit oil into themixing chamber 96 from multiple angles about the respectiveannular passages second apertures - Under most conditions of operation, the flow of oil to the
compressor 24 should not exceed a predetermined desired flow rate for maximum performance of thecompressor 24. Whenever thecompressor 24 is operating at a temperature below a first predetermined set point, thesleeve 76 is in a first position as shown inFIG. 2 . In the first position, thefirst aperture 92A is fully exposed to the firstannular passage 84A and thesecond aperture 92B is fully blocked from communication with the secondannular passage 84B. Thus, none of the flow of oil from thefilter 32 is supplied to thevalve 40 through theoil cooler 36. Rather, all of the flow of oil from thefilter 32 to thevalve 40 is provided through thefirst flow path 56, which is a flow path between thefilter 32 and thevalve 40 along which the oil is not actively cooled. The flow path may be a direct flow path between thefilter 32 and thevalve 40 as shown inFIG. 1 . Thefirst aperture 92A in thesleeve 76 is sized to provide a minimum required flow of oil when thesleeve 76 is in the first position. If thefirst aperture 92A is one of a plurality of apertures in communication with the firstannular passage 84A, the plurality of apertures as a whole are sized to provide a minimum required flow of oil when thesleeve 76 is in the first position. - When the
compressor 24 is operating at a temperature from the first predetermined set point up to a second predetermined set point, thesleeve 76 is gradually moved by the actuator 80 from the first position toward a second position (FIG. 3 ) as described in further detail below. In the second position, thesecond aperture 92B is partially exposed to the secondannular passage 84B and thefirst aperture 92A is fully blocked from communication with the firstannular passage 84A. Thus, none of the flow of oil from thefilter 32 is supplied to thevalve 40 directly through thefirst flow path 56. Rather, all of the flow of oil from thefilter 32 to thevalve 40 is provided through thesecond flow path 60, which directs the flow of oil through theoil cooler 36 before delivering it to thevalve 40. When thesleeve 76 is in the second position, the exposed portion of thesecond aperture 92B in thesleeve 76 provides a flow of cooled oil about equal to the minimum required flow (i.e., about equal to the flow of oil provided through thefirst aperture 92A when thesleeve 76 is in the first position). During the transition between the first position and the second position, portions of bothapertures annular passages supply flow path 64. The remaining portions of bothapertures sleeve 76, the overall flow (i.e., “combined flow” or “bulk flow”) of oil remains the same (i.e., about equal to the minimum required flow provided by thefirst aperture 92A in the first position) as the combined size of the portions of theapertures first aperture 92A. - When the
compressor 24 operates at a temperature above the second set point, thefirst aperture 92A remains closed and an increasingly greater portion of thesecond aperture 92B is gradually exposed to the secondannular passage 84B, and thus thesecond inlet 70B. Thus, only cooled oil is provided to the oilsupply flow path 64, similar to thesleeve 76 in the second position (FIG. 3 ). However, as thesleeve 76 moves from the second position (FIG. 3 ) toward a third position (FIG. 4 ), the overall flow of oil gradually increases, in excess of the minimum flow to provide additional cooling. Thesecond aperture 92B in thesleeve 76 is sized to provide a maximum flow of cooled oil when fully open (i.e., fully exposed to the secondannular passage 84B and thesecond inlet 70B when thesleeve 76 is in the third position). If thesecond aperture 92B is one of a plurality of apertures in communication with the secondannular passage 84B, the plurality of apertures as a whole are sized to provide a maximum flow of cooled oil when fully open. - The
actuator 80 includes asensor portion 80A and aprime mover portion 80B. Thesensor portion 80A is positioned in achamber 100 of thevalve body 74 that is remote from thechamber 78 that houses thesleeve 76. Thechamber 100, and thus thesensor portion 80A of theactuator 80, is in fluid communication with the oil or the air/oil mixture.FIG. 1 illustrates three possible paths A, B, C for fluidly coupling thechamber 100 with oil or the air/oil mixture. Each of the paths A, B, C represents a potential tubing or piping conduit for fluidly coupling thechamber 100 and thesensor portion 80A with a fluid of thecompressor system 20. The first path A couples thechamber 100 to the oilsupply flow path 64 at a position just upstream of thecompressor 24. Thus, thesensor portion 80A of theactuator 80 senses and reacts to the temperature of the oil just prior to injection into thecompressor 24. The second path B couples thechamber 100 to the air/oil mixture just downstream of thecompressor 24. Thus, thesensor portion 80A of theactuator 80 senses and reacts to the temperature of the air/oil mixture just after ejection from thecompressor 24. The third path C couples thechamber 100 to the oil just downstream of theoil separator 28. Thus, thesensor portion 80A of theactuator 80 senses and reacts to the temperature of the oil just after separation from the compressed air/oil mixture. - In some constructions where the
