WO2000035329A2 - Equipement de nettoyage portable, a haute pression et haute temperature - Google Patents

Equipement de nettoyage portable, a haute pression et haute temperature Download PDF

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Publication number
WO2000035329A2
WO2000035329A2 PCT/US1999/029770 US9929770W WO0035329A2 WO 2000035329 A2 WO2000035329 A2 WO 2000035329A2 US 9929770 W US9929770 W US 9929770W WO 0035329 A2 WO0035329 A2 WO 0035329A2
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WO
WIPO (PCT)
Prior art keywords
fluid
heat exchanger
engine
cleaning fluid
cleaning
Prior art date
Application number
PCT/US1999/029770
Other languages
English (en)
Other versions
WO2000035329A9 (fr
WO2000035329A3 (fr
Inventor
Shawn L. York
Original Assignee
York Shawn L
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 York Shawn L filed Critical York Shawn L
Priority to AU21854/00A priority Critical patent/AU2185400A/en
Publication of WO2000035329A2 publication Critical patent/WO2000035329A2/fr
Publication of WO2000035329A3 publication Critical patent/WO2000035329A3/fr
Publication of WO2000035329A9 publication Critical patent/WO2000035329A9/fr
Priority to US09/868,350 priority patent/US6675437B1/en

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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L11/00—Machines for cleaning floors, carpets, furniture, walls, or wall coverings
    • A47L11/40—Parts or details of machines not provided for in groups A47L11/02 - A47L11/38, or not restricted to one of these groups, e.g. handles, arrangements of switches, skirts, buffers, levers
    • A47L11/4011—Regulation of the cleaning machine by electric means; Control systems and remote control systems therefor
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L11/00—Machines for cleaning floors, carpets, furniture, walls, or wall coverings
    • A47L11/34—Machines for treating carpets in position by liquid, foam, or vapour, e.g. by steam
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L11/00—Machines for cleaning floors, carpets, furniture, walls, or wall coverings
    • A47L11/40—Parts or details of machines not provided for in groups A47L11/02 - A47L11/38, or not restricted to one of these groups, e.g. handles, arrangements of switches, skirts, buffers, levers
    • A47L11/408—Means for supplying cleaning or surface treating agents
    • A47L11/4083—Liquid supply reservoirs; Preparation of the agents, e.g. mixing devices
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L11/00—Machines for cleaning floors, carpets, furniture, walls, or wall coverings
    • A47L11/40—Parts or details of machines not provided for in groups A47L11/02 - A47L11/38, or not restricted to one of these groups, e.g. handles, arrangements of switches, skirts, buffers, levers
    • A47L11/408—Means for supplying cleaning or surface treating agents
    • A47L11/4088—Supply pumps; Spraying devices; Supply conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
    • B60P3/00—Vehicles adapted to transport, to carry or to comprise special loads or objects
    • B60P3/14—Vehicles adapted to transport, to carry or to comprise special loads or objects the object being a workshop for servicing, for maintenance, or for carrying workmen during work
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices

Definitions

  • This invention relates to carpet cleaning generally, and more particularly to portable, self-contained pumping and heating systems for carpet cleaning. More particularly still, the invention relates to a cleaning system that uses heated cleaning solution where the heat is derived from secondary heat of a primary heat-generating engine, which also provides mechanical force used to deliver and remove the cleaning solution during cleaning.
  • carpets unlike other fabric in household use, is exposed to an enormous amount of foreign matter such as dirt, grass, leaves, sand, dust, mud, animal hair, and spilled food.
  • the problem is compounded by both the permanent (e.g. wall-to-wall) installation of carpet and the length of fibers found in many carpets.
  • Permanent (e.g. wall-to-wall) installation requires on-site cleaning. Bundles or yarns comprised of many fibers tend to capture or adhere to soiling, such as particulate matter. Conventional washing and cleaning processes remain ineffective.
  • Hot- ater extraction methods have been developed to facilitate carpet-cleaning.
  • Hot water may actually include liquid water; saturated, two-phase, steam and water droplets; or superheated steam. The latter is not commonly relied upon, since it is typically hotter than the distortion temperature of synthetic fibers. Moreover, the energy requirements for the phase change to steam simply cannot be met by most heating plants for the purpose.
  • water is heated, pressurized, supplemented with chemical cleaning additives and applied to carpet in order to dissolve or release soils and particulates and to suspend the resulting matter in the water (e.g. solvent, carrier, etc.).
  • a "vacuum” system then extracts the dissolved soils, suspended particulates, and water out of the fibers.
  • the water and air flows drawn by the vacuum system entrain the entire mixture, carrying it to a holding tank.
  • the water should preferably be at about 210° F at the carpet surface. When water is substantially cooler, machine operators compensate by increasing the pressure, chemical content, or quantity of the cleaning fluid, or some combination thereof.
  • Pressure translates to fluid velocity, which affects penetration of fiber bundles (yarns) by the fluid. Higher velocity fluid may also better strip soils from fibers mechanically. Mechanical agitation may improve rates of dissolving by a solvent, and may reduce boundary layers near fibers for improved chemical reaction.
  • Water-based carpet cleaning may apply or leave excess water standing in carpets, or retained by surface tension therein. Excess water tends to damage carpets by soaking into areas over time, causing over- wetting. Over-wetted textiles often show signs of reduced strength, mildew, and delamination, a process in which the carpet takes on a rippled appearance due to separation of primary and secondary backings.
  • Excessive concentrations of chemicals may increase reaction rates for dissolving or removing soils, by removing binding agents adhering them to carpets.
  • Alkaline chemicals may remove or discolor pigments in carpet, remove stain- resisting treatments, void manufacturers' warranties, and attack fibers, glues, or backing materials ' ' structural integrity.
  • cleaning chemicals are known to leave residues that cause carpet to re-soil at an accelerated rate by adhering to soiling materials.
  • Increased cleaning fluid temperatures increase chemical reaction rates, allowing textile cleaners to decrease the concentration of chemicals, the fluid pressure, and the fluid quantity used in the cleaning process.