sensor portion 80A of theactuator 80 is fluidly coupled along path A ofFIG. 1 , thevalve 40 may be physically coupled to thecompressor 24 or positioned directly adjacent the oil inlet of thecompressor 24 where the oilsupply flow path 64 injects oil into thecompressor 24 so that thesensor portion 80A may be positioned directly in or adjacent to the compressor's oil inlet. In some constructions where thesensor portion 80A of theactuator 80 is fluidly coupled along path B ofFIG. 1 , thevalve 40 may be physically coupled to thecompressor 24 or positioned directly adjacent the outlet of thecompressor 24 where the compressed air/oil mixture is ejected from thecompressor 24 to theoutlet flow path 44 so that thesensor portion 80A may be positioned directly in or adjacent to the compressor's outlet. In some constructions where thesensor portion 80A of theactuator 80 is fluidly coupled along path C ofFIG. 1 , thevalve 40 may be physically coupled to or positioned directly adjacent the outlet of theoil separator 28 or the inlet of thefilter 32 so that thesensor portion 80A may be positioned directly in or adjacent to the separator outlet or the filter inlet. In other arrangements, thesensor portion 80A is remotely located and fluid is directed along one of the paths A, B, or C to thesensor portion 80A to allow thesensor portion 80A to sense the fluid temperature. The operation of thevalve 40 can be calibrated to control the temperature and the flow of oil based on the use of any one of the possible paths A, B, C. - In some constructions, the
actuator 80 may be a diaphragm-type thermal actuator available from Caltherm Corporation of Columbus, Ind. Thesensor portion 80A of theactuator 80 can include anexpansion material 104 contained within acup 108 and configured to move theprime mover portion 80B in a predetermined linear manner within the operating temperature range of the compressor 24 (i.e., the temperature range of the oil or air/oil mixture). In some constructions, theexpansion material 104 is wax which changes phase from solid to liquid within the operating temperature range of thecompressor 24. Theprime mover portion 80B of theactuator 80 can include apiston 112 that is coupled to adiaphragm 116 with aplug 120. Thediaphragm 116 cooperates with thecup 108 to define a chamber that contains theexpansion material 104. A housing orpiston guide 124 of theactuator 80 at least partially encloses thepiston 112 and theplug 120, and cooperates with thecup 108 to sandwich thediaphragm 116 in position. The exterior of thepiston guide 124 includesmale threads 128 for engaging theactuator 80 with a threadedaperture 132 of thevalve body 74. - Although the
actuator 80 is illustrated to include a linearly travelingprime mover portion 80B which actuates thesleeve 76 in a linear manner, a rotary type actuator can be substituted. Thevalve 40 can be reconfigured to selectively establish and terminate fluid communication between theinlets apertures sleeve 76 within thechamber 78 or a transmission device can be provided to convert rotative movement to linear movement. - In some constructions, the
actuator 80 may be an electro-mechanical actuator. In such constructions, thesensor portion 80A of theactuator 80 can be an electrical sensor configured to output an electrical signal. Theprime mover portion 80B can be an electrical motor that is configured to move thesleeve 76 back and forth in a calibrated manner between the positions described above, based on the fluid temperature sensed by thesensor portion 80A. Thesensor portion 80A and theprime mover portion 80B can be located remotely from each other or adjacent each other. - In operation, the
valve 40 operates to control the quantity and temperature of the oil delivered to thecompressor 24 to assure that the minimum and most efficient quantity of oil is delivered to thecompressor 24 unless the oil temperature demands additional flow. During compressor start-up, thecompressor 24 and the oil are both cold. The oil does not perform optimally at this lower temperature and it is desirable to heat the oil to a desired temperature range as quickly as possible. Thevalve 40 senses this low oil temperature and maintains the sleeve in the position illustrated inFIG. 2 . When in this position, none of the oil passes through theoil cooler 36. Rather, the oil continues to circulate through thecompressor 24, thereby heating the oil. As the oil temperature enters the optimal temperature range, thesleeve 76 begins moving to the right toward the position illustrated inFIG. 3 . Before reaching the position ofFIG. 