  • Increasing the cleaning fluid temperature may change the thermodynamics of the application and drying process. For example, if less time is required to apply a high- speed spray of droplets, less soaking can occur. Also, the thermodynamic quality of the water in a high pressure jet may be increased, providing increased steam to break up water into smaller droplets, and to augment the air flow moving away form the cleaned carpet yarns. Less water residence time, and smaller particle sizes for water droplets result in entrainment of more liquid in the vacuum drawn pickup line. Likewise, higher energy content, less water, and less residence time means faster drying time. Thus, the risk of de-lamination, mold growth, tensile strength loss, and other ill effects of moisture is reduced. Instead, carpet is left with low moisture and a more neutral pH.
  • cleaning fluid temperatures must not only be high, but consistent. Since the effectiveness of any hot-water extraction method depends greatly on the fluid temperature, an inconsistent fluid temperature results in a carpet that appears patchy because it is cleaner in some places than in others. In addition, temperatures in excess of 240° F can permanently yield synthetic fibers, thereby causing fiber memory loss and ruining the pile texture of carpet.
  • Truck-mounted textile cleaning equipment may be of an "integral” type, also known as “direct drive” type (dependent on the automotive power plant for energy), or of a “slide-in” type (standalone). Each has its own set of performance and maintenance problems.
  • Direct drive systems marketed today rely exclusively on heat extracted from the engine coolant (radiator water). The result is that the best heat exchangers and transfer times do not produce a maximum cleaning fluid temperature above 195 ° F in the heat exchanger, which temperature is substantially reduced by the time fluid reaches a carpet surface.
  • Integrated, direct drive systems rely on the coolant of an internal combustion engine to provide heat to the cleaning fluid. They rely on the fan belts of the vehicle engine for mechanical power. Such systems can provide comparatively high vacuum power, but temperatures typically range from 100 ° to 170 ° F at the carpet surface. Since they take energy from the coolant that passes through the vehicle radiator, they provide an inconsistent, and still too low fluid temperature at the carpet surface. A lot of energy is available from the engine coolant, but at a low thermodynamic availability.
  • the fan belt from a typical utility van drives a shaft running from the vehicle engine, between the vehicle seats, to the bed of the van to power the pump and vacuum equipment.
  • large, high torque (e.g. V-8), gasoline-powered engines were not designed to run stationary at 1500 RPM for hours at a time just to drive the fan belt while carpet cleaners perfo ⁇ ri their work.
  • gasoline engines idling for lengthy periods of time tend to create enormous amounts of radiant heat that which destroys electrical components and leads to reliability problems.
  • the integrated, truck -mounted systems can also dump substantial waste heat and vibrational energy into the vehicle.
  • Standard-in machines typically depend on a small gasoline engine to power equipment, all installed in a common utility vehicle such as a van. Process heat is taken from the heat rejected by the engine. As v/ith direct-drive systems, the equipment compartment (bed) and cab of a van become very hot when the engine is run in stationary mode with only the confined, standard, inadequate cooling system The unit is also nearly impossible to isolate mechanically from the body of the vehicle. As a practical matter, slide-in systems literally self-destruct during a comparatively short and very unreliable life.
  • Stationary (e.g. slide-in) engines are not designed and operated at the efficiencies common to current automotive power plants.
  • the engines of slide-in units have been selected to have thermal outputs to support higher temperatures at the required water flow rates, the fuel efficiency is still extremely poor, and the environmental heat rejection problem is even more serious.
  • the exhaust temperature for a gasoline internal combustion engine maybe as high as 1400° F.
  • the temperature difference above that of the cleaning fluid, and thus the thermodynamic availability, is initially adequate.
  • the mass flow rate of exhaust is very low, so overall heat transferred to the cleaning fluid is also low.
  • Auxiliary heating is a method tried for improving performance of direct-drive systems. Despite their increased mechanical power, currently available direct drive machines remain incapable of maintaining a consistently high cleaning fluid temperature. Use of external heating devices may raise the top-end temperature.
  • auxiliary burners such as propane, kerosene, diesel, and electric burners, has been declining in recent years.
  • Direct drive, co-generation machines lack any safe, reliable, and convenient method for conveying the cleaning fluid and the exhaust through a heat exchanger.
  • Bringing an engine exhaust line into an enclosed rear cabin of a vehicle, together with the pumping equipment and cleaning fluid, is dangerous.
  • An inevitable opening or leak in the exhaust pipe would fill the vehicle with exhaust gases, which are toxic, corrosive, and possible even highly combustible.
  • extending a cleaning fluid line outside the cabin of a van or other service vehicle to access and exhaust line is not a viable solution. Any water-based cleaning fluid left in the line in cold weather will freeze when the engine is not running, bursting the line.
  • Exhaust gases from an internal combustion engine vary significantly in temperature due to changes in the combustion rate and temperature of the engine.
  • the amount of heat transferred by exhaust must be distributed over some amount of cleaning fluid.
  • Cleaning fluid moving comparatively slowly through a heat exchanger during a time of less use of such fluid by an operator will absorb more heat and exit the exchanger at a comparatively higher temperature. If an operator stops to move furniture, reposition equipment, or make a dry pass to vacuum up excess cleaning fluid, the flow rate of cleaning fluid through a washing plant will slow or stop. The resulting temperatures and pressures can harm carpet, destroy equipment, and cause personal injury.
  • a failure in a temperature regulating mechanism can allow the fluid temperature to continue rising to dangerous levels.
  • the electrical and electronic control elements such as sensors, solenoids, and valves, used to detect excessive temperatures and bleed off cleaning fluid or shut down the system are prone to failure
  • Control orifices can be very small and are subject to clogging from calcium, lime, and magnesium deposits from the cleaning fluid.
  • the high temperatures involved accelerate the buildup of deposits and can damage the wire coils and insulation, causing failure in items such as solenoids. Valve failures can cause catastrophic failure of the entire system.
  • the system needs to be freezing-safe in virtually all weather, yet not damage vehicle structure or electronics. Operator safety is also needed, against exposure to exhaust gases, or pressure failures.
  • a reliable PTO drive train is needed for transferring mechanical energy, but more importantly for engaging and disengaging frequently and re ⁇ ably for many duty cycles.
  • a transportable cleaning system that utilizes a direct drive washing plant with an intermediate, nonfreezing fluid to transfer heat between engine exhaust and a cleaning fluid.
  • a failsafe thermostat device regulates the temperature of the cleaning fluid without interrupting the cleaning process or wasting cleaning fluid.
  • a PTO for mechanical power can run full time at the engine or transfer case without gear engagement and disengagement. Instead, a PTO clutch is engageable downstream from the transmission or transfer case in the power tram. Thus high, positive displacement, mechanical power can be output reliably from the transmission or transfer case, not jury-rigged from the fan belt. The downstream positioning of the clutch permits the PTO to be continuously engaged, thereby avoiding the shifting frequency problems that might otherwise be encountered. Also, any constantly rotating PTO shaft provided in a production truck can be accessed and used.
  • an apparatus and method in accordance with the present invention may include a diesel vehicle engine to power pumps and blowers pressurizing cleaning fluid and air supplies.
  • a hydraulically or otherwise actuated clutch may provide access to a full-time PTO shaft.
  • Multiple heat exchangers, and multiple loop heat exchangers, retrieving heat from both exhaust flows and engine coolant, provide comparatively higher temperatures for heating cleaning fluids, such as water-based fluids. The higher, cleaning-fluid temperatures can be obtained through higher thermodynamic availability, more net energy available, higher heating fluid temperatures, improved heat- exchange staging, and improved heat transfer efficiencies.
  • the apparatus and method of the present invention provide delivery of necessary quantities of heated water, or even- superheated (pressurized and heated over ambient boiling point) water, in sufficient quantities to support a carpet cleaning tool (e.g. wand), at temperatures greater than 195 ° F in the line and 170° F at the carpet. Temperature may approach the ambient boiling point, which may even be exceeded by design, if desired, in the pressurized cleaning fluid.
  • a carpet cleaning tool e.g. wand
  • the enhanced vacuum power of the current invention allows multiple operators with separate lines and wands to work from a single supply system on one truck. This decreases cleaning time, cuts labor costs, and minimizes inconvenience to customers. Substantially lower repair costs and downtime flow from a simpler design.
  • the current invention provides a 'multi-function" (e.g. steam cleaning and pressure washing) machine in accordance with new and newly proposed restrictions on hazardous waste dumping, promulgated by the EPA and other governmental agencies.
  • Figure 2 is a perspective, cutaway, rear-quarter- wew of a truck equipped with one embodiment of an apparatus in accordance with the invention
  • Figure 3 is a perspective, cutaway, left, rear-quarter view of the truck of Figure 1, shown from a different angle with coiled vacuum tubing stored in the cargo compartment;
  • Figure 4 is a perspective view of one embodiment of an engine system suitable for the truck and apparatus of Figure 1 ;
  • Figure 5 is a perspective view of one embodiment of a fluid d ⁇ ve system suitable for the apparatus of Figure 1 ;
  • Figure 6 is a perspective view of one embodiment of an intermediate thermal fluid heating system suitable for the apparatus of Figure 1 ,
  • Figure 7 is a perspective view of one embodiment of a fluid storage and preheat system suitable for the apparatus of Figure 1 ;
  • Figure 8 si a perspective view of one embodiment of a fluid top heating system suitable for the apparatus of Figure 1 ;
  • Figure 9 is a perspective view of one embodiment of a waste storage system suitable for the apparatus of Figure 1 ;
  • Figure 10 is a schematic block diagram, a flowchart showing one possible flow of cleaning fluid in accordance with the invention.
  • Figure 1 1 is a schematic block diagram or flowchart showing one possible flow of air in accordance with the invention
  • Figure 12 is a schematic diagram or flowchart showing one possible flow of energy from fuel into the coolant, piston, and exhaust of an internal combustion engine, in accordance with the invention
  • Figure 13 is a schematic block diagram or flowchart showing one possible flow of thermal energy through the coolant of an internal combustion engine to a cleaning fluid, in accordance with the invention
  • Figure 14 is a schematic block diagram or flowchart showing one possible flow of mechanical energy through the piston of an internal combustion engine to a cleaning fluid and to an associated airflow, in accordance with the invention.
  • Figure 15 is a schematic block diagram or flowchart showing one possible flow of thermal energy through the exhaust of an internal combustion engine to a cleaning fluid, in accordance with the invention.
  • FIG. 1 is a schematic representation of a cleaning system, with which a given method of operation is provided, in accordance with the invention.
  • a washing plant 10 is mounted on a support, such as a vehicle or trailer, having an engine compartment 12, a cargo bay 14, an undercarriage 16, and remote cleaning implements 18.
  • a support such as a vehicle or trailer, having an engine compartment 12, a cargo bay 14, an undercarriage 16, and remote cleaning implements 18.
  • the dashed or phantom line in Figure 1 represents walls and floors of a vehicle that separate the engine compartment 12 from the cargo bay 14, etc.
  • the engine compartment 12 contains an engine system 20.
  • the cargo bay has a fluid storage and preheat system 22, a fluid drive system 24, a fluid top heating system 26, a portion of an intermediate fluid heating system 28 (e.g. oil heating system 28), and a waste storage system 30.
  • the intermediate fluid heating system 28 extends outside the cargo bay 14 to reach the undercarriage 16.
  • the remote cleaning implements 18 include a fluid applicator system 32.
  • the operation of the washing plant 10 may occur through a series of several steps. First, cleaning fluid 34 in a storage tank 36 receives heat while circulating around an outer shell of a first heat exchanger 38, labeled E-l 38, immersed in the storage tank 36. The resulting temperature rise pro ides a first or preheating stage for the cleaning fluid 34.
  • the first heat exchanger heats the water or cleaning fluid 34 to a temperature between 90-190 degrees F.
  • a water pump 40 draws preheated cleaning fluid 34 from a portion of the storage tank 36 near the first heat exchanger 38.