3 , some of the oil entering the mixingchamber 96 is cooled enough to remove an amount of heat about equal to the heat added by thecompressor 24 during operation, thereby maintaining the oil within the desired range. As the load increases on thecompressor 24, thesleeve 76 eventually reaches the point illustrated inFIG. 3 . At this point, all of the oil must be cooled to maintain the oil within the desired temperature range and of the desired flow rate. As load increases further, the oil temperature increases above the desired range. Theactuator 80 senses this temperature and moves thesleeve 76 toward the position illustrated inFIG. 4 . In this position, thevalve 40 admits additional cooled oil to further cool thecompressor 24. Thus, the flow rate of oil to thecompressor 24 only increases above the minimum predetermined amount when the oil temperature dictates that additional flow is required. -
FIGS. 5-8 illustrate acompressor system 110 that includes a flow and temperature control device 115 that includes an electromechanical orelectrical actuator 120. As with the system ofFIGS. 1-4 , the system ofFIGS. 5 and 6 includes an oil-flooded compressor 125 (e.g., an oil-flooded screw compressor) that operates to produce a flow of compressed air. Oil is injected or drawn into thecompressor 125 to improve the seals within thecompressor 125, to lubricate the moving parts of thecompressor 125, and to remove some of the heat of compression generated during the compression process. Thesystem 110 also includes anoil separator 130 and an oil cooler 135 that are similar to those described with regard toFIGS. 1-4 and will not be described in detail. - The flow and temperature control device 115 includes a
flow divider 140, athermal control valve 145, acontroller 150, andvarious sensors 155. Theflow divider 140 is positioned to receive a flow ofhot oil 160 from theoil separator 130 and operates to divide that flow into afirst flow 165 directed to theoil cooler 135 and asecond flow 170 directed to thethermal control valve 145. Thefirst flow 165 is cooled in theoil cooler 135 and discharged from theoil cooler 135 as athird flow 175. Thethermal control valve 145 is positioned to receive thesecond flow 170 or hot coolant flow, and thethird flow 175 or cooled coolant flow and to discharge afourth flow 180 or bulk flow of coolant at a desired mixed temperature. The fourth flow ofcoolant 180 is injected into or drawn into thecompressor 125 through an oil filter to complete the oil flow cycle. - With reference to
FIG. 6 , thethermal control valve 145 ofFIG. 5 is illustrated as including avalve body 185, asleeve 190, and the electromechanical orelectrical actuator 120. Thevalve body 185 includes a cooledcoolant inlet 195, ahot coolant inlet 200, and amixed coolant outlet 205. In preferred constructions, the cooledcoolant inlet 195 includes a larger flow area than thehot coolant inlet 200. Thevalve body 185 also defines acylinder bore 210 sized to receive thesleeve 190 and anactuator space 215 sized to receive a portion of the electro/mechanical actuator 120. Acover 220 attaches to thevalve body 185 to seal at least a portion of theelectromechanical actuator 120 within thevalve 185 and to inhibit oil leakage from thevalve body 185. - The
sleeve 190 includes an outercylindrical surface 225 sized to closely fit within thecylinder bore 210. Thesleeve 190 is movable axially (as indicated by the arrow inFIG. 6 ) along the cylinder bore 210 and provides a seal there between. Thesleeve 190 includes acentral aperture 230 that receives a threadednut 235 and at least oneflow passage 240 that allows for the flow of oil through thesleeve 190. - The
electromechanical actuator 120 includes amotor 245 that is positioned within theactuator space 215 and that is operable to rotate alead screw 250 connected to themotor 245. In preferred constructions, astepper motor 245 is used to allow for the precise positioning of thelead screw 250. However, other constructions could employ a standard DC motor or other type of motor as required. - The
lead screw 250 threadably engages thenut 235 such that rotation of thelead screw 250 produces axial movement of thesleeve 190. In some constructions, a clutch mechanism (not shown) is positioned between themotor 245 and thelead screw 250 to reduce the likelihood of damage should movement of thesleeve 190 be inhibited. Apin 255 is fixedly positioned with respect to thevalve body 185 and engages thesleeve 190 to inhibit rotation of thesleeve 190 while still allowing free axial movement of thesleeve 190 in response to rotation of thelead screw 250. - In operation, a
signal 260 is provided to themotor 245 that results in operation of themotor 245. With thevalve 145 in the first position illustrated inFIG. 6 , only hot oil entering thevalve body 185 via thehot coolant inlet 200 flows out of thevalve 145 via themixed coolant outlet 205. This position represents one end of travel for thesleeve 190. As themotor 245 operates and rotates thelead screw 250, thesleeve 190 begins to move toward a second position (shown inFIG. 7 ). As thesleeve 190 moves to the right of the position inFIG. 6 , the cooledcoolant inlet 195 begins to uncover. Cooled oil is now able to flow into the space to the left of thesleeve 190 and through thesleeve 190 to themixed coolant outlet 205. It should be noted that as the cooledcoolant inlet 195 begins to uncover, thehot coolant inlet 200 begins to cover. In preferred constructions, the area of the cooledcoolant inlet 195 that is exposed or opened is equal to the area of thehot coolant inlet 200 that is covered or closed. With continued movement to the right, thesleeve 190 will eventually occupy the second position in which thehot coolant inlet 200 is completely covered, thereby blocking any flow of hot coolant, and the cooledcoolant inlet 195 is partially open. With thesleeve 190 in any position between the first position and the second position, a substantially equal amount of oil flows from thevalve body 185 via themixed coolant outlet 205. When in the first position, 100 percent of that oil is hot oil, when in thesecond position 100 percent of that oil is cooled oil, and when in a positioned between the first position and the second position, the flow is a mixture of hot coolant and cooled coolant. As thesleeve 190 moves further to the right, from the second position toward a third position (shown inFIG. 8 ), additional cooled coolant is able to flow through thevalve 145. Eventually, thesleeve 190 reaches the third position (shown inFIG. 8 ) from which additional travel to the right is inhibited. In this position, a greater quantity of coolant flows to thecompressor 125 than when thesleeve 190 is in the second position. Thus, thevalve 145 is operable to deliver a first quantity of coolant to the compressor when thesleeve 190 is positioned between the first position and the second position. The first quantity of coolant is substantially the same no matter the position of thesleeve 190 between the first position and the second position. However, the temperature of the coolant is varied. When thesleeve 190 is in the third position, a second quantity of coolant is delivered to thecompressor 125. The second quantity is greater than the first quantity. As thesleeve 190 moves from the second position toward the third position, the available cooled coolant flow area continues to increase. Thus, the quantity of coolant delivered to thecompressor 125 varies between the first quantity and the second quantity as thesleeve 190 moves from the second position to the third position. - With reference to
FIG. 5 , thecontroller 150 employs a number of inputs orsensors 155 that can be monitored and used to determine what control signal 260 to provide to themotor 245. In some constructions, themotor 245 can receive detailed positional signals that drive themotor 245 andlead screw 250 to a particular position, while other constructions employ a feedback loop to move thesleeve 190 in a desired direction between the first position and the third position. In the illustrated construction, thecontroller 150 includessensors 155 that monitor, among other parameters, compressor discharge temperature, oil inlet temperature, discharge air temperature, oil cooler discharge temperature, ambient air temperature and ambient air relative humidity. Any or all of these parameters can be used by thecontroller 150 to generate thecontrol signal 260 that is then transmitted to themotor 245. Thesignal 260 can move themotor 245 to position thesleeve 190 in a desired position or can simply move the sleeve 190 a desired distance in a desired direction. In this arrangement precise control of the position of thesleeve 190 and the temperature of the coolant leaving thevalve 145 is possible. - The arrangement of
FIGS. 5 and 6 can measure ambient air conditions such as temperature, pressure, and/or relative humidity. The arrangement can also measure system pressure (e.g., at the oil separator, or compressor discharge pressure) and can use this data to calculate the minimum required temperature of the compressed mixture (i.e., the target airend/compressor discharge temperature) within thecompressor 125 to inhibit the formation of condensation. This value is calculated at specific time intervals and is compared with the actual airend/compressor discharge temperature with any variation between the two being used to generate a signal to move thevalve 145 in a required direction in an effort to nullify the difference. Thevalve 145 can than be adjusted to maintain the optimum required airend/compressor discharge temperature to assure that condensation does not form within thecompressor 125. Other designs must operate at a higher temperature that corresponds to the worst case conditions (e.g., highest ambient air temperature, highest relative humidity, and the highest system discharge pressure) to assure that condensation does not form in thecompressor 125. The operation at a temperature higher than required can reduce the life of the coolant and thecompressor 125. This is particularly important withvariable speed compressors 125, such as those disclosed herein because the operating conditions can vary greatly when compared to the worst case scenario. - In one particular construction, the