  • cleaning fluid 34 After passing through the pump 40. cleaning fluid 34 reaches a regulator 42, which acts as a three-way valve, having three outlets 43a, 43b, and 43c. If the fluid applicator system 32 is using (distributing, passing) fluid, a portion of the cleaning fluid
  • a malfunction of any flow path below the regulator 42 may be reflected therein.
  • an obstruction in the regulator 42, valves, or the associated lines carrying cleaning fluid will activate the regulator 42 to relieve the obstructed flow, directing it into the ambient through another outlet 31c.
  • the regulator could be configured to protect against overheating, but an exhaust diverter provides a fail-safe system that does not rely on active control to ensure safety from overheating.
  • Cleaning fluid 34 directed to the fluid applicator 32 travels through the outlet 31 a and into the first heat exchanger 38, where it circulates to more directly receive heat in a second preheating stage.
  • cleaning fluid 34 attains a temperature in the range of 200-205 degrees F, or, alternatively, in a range of 190-210 degrees F.
  • the cleaning fluid 34 then exits the first heat exchanger 38, exits the storage tank 36, and enters a second heat exchanger 44, labeled E-2 44.
  • the cleaning fluid 34 circulates through the second heat exchanger 44 to receive heat in a top-heating stage.
  • Cleaning fluid 34 exiting the second heat exchanger 44 is at a temperature sufficient for carpet cleaning.
  • This third heating stage raises the temperature of the cleaning fluid 34 between 235-245 degrees F. Then, the cleaning fluid 34 travels through a feed line 45 and into a wand 46, where it is directed against a surface to be cleaned, such as a carpet
  • the wand 46 may be of any type known in the art. Although the invention is described with respect to cleaning carpets, it is also suitable for cleaning upholstery on furniture, such as chairs and sofas, cleaning forced-air registers, walls, outdoor surfaces such as driveways, walk ways, building exteriors such as stucco, brick, and vinyl siding, among others. Yet another application of the cleaning system is that of performing hazardous material cleanup.
  • a vacuum is generated in a return line 49, which is used to cause air that surrounds the remote cleaning implements 1 8 to enter the wand 46, thereby removing the cleaning fluid 34 from the surface being cleaned (e.g. carpet 471, and passing into a dump tank 48 via a return line 49.
  • the cleaning fluid 34 carried in the air in the dump tank 48 enters a separator 50, which contains a cyclone 51, a deflector 52, and filters 54.
  • the cyclone 51 separates most liquid cleaning fluid 34 from air and vapor. Any remaining cleaning fluid 34 still entrained in air is then forced to go around a deflector 52 that directs the liquid-droplet-laden air into accumulated cleaning fluid 34 in the dump tank 48, where most droplets will be captured by surface tension. Finally, the filters 54 permit passage of air, but restrict the flow of any droplets of liquid cleaning fluid 34 and particulates of filterable size. Cleaning fluid 34 removed from air by the cyclone 51 , the deflector 52, and the filters 54 collects in the dump tank 48. A second filter system can also be incorporated with tank 48 to filter the used cleaning fluid 34 to such a degree that it may be safely disposed directly to the environment or to be recycled for cleaning again in storage tank 36.
  • Air passing out of the dump tank 48 through the filters 54 contains only a comparatively low concentration of vaporized cleaning fluid. Even if saturated at 100 percent humidity, this air passes from the dump tank 48 to a blower 56 drawing the flow.
  • the blower 56 creates a pressure differential to induce, or draw, air into the air channel of the wand 46 and through the return line, expelling it through a muffler 58
  • the muffler 58 dampens noise created by the high volumetric flow rate of the blower 56, expelled into ambient air around the washing plant 10.
  • the first heat exchanger 38 contains a reservoir or shell, filled with heated coolant 60.
  • Coolant 60 in the engine 62 carries excess or waste heat of combustion passed through the walls of the engine.
  • the coolant 60 then, optionally, travels through a radiator 64, such as a convector, which cools the coolant 60 by transferring heat to air flowing through the grill into the engine compartment 12.
  • a thermostatically-controlled or otherwise-controlled valve 66 can divert the coolant 60 away from the radiator 64 toward the first heat exchanger 38, for heating the cleaning fluid 34 in the storage tank 36 and in the first heat exchanger 38.
  • the valve 66 can be positioned in a flow of the coolant 60 to control the temperature of the coolant 60.
  • the valve 66 can operate to permit flow exclusively into the first heat exchanger 38 when the coolant 60 is sufficiently cool. Initially, on startup, such will be the case. Once heated to a maximum allowable temperature, or to a temperature sufficiently close to that of the engine, the coolant 60 may not accept enough heat to sufficiently cool the engine. Therefore, when the first heat exchanger 38, alone, is not removing an adequate amount of heat from the coolant 60, the valve 66 can direct flow inlo both the radiator 64 and the first heat exchanger 38.
  • an automotive thermostat can serve as the control valve 66.
  • a remote sensor 68 in the storage tank 36 can provide a temperature reading of a fluid at a different location.
  • the remote sensor 68 can be placed in the storage tank 36 to measure the temperature of the cleaning fluid 34.
  • the remote sensor 68 can then signal the valve 66 to shunt coolant 60 into the radiator 64 when the temperature of the coolant 60 or of the cleaning flu'd 34 in the storage tank reaches a level where cooling of engine 62 by heat e cf ⁇ anger 38 is insufficient. This diverts at least a portion of coolant 60 back through radiator 64 for adequate cooling of engine 62.
  • the second heat exchanger 44 or E-244 may be of a shell type, a shell filled with an intermediate heat transfer fluid 70. Any fluid 70 with a freezing point safe for exposure to seasonal ambient temperatures may suffice. Intermediate heat transfer fluid
  • the intermediate heat transfer fluid 70 is suitable, and means any suitable, intermediate, heat-transfer fluid 70.
  • the intermediate heat transfer fluid 70 is pressurized by an intermediate fluid pump such as oil pump 72.
  • the oil pump 72 circulates the intermediate heat transfer fluid 70 between the second heat exchanger 44 and a third heat exchanger 74, labeled E-3 74.