controller 150 controls thecontrol valve 145 by first determining a target airend discharge temperature. The target airend discharge temperature is the minimum temperature at which condensation will not form in thecompressor 125. It is most efficient and cost effective to operate thecompressor 125 using oil (coolant, lubricant, etc.) at a temperature as close to the target airend temperature as possible without going below the target airend temperature. This target temperature can be determined by using the inlet temperature and sump pressure. In one application, the target pressure set point is used instead of sump pressure because sump pressure is always changing, thereby making the target temperature less stable. To compensate for this, some constructions add a few degrees (e.g., 10 F) to the target airend discharge temperature. - If a relative humidity sensor is employed, the relative humidity of the ambient air can be factored into the equation to calculate the target airend temperature. In constructions that do not employ a relative humidity sensor, a constant relative humidity (e.g., 90 percent) can be assumed. Once the target airend temperature is calculated, the
controller 150 operates to position thecontrol valve 145 to maintain the airend discharge temperature at the target airend temperature. - There are multiple control methods for controlling the
valve 145. In one construction, a PID control system is employed. The PID loop calculates the error between actual airend discharge temperature and target airend discharge temperature and uses that error with the rate of change to determine the number of steps and direction to move thecontrol valve 145. In another construction, thecontroller 150 can make several comparisons between the airend discharge temperature and the target airend discharge temperature to determine how much to move thecontrol valve 145. This would be similar to a fuzzy logic control. Thecontroller 150 would also look at the rate of change to calculate where the airend discharge temperature will be in the future (e.g., 5 seconds later). If the actual discharge temperature is within a desired range (e.g., plus/minus 1 deg) of the target temperature and the estimated airend discharge temperature in the future is within a second desired range (e.g., plus/minus 1 deg of the target temperature), thecontroller 150 can maintain the current valve position. - However, if the system is outside of these desired ranges, the
controller 150 will make a series of comparisons to determine how much to move thevalve 145 and in what direction to move thevalve 145. - First, the
controller 150 calculates a target injected coolant temperature (target airend discharge temp−(airend discharge temp−inlet coolant temp)). Next, thecontroller 150 checks for the need to make an extreme movement in thecontrol valve 145. An extreme movement would be a move to the full third position (maximum flow of oil from the oil cooler to the airend) or a move to the first position (no flow of oil from the cooler, hot oil being bypassed directly to the airend). If the target injected coolant temperature is less than the temperature of the oil in the cooler, thecontrol valve 145 will move to the third position. If the target injected coolant temperature is greater than the airend discharge temperature, thecontrol valve 145 will move to the first position. If neither of the extreme movements is required, thecontroller 150 will calculate a normal movement of thevalve 145. Thecontroller 150 will calculate a percentage of travel (e.g., 100 percent would move thevalve 145 from the first position to the third position or vice/versa). - The percentage can be calculated using the following formula:
-
(airend discharge temperature in future−target airend discharge temperature)/(airend discharge temperature−cooler output temperature). - If this value is positive, the
valve 145 will move toward the third position. If it is negative, thevalve 145 will move toward the first position. In a preferred construction, 1 percent=71 steps in thestepper motor 245. Thus, the calculated percentage is multiplied by 71 and themotor 245 moves that many steps in the desired direction. These movements are calculated periodically (e.g., every 5 seconds). - It should be noted that the valves described and illustrated herein utilized linear or axial movement to move between the first position, the second position, and the third position. However, rotary valves or other valve arrangements could also be employed if desired. For example, one construction employs a rotary valve that rotates a valve element to expose and cover two inlet ports. In this construction, the stepper motor can directly drive the valve element or a gear train or other transmission arrangement can be employed. Thus, the invention should not be limited to the valve arrangements illustrated herein.
- Thus, the invention provides, among other things, a
compressor system 20 including acontrol valve 40 operable to mechanically control the temperature and the flow of oil to acompressor 24. Asleeve 76 of thevalve 40 is provided with multiple apertures to provide cooled, non-cooled, or mixed oil in variable predetermined flow amounts to thecompressor 24 based on a sensed condition of thecompressor 24. Various features and advantages of the invention are set forth in the following claims.
Claims (20)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/580,291 US9518579B2 (en) | 2010-01-22 | 2010-10-28 | Oil flooded compressor having motor operated temperature controlled mixing valve |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
USPCT/US2010/027132 | 2010-01-22 | ||
PCT/US2010/021732 WO2011090482A2 (en) | 2010-01-22 | 2010-01-22 | Compressor system including a flow and temperature control device |
PCT/US2010/054495 WO2011090528A1 (en) | 2010-01-22 | 2010-10-28 | Compressor system including a flow and temperature control device |
US13/580,291 US9518579B2 (en) | 2010-01-22 | 2010-10-28 | Oil flooded compressor having motor operated temperature controlled mixing valve |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2010/021732 Continuation-In-Part WO2011090482A2 (en) | 2010-01-22 | 2010-01-22 | Compressor system including a flow and temperature control device |
Publications (3)
Publication Number | Publication Date |
---|---|
US20130058799A1 US20130058799A1 (en) | 2013-03-07 |
US20160138594A9 true US20160138594A9 (en) | 2016-05-19 |
US9518579B2 US9518579B2 (en) | 2016-12-13 |
Family
ID=47757208
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/580,291 Active 2032-06-16 US9518579B2 (en) | 2010-01-22 | 2010-10-28 | Oil flooded compressor having motor operated temperature controlled mixing valve |
Country Status (1)
Country | Link |
---|---|
US (1) | US9518579B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150285264A1 (en) * | 2014-04-07 | 2015-10-08 | Union Pacific Railroad Company | Air compressor with self contained cooling system |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6236596B2 (en) * | 2013-02-26 | 2017-11-29 | ナブテスコオートモーティブ株式会社 | Oil separator |
US9322401B2 (en) * | 2014-02-10 | 2016-04-26 | General Electric Company | Linear compressor |
JP6679324B2 (en) * | 2016-01-29 | 2020-04-15 | 日本サーモスタット株式会社 | Valve device with fail-safe mechanism |
US10036325B2 (en) * | 2016-03-30 | 2018-07-31 | General Electric Company | Variable flow compressor of a gas turbine |
EP3425247A1 (en) * | 2017-07-07 | 2019-01-09 | Continental Automotive GmbH | Valve for mixing two gas flows |
BE1026208B1 (en) * | 2018-04-12 | 2019-11-13 | Atlas Copco Airpower Naamloze Vennootschap | Oil-injected screw compressor device |
CN109737226A (en) * | 2019-03-01 | 2019-05-10 | 北京瑞莱博石油技术有限公司 | A kind of high temperature and pressure number back pressure device |
Family Cites Families (36)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2540629A (en) | 1946-01-04 | 1951-02-06 | Glenn L Martin Co | Oil temperature control valve and cooler |
US2480676A (en) | 1946-12-04 | 1949-08-30 | Young Radiator Co | Temperature-regulating valve mechanism |
US2975973A (en) | 1957-11-27 | 1961-03-21 | United Aircraft Prod | Thermostatic valve |
DE1149368B (en) | 1958-10-06 | 1963-05-30 | Gea Luftkuehler Happel Gmbh | Cross-flow tube heat exchanger with precautions against mixing of the two heat-exchanging media |
US2988280A (en) | 1958-11-26 | 1961-06-13 | United Aircraft Prod | Thermostatic valve |