  • Exhaust 76 from the engine 62 can flow through a catalytic converter 77 and a muffler 78 before reaching a diverter 80 or a valve 80.
  • the valve 80 can be pressure- actuated by a vacuum source 82, driven by the engine 62
  • a bias is built into the valve 80, but can be optional.
  • the default positioning of the valve 80 passes exhaust directly to the environment, exposing none of the cleaning fluid 34 to the exhaust flow. The result is a fail-safe diverter. Any failure results in no substantial heat input from the exhaust flow to the cleaning fluid.
  • the vacuum source 82 may be the engine manifold or a pump 82 of a type that is continually coupled to the engine 62 to perform functions necessary for the engine system 20.
  • low pressure in the valve 80 may be used to actuate the valve 80 to direct exhaust 76 through the third heat exchanger 74 to heat the intermediate heat transfer fluid (e.g. oil) 70.
  • a thermostat 84 in the intermediate heat transfer fluid 70 measures the temperature thereof, and disconnects the vacuum pump 82 from the valve 80 when the temperature exceeds a selected value.
  • higher pressure in the valve 80 actuates the valve 80 to divert the flow of exhaust 76 to flow directly out of the washing plant 10 without traveling through the third heat exchanger 74.
  • Regulating the temperature of the intermediate heat transfer fluid 70 in this manner also serves to regulate the temperature of the cleaning fluid 34, because the intermediate heat transfer fluid 70 provides the top heating stage to the cleaning fluid 34. Thus, it is the temperature of the intermediate heat transfer fluid 70 that most directly determines the temperature of the cleaning fluid 34 that reaches the carpet 47.
  • the engine 62 transmits mechanical power to a transmission system 86, which includes a transmission, and possibly a transfer case.
  • a power takeoff 88, or PTO 88 extends from the transmission system 86 (e.g. either a transmission or transfer case) to permit further transmission of mechanical power to the fluid drive system 24.
  • a clutch 90 links the PTO 88 to a first mechanical coupling 92 when activated by a user.
  • the clutch 90 is placed downstream (with respect to power flow) of the transmission system 86 to avoid additional wear on the transmission system 86 from repeated engagement and disengagement with the PTO 88.
  • the PTO 88 may remain continually-meshed with the transmission system 86. This permits the apparatus 10 to avoid the problems that may otherwise result from frequent engagement and disengagement of gear members.
  • the clutch 90 can be one of many types known in the art, such as mechanical, hydraulic, and hydraulically actuated clutches.
  • a hydraulically actuated clutch is, however, preferable.
  • the first mechanical coupling 92 can include one or more coupling systems known in the art such as shafts, spur gears, worm gears, racks, pinions, bevel gears, u-joints, slip shafts, splined shafts, belts, pulleys, chains, cams, levers, and hydrostatic systems.
  • the first mechanical coupling 92 then transmits mechanical power from the PTO 88 to the blower 56.
  • a second mechanical coupling 94 is connected to the blower 56 to transmit mechanical power to the water pump 40.
  • the second mechanical coupling 94 may be of any type known in the art, such as those mentioned above in connection with the first mechanical coupling 92. However, the second mechanical coupling 94 is shown to be a belt and pulley system.
  • a third mechanical coupling 96 is connected to the water pump 40 to transmit mechanical power to the intermediate heat transfer fluid pump 72.
  • the third mechanical coupling 96 can also be of any type known in the art, such as those mentioned in connection with the first mechanical coupling 92.
  • the third mechanical coupling 96 shown includes a direct drive shaft extending from the water pump 40 directly to the intermediate heat transfer fluid pump 72.
  • a washing plant 110 is mounted on a truck 1 12.
  • the truck 1 12 shown has a large cargo bay 1 14 for storing, protecting, and conveying washing equipment to and from the cleaning site.
  • truck 1 12 can actually be a trailer with its own motor provided that is utilized to power apparatus 10.
  • a tank 116 in the cargo bay 1 14 stores a reservoir of the cleaning fluid 117 used to clean carpets.
  • the cleaning fluid 117 can utilize liquid water, steam vapor, or two-phase steam as its principal constituent. Cleaning chemicals may also be added.
  • An apparatus and method in accordance with the invention provide water hot enough to clean carpets well, even without chemical additives.
  • a pre-spray or pre-clean system may be used to enhance cleaning.
  • the apparatus 10 may be used to spot clean areas of heavy soiling prior to general cleaning.
  • the apparatus 10 may also be utilized to clean other surface rather than solely carpets. These other surfaces can include tile, vinyl, concrete, cement, asphalt, brick, stucco, marble, granite, upholstery, automobiles, construction equipment, or glass, but not limited thereto.
  • An equipment operator fills the tank 1 16 with cleaning fluid 1 17 before driving the truck 112 to a cleaning site.
  • Cleaning fluid 117 in the tank 1 16 is heated en route to the site.
  • a water pump 118 in the cargo bay 114 conveys cleaning fluid 1 17 through a first water conduit 120 and possibly a second water conduit 121. From the first and second water conduits 120 and 121, the cleaning fluid 117 passes to a first wand 122 and a second wand 123 passed over an area to be cleaned by operators.
  • the washing plant 110 delivers sufficient heat, pressure, and fluid flow rates to permit the simultaneous use of both wands 122 and 123.
  • multiple wands 122 and 123 can be included, which can exceed two wands where apparatus 10 can service as many as 10 wands with sufficient power and cleaning fluid for proper operation. Also, but a single wand 122 can be incorporated into apparatus 10 where only a single operator is available to operate apparatus 1 to perform the desired cleaning operation.
  • a blower 124 in the cargo bay 114 generates a vacuum by drawing air through a tube 126 from a dump tank 128.
  • the vacuum drawn in the dump tank 128 induces an air flow through a first conduit 130 and a second conduit 131 , which are connected to the first and second wands 122 and 123.
  • a vacuum is created proximate the surface of the carpet being cleaned, thereby drawing the cleaning fluid 1 17 and particulate matter from the carpet, through the first and second conduits 130 and 131, and into the dump tank 128.