US3721386A (en) * | 1970-10-23 | 1973-03-20 | J Brick | Temperature-volume controlled mixing valve |
US3865514A (en) * | 1973-07-25 | 1975-02-11 | Sperry Rand Corp | Power transmission |
GB1501413A (en) | 1974-06-06 | 1978-02-15 | Sullair Europ Corp | Flow regulating valve assemblies |
US4019678A (en) * | 1974-06-17 | 1977-04-26 | United Aircraft Products, Inc. | Mixing valve |
US4190198A (en) | 1978-04-12 | 1980-02-26 | Lockhart Industries, Inc. | Oil cooler bypass valve actuating means |
US4195774A (en) | 1979-01-04 | 1980-04-01 | United Technologies Corporation | Dual in-line valve construction |
US4398662A (en) | 1981-10-16 | 1983-08-16 | Modine Manufacturing Company | Oil temperature regulator |
US4431390A (en) * | 1981-10-23 | 1984-02-14 | Dresser Industries, Inc. | Condensation control apparatus for oil-flooded compressors |
DE3238241A1 (en) | 1981-12-17 | 1983-07-21 | Gebrüder Sulzer AG, 8401 Winterthur | DEVICE FOR THE OIL SUPPLY OF A SCREW COMPRESSOR |
JPS6025020Y2 (en) | 1982-03-31 | 1985-07-26 | アイシン精機株式会社 | thermo valve |
US4537346A (en) | 1983-10-17 | 1985-08-27 | Standard-Thomson Corporation | Fail-safe oil flow control apparatus |
US5094426A (en) * | 1990-04-27 | 1992-03-10 | John Zajac | Metering valve assembly |
US5052424A (en) * | 1990-07-16 | 1991-10-01 | Eaton Corporation | Electrically operated servo actuator with automatic shut off |
US5318151A (en) * | 1993-03-17 | 1994-06-07 | Ingersoll-Rand Company | Method and apparatus for regulating a compressor lubrication system |
CH690925A5 (en) | 1996-03-18 | 2001-02-28 | Ostaco Ag | Manifold valve with flow meter. |
US5803354A (en) | 1996-06-17 | 1998-09-08 | Benedict; Charles E. | Temperature responsive fluid flow controllers |
DE29619609U1 (en) | 1996-11-12 | 1997-01-16 | Behr Thermot-Tronik Gmbh & Co., 70806 Kornwestheim | Thermostatic valve |
US5988514A (en) | 1998-01-13 | 1999-11-23 | Huang; Tien-Tsai | Apparatus for controlling fluid temperature |
JP4262346B2 (en) | 1999-01-27 | 2009-05-13 | 本田技研工業株式会社 | thermostat |
JP2000346215A (en) | 1999-06-02 | 2000-12-15 | Hokuetsu Kogyo Co Ltd | Variable flow bypass valve |
US6405932B1 (en) | 2001-03-01 | 2002-06-18 | Strahman Valves, Inc. | Hot water temperature control valve system |
US7299994B2 (en) | 2001-08-31 | 2007-11-27 | Huron, Inc. | Oil cooler bypass valve |
DE10153459B9 (en) | 2001-10-30 | 2004-09-09 | Kaeser Kompressoren Gmbh | Arrangement for controlling the flow of cooling fluid in compressors |
US6575707B2 (en) * | 2001-11-05 | 2003-06-10 | Ingersoll-Rand Company | Air compressor having thermal valve |
EP1451469B1 (en) | 2001-12-07 | 2008-10-08 | Compair UK Limited | Lubricant-cooled gas compressor |
US6915958B2 (en) | 2002-05-22 | 2005-07-12 | Tesma International Inc. | Linear proportional valve |
CA2431717C (en) | 2002-12-10 | 2012-10-16 | Tesma International Inc. | Proportional valve with linear actuator |
GB0307283D0 (en) | 2003-03-28 | 2003-05-07 | Microgen Energy Ltd | A splitter valve |
US7490662B2 (en) | 2004-10-13 | 2009-02-17 | Visteon Global Technologies, Inc. | Integrated thermal bypass valve |
US7762789B2 (en) | 2007-11-12 | 2010-07-27 | Ingersoll-Rand Company | Compressor with flow control sensor |
CN102803730B (en) * | 2010-01-22 | 2015-11-25 | 英格索尔-兰德公司 | Comprise the compressor assembly of flow and temperature control apparatus |
-
2010
- 2010-10-28 US US13/580,291 patent/US9518579B2/en active Active
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150285264A1 (en) * | 2014-04-07 | 2015-10-08 | Union Pacific Railroad Company | Air compressor with self contained cooling system |
Also Published As
Publication number | Publication date |
---|---|
US20130058799A1 (en) | 2013-03-07 |
US9518579B2 (en) | 2016-12-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2526298B1 (en) | Compressor system including a flow and temperature control device | |
US9518579B2 (en) | Oil flooded compressor having motor operated temperature controlled mixing valve | |
US9360011B2 (en) | System including high-side and low-side compressors | |
US8234877B2 (en) | Compressor discharge valve providing freeze and charge migration protection | |
RU2627745C2 (en) | Fluid medium loop in the turbomachine | |
CN106246538B (en) | The regulating valve of pump with regulating device and the delivered volume for adjusting pump | |
US8029248B2 (en) | Integrated coolant pumping module | |
US11415136B2 (en) | Screw compressor | |
US6139280A (en) | Electric switch gauge for screw compressors | |
WO2013175817A1 (en) | Screw compressor | |
US7762789B2 (en) | Compressor with flow control sensor | |
US9341093B2 (en) | Control valve | |
CN116802390A (en) | Heat exchanger mounted in a turbine engine cavity | |
KR20170118126A (en) | Method and apparatus for controlling the oil temperature of an oil-injected compressor plant or vacuum pump | |
CN114198828A (en) | Air suspension unit system and control method | |
US20040112679A1 (en) | System and method for lubricant flow control in a variable speed compressor package | |
US9581237B2 (en) | Transmission fluid expansion reservoir | |
CN212431383U (en) | Water chilling unit | |
US9828998B2 (en) | Screw compressor | |
CN109964037A (en) | Screw compressor system for commercial vehicle | |
JP2004309081A (en) | Expansion valve and its control method | |
CN114575957B (en) | Oil quantity adjusting method of diesel engine lubricating oil duct assembly | |
CN116917625A (en) | ETXV type direct discharge injection compressor | |
CN110678654A (en) | Compressor system with adjustable and/or controllable temperature monitoring device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: INGERSOLL-RAND COMPANY, NEW JERSEY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SCARPINATO, PAUL A.;SREEDHARAN, SUDHIR;MEHAFFEY, JAMES D.;AND OTHERS;SIGNING DATES FROM 20110315 TO 20110323;REEL/FRAME:028823/0144 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
AS | Assignment |
Owner name: INGERSOLL-RAND INDUSTRIAL U.S., INC., NORTH CAROLI Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:INGERSOLL-RAND COMPANY;REEL/FRAME:051315/0108 Effective date: 20191130 |
|
AS | Assignment |
Owner name: CITIBANK, N.A., AS ADMINISTRATIVE AGENT AND COLLATERAL AGENT, DELAWARE Free format text: SECURITY INTEREST;ASSIGNORS:CLUB CAR, LLC;MILTON ROY, LLC;HASKEL INTERNATIONAL, LLC;AND OTHERS;REEL/FRAME:052072/0381 Effective date: 20200229 |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1551); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 4 |
|
AS | Assignment |
Owner name: INGERSOLL-RAND INDUSTRIAL U.S., INC., NORTH CAROLINA Free format text: RELEASE OF PATENT SECURITY INTEREST;ASSIGNOR:CITIBANK, N.A., AS COLLATERAL AGENT;REEL/FRAME:067401/0811 Effective date: 20240510 Owner name: HASKEL INTERNATIONAL, LLC, CALIFORNIA Free format text: RELEASE OF PATENT SECURITY INTEREST;ASSIGNOR:CITIBANK, N.A., AS COLLATERAL AGENT;REEL/FRAME:067401/0811 Effective date: 20240510 Owner name: MILTON ROY, LLC, NORTH CAROLINA Free format text: RELEASE OF PATENT SECURITY INTEREST;ASSIGNOR:CITIBANK, N.A., AS COLLATERAL AGENT;REEL/FRAME:067401/0811 Effective date: 20240510 |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1552); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 8 |