  • Air drawn from the dump tank 128 exits the blower 124 through a tube 132 that leads to a muffler 135 (shown in Figure 5), which reduces noise generated by the blower 124.
  • a cover 135 over the muffler serves to attenuate the noise further from the blower 124.
  • a control panel 136 mounted on the tank 116 is accessible to an operator to provide diagnostic information and controls for optimizing the performance of the washing plant 110.
  • FIG 3 shows one presently preferred embodiment of a washing plant 10 of Figure 2 from a different viewpoint.
  • a portion of the truck 1 12 has been shown in phantom lines to reveal an engine 138, a transmission system 140, a radiator 142, and a vacuum pump 144 for creating a vacuum 145 in relation to gauge, or atmospheric pressure.
  • a line 146 conveys exhaust 147 from the engine 38 to a third heat exchanger 148 located directly below the cargo bay 1 14; the exhaust 147 leaves the third heat exchanger 148 via an outlet 149.
  • An intermediate fluid pump 150, or intermediate heat transfer fluid pump 150 circulates an intermediate heat transfer fluid 151, or oil 151, through the third heat exchanger 148 to draw heat from the exhaust 147 into the intermediate heat transfer fluid 151.
  • the intermediate heat transfer fluid 151 circulates through a second heat exchanger 152.
  • Cleaning fluid 117 flows through the second heat exchanger 152 to draw heat from the intermediate heat transfer fluid 151. Since the intermediate heat transfer fluid 151 expands when heated, an expansion tank 154, which is attached to the second heat exchanger 152, provides buffer space for extra intermediate heat transfer fluid 151 overflowing from the second heat exchanger 152 during operation of the washing plant 110.
  • the cleaning fluid 117 exits the second heat exchanger 152, briefly reent ⁇ rs the tank 116, and then leaves the tank 116 to reach the first or second wands 122 or 123 via the first and second water conduits 102 and 121
  • a rack 156 may be included as shown in Figure 2 to safely and conveniently store the water conduits 120 and 121 and the conduits 130 and 131 for transportation to or from a site.
  • FIG 4 illustrates the engine system 20.
  • the engine 138 can be any type of internal combustion engine.
  • Engine 138 can also be designed to tolerate operation at comparatively modest speeds while stationary for long periods of time. Such performance is well suited to a diesel cycle engine.
  • a diesel cycle also provides comparatively higher torque at a lower rotational rate (angular velocity) with a lower net fuel consumption than a comparable gasoline cycle.
  • engine 138 can also be a turbine engine with heating and pumping stages adapted to drive system 10 in accordance with the present invention.
  • the line 146 conveys exhaust gas 147 away from the engine 138 to the third heat exchanger 148.
  • the transmission system 140 provides gearing to maintain a consistent load on the engine at different speeds and may include a transfer case.
  • the power takeoff (PTO) 158 extends from the transmission system 140 to provide power to mechanically- driven components of the washing plant 110.
  • the PTO 158 extends to a clutch 160, which couples the PTO 158 to a shaft 161 when engaged by a user.
  • the vacuum pump 144 operates a safety cutoff designed to stop the transfer of heat to the intermediate heat transfer fluid 151 in the third heat exchanger 148 when the intermediate heat transfer fluid 151 becomes too hot.
  • the vacuum pump 144 can be continually driven by the engine 138 to provide a vacuum (with respect to gauge pressure).
  • a vacuum 145 also exists in the line 162 when the line 162 is connected to the vacuum pump 144.
  • Controls can be operated with either sense (direction, or state) as active and the other a default. However, safety may be best served by carefully selecting default positions for control systems.
  • a valve 163 may support the vacuum 145 in the line 162 when the temperature of the intermediate heat transfer fluid 151 does not exceed a selected, permissible level.
  • the line 164 may signal the valve 163 to disconnect the line 162 from the vacuum pump 144 so that the line 164 is no longer evacuated.
  • the third heat exchanger 148 effectively receives no exhaust heat.
  • the valve 163 is selected to be failsafe, so that unless affirmatively activated by a vacuum originating in a functioning (rotating) engine system 20, the valve 163 closes by default against heat exchange, to divert exhaust to the environment. Thus, the default position directs exhaust away, as if no heat exchanger 148 existed, keeping the intermediate heat transfer fluid 151 from overheating.
  • the radiator 142 can be thought of as a liquid coolant reservoir designed to conduct heat from the engine 138 to the ambient air, which serves as a heat sink.
  • the coolant 165 can be one of any number of fluids such as water, glycol, or a water/glycol mixture.
  • a thermostatic valve 66 of the engine can serve to direct coolant. Even a remotely located or remotely controlled valve 168, however, can operate effectively the same as an integrated thermostatic valve 66, 168.
  • the line 116 conveys coolant 165 from the engine 138 to a thermostatically controlled valve 168.
  • the valve 168 can operate autonomously with integrated control (e.g. like a conventional thermostatic valve), or can be controlled by signals through a line 169 from a remote sensor.
  • integrated control e.g. like a conventional thermostatic valve
  • the vaive 168 can shunt all coolant 165 to the line 170 leading to the tank 1 16.
  • the valve 168 restricts the line 170 or otherwise circulates the coolant
  • valve 168 may be a flow divider proportioning the flow of coolant 165 between the radiator 142 and the tank 1 16 by any suitable means.
  • Coolant 165 leaves the radiator through a line 172 to reach a junction 174, to be joined by any coolant 165 portion leaving the tank to return to the engine 138.
  • the line 170 to the tank 116 is closed off, sending all coolant through he vehicle radiator 142 to ensure that the engine 138 cannot overheat.
  • FIG. 5 shows the fluid drive system 24.
  • a shaft 177 coupled to the shaft 161 and extending from the clutch 160 and underneath the cargo bay 1 14, terminates in a pulley 178 under the blower 124. Any suitable driving connection 180 will suffice.
  • a belt 180 may be engaged by the pulley 178. extending up through an opening in the floor 179 of the cargo bay 114 to reach another pulley 184 rotatably coupled to the blower 124.
  • the shaft 177 turns the pulley 184 to operate the blower 124.
  • a second belt 186 may extend from the pulley 184 to reach an additional pulley 188, which drives the water pump 1 18.
  • a shaft 189 extends through the opposite side of the water pump 118 to drive the intermediate heat transfer fluid pump 150 (e.g. oil pump 150).
  • the blower 124 draws air through the tube 126 and expels it through the tube 132 and into the muffler 134 (shown without the cover 135).
  • the water pump 118 draws cleaning fluid 117 from the tank 116 through the line 190 and expels it to the regulator 191 via the line 192.
  • the intermediate heat transfer fluid pump 150 draws intermediate heat transfer fluid 151 through the line 194 from the second heat exchanger 152 and expels it through the line 196 to the third heat exchanger 148.
  • each of the pumps can be electrically driven with an electro-magnet motor powered by an electrical power supply driven by engine system 20.
  • An alternator, coupled to engine system 20 can be provided to supply sufficient enough electrical energy to drive all pumps and regulators, instead of rely exclusively upon mechanical force of pulley drives.
  • a mixture of mechanical and electro-magnet derived power can be incorporated within the present invention as is practicable by the design of those skilled in the art.
  • Figure 6 depicts the intermediate heat transfer fluid heating system 28.
  • the exhaust 147 from the engine 138 travels via the line 146 under the cargo bay 1 14 and passes through a muffler 198 to decrease engine noise.
  • the exhaust 147 reaches a diverter 200 controlled by air pressure in the line 162 from the vacuum pump 144.
  • the diverter 200 shunts the exhaust 147 into the third heat exchanger 148.
  • the exhaust 147 exits via the outlet 149 Alternatively, when the line 162 is not evacuated, the diverter 200 blocks the third heat exchanger 148 and channels the exhaust 147 out of the washing plant 110 through the tailpipe 202
  • the vacuum control concept is straightforward, stable, and fail-safe. However, any suitable control mechanism may control actuation of the diverter valve 200 in order for the exhaust flow to bypass the third heat exchanger 148, unless the cleaning fluid is present to prevent a temperature runaway or equipment damage.
  • intermediate heat transfer fluid 151 continues to flow into the third heat exchanger
  • the intermediate heat transfer fluid 151 or any suitable alternative heat transfer fluid
  • the third heat exchanger 148 may preferably be located outside the cargo bay 1 14, due to the danger of channeling exhaust gases through an enclosed portion of a vehicle.
  • the third heat exchanger 148 may be left in the third heat exchanger 148 without a heat source. If plain water instead of the intermediate heat transfer fluid 151, or other non-freezing heat-transfer fluid 151, were used for the intermediate heat transfer fluid 151 , the water could freeze, and the third heat exchanger 148, the line 196, the line 204, or all of them could be damaged.
  • plain water instead of the intermediate heat transfer fluid 151, or other non-freezing heat-transfer fluid 151, were used for the intermediate heat transfer fluid 151 , the water could freeze, and the third heat exchanger 148, the line 196, the line 204, or all of them could be damaged.
  • the third heat exchanger 148 comprises low fin tubing.
  • "Low fin” is a term of art used to describe short radially extending, sometimes helical threads formed on a tube to be positioned in a fluid flow of a heat exchanger. Exhaust gases 147 flowing into the third heat exchanger 148 may be distributed among several tubes 205. Tubes 205 may be narrow and positioned such that intermediate heat transfer fluid 151 can flow between them. Fins 206 (e.g. Helical thread 206) on the tubes 205 increase the total surface area available to intermediate heat transfer fluid 151 to allow greater heat transfer from exhaust 146 to intermediate heat transfer fluid 151 via tubes 205. The threads 206 also increase the surface area through which exhaust heat can be conducted and converted to the intermediate heat transfer fluid 151.
  • Fins 206 e.g. Helical thread 206
  • Fins 206 can be formed that increase the total surface area of the exterior of tubes 205 to as much as 2.5 times the regular surface area of tubes 205 without any threads formed therein. Further, fins 206 need not be formed directly in tubes 205, but can be formed by adding a second metal, the same as or different than that used for tube 205, to increase the total surface area of tubes 205 by forming the second metal into fins for increased heat dissipation. Further still, the threads 206 can be placed on the interior surface of tubes 205 as well.
  • a heat exchanger utilizing low fin tubing has on the order of two-and- a-half times the heat transfer capability of a comparable heat exchanger with no such tubing.
  • Low fin tubing heat exchangers have never been used in previous carpet-cleaning machines. Part of the reason may be because the high heat transfer rate causes the water to leave deposits of lime, magnesium, calcium, and other minerals, thereby fouling (coating) the surfaces of the heat exchanger with insulators.
  • This problem is solved by the present invention through the use of. among other things, the intermediate heat transfer fluid 151 to transfer the heat from the exhaust 147 to water lines 120, 121 in a separate heat exchange process.
  • FIG. 7 shows the fluid storage and preheat system 22.
  • the line 192 from the water pump 118 conveys cleaning fluid 117 to the regulator 191, which sends some of the cleaning fluid 117 directly back into the tank 116 via a line 208. If an operator is using a wand 122, 123 to apply cleaning fluid 117 to a carpet, the regulator 191 also sends a portion of the cleaning fluid 117 through the line 210.
  • the line 210 goes through the tank 116, but is sealed away from the cleaning fluid 1 17 in the tank 116.
  • the regulator 191 also contains an outlet 211 to expel the cleaning fluid 117 into the environment or to the cargo bay 114 if the pressure inside the regulator 191 exceeds a set safety limit.
  • Tank 116 is further divided into compartments, including compartment
  • Tank 116 can have one or more compartments, according to the design of the skilled artisan. Fluid traveling through the line 210 reaches a first heat exchanger 212 immersed in the cleaning fluid 117 in compartment 116A of storage tank 116. Compartment 116A provides a smaller volume of cleaning fluid 1 17 to be heated in this first heat exchange stage. Heated coolant 165 from the engine 138 enters the first heat exchanger 212 via the line 170 and exits via the line 176. The heated coolant 165 within the first heat exchanger 212 serves a dual function.
  • the coolant may pass through the tubes or the shell of the heat exchanger 212. Passing the coolant 165 through the shell provides heat transfer to the cleaning fluid 1 17 in the bulk of the tank 1 16, as well as to that passing though the internal tubes of the heat exchanger 212.
  • the illustrated embodiment provides two heat exchange processes into the cleaning fluid 117.
  • the heat exchanger 212 heats the ambient cleaning fluid I I 7 in compartment 1 16A through the shell.
  • the portion of cleaning fluid 1 17 in the vicinity of the first heat exchanger 212 may remain somewhat hotter than the remaining cleaning fluid 117 in the other compartments 116 A and 116C of tank 116 if the baffles 214 are configured to limit fluid circulation within the tank 1 16.
  • cleaning fluid 117 drawn from the tank 116 through the line 190 may be at a comparatively higher temperature than that of the remaining cleaning fluid 1 17 in the tank 1 16. This heating occurs independently from any movement of cleaning fluid 1 17 by operation of the pump 1 18 and PTO 158.
  • the cleaning fluid 117 can receive heat while the blower 124, the water pump 118, and the intermediate heat transfer fluid pump 150 are not operating.
  • the cleaning fluid 117 in the tank 116 may thus be heated by engine coolant during virtually the entire transit time to a cleaning site.
  • the baffles 214 can have openings 215 strategically placed at the tops and bottoms to provide fluid flow between adjacent compartments
  • cleaning fluid 117 entering the first heat exchanger 212 from the line 210 travels through a series of tubes, which can be configured as helically-twisted coils (not shown) within the first heat exchanger 212 to increase the surface area and path length (and reduce the hydraulic diameter, 4xCS Area/Wetted Perimeter) through which heat can move from the coolant 165 to the cleaning fluid 117. Therefore, as cleaning fluid 117 exits the first heat exchanger 112 through a line 216, it will be at a temperature higher than that of the bulk cleaning fluid 117 in compartment 1 16A, or any other compartment, of the tank 116.
  • the cleaning fluid 117 may re-enter the tank 116 via the line 218, exiting out of the tank 1 16 through a hookup 220 (fitting 220) connected to the conduit 120.
  • a sensor 222 is provided to sense the temperature of the cleaning fluid 117 in the tank 116, compare that temperature to a preset limit, and transmit a corresponding signal via the line 169 to the valve 168 controlling flow.
  • the valve 168 can be an independent, integrated (e.g. automotive) thermostat positioned to control the flow of the coolant 165 based on local temperature.
  • Figure 8 illustrates a perspective, partial cut-away view of the fluid top-heating system 26.
  • Intermediate heat transfer fluid 151 heated by passing through the third heat exchanger 148, enters the second heat exchanger 152 via the line 204 and exits to the intermediate heat transfer fluid pump 150 via the line 194.
  • the line 216 conveys the heated cleaning fluid 1 17 out of the tank 1 1 and into the second heat exchanger 152 for further heating.
  • Cleaning fluid in the second heat exchanger 152 travels through sets of helically- twisted coils 226, similar to those in the first heat exchanger 212.
  • the coils 226 improve the efficiency of heat transfer between the intermediate heat transfer fluid 151 and the cleaning fluid 117 by conducting the cleaning fluid 1 17 through a larger area, smaller hydraulic diameter, and longer path through the intermediate heat transfer fluid 151.
  • the coils 226 in one embodiment are about 160 feet in length with a one- quarter- inch inside diameter. Other dimensions and lengths are contemplated to be within the scope of the present invention. For example, the length can be between 100-250 feet with a corresponding inside diameter from one inch to as small as one-eighth-inch.
  • a thermostat 228 controls the temperature of the intermediate heat transfer fluid 151 against a preset limit.
  • a remote sensor transmits a corresponding signal via the line 164 to the valve 163.
  • an integrated, self-regulating thermostat 228 can be positioned within a separate enclosure on one of the lines 194, 196, or 204 carrying intermediate heat transfer fluid 151.
  • the thermostat 228 can be mounted in the second heat exchanger 152, as depicted in Figure 8.
  • the waste storage system 30 is shown in greater detail in Figure 9, which illustrates a perspective partial cut-away view thereof.
  • the waste storage system 30 has first and second conduits 130 and 131 to draw air into the dump tank 128.
  • the first and second conduits 130 and 131 are mounted to a baffle 234 facing into a cyclone baffle 236, curved to divert the incoming air to form a whirling, cyclonic flow. Air and water vapor, with entrained water droplets and soil, impinge against he cyclone baffle 236 and begin to swirl. Air and vapor move to the center of the vortex, while centrifugal effects move liquids and solids outward.
  • the baffle 234 creates a barrier to ensure that water and soil entering the dump tank 128 drop out quickly in the pass against the cyclone baffle 236.
  • the air is drawn by vacuum across another baffle 238 extending across the middle of the dump tank 128.
  • the baffle 238 is a barrier to liquid and solids and diverts the movement of warm, moist air, which condenses against he baffle 238 and by direct contact with liquid in the dump tank 128.
  • the flow underneath the baffle 238 eventually reaches the filters 240.
  • any remaining particulate matter and liquid droplets are trapped in the dump tank 128 by the filters 240. All but a small concentration of vaporized cleaning fluid remains in the dump tank 128.
  • the dump tank 128 may be emptied through a drain 242 at the bottom of the dump tank 128.
  • the collected cleaning solution 135 can be further filtered with a filter means sufficient to clean the solution 135 and re-utilize the cleaned solution again within system 10 for cleaning purposes
  • the invention contemplates not only a novel apparatus, but also a collection of novel steps for improved carpet cleaning.
  • an apparatus In order to effectively suspend or dissolve particulates and other soiling agents found m carpet, an apparatus should provide a high flow rate of cleaning fluid at a high temperature and pressure. In addition, a high flow rate of air at a low pressure is required to remove fluids and soils from a carpet.
  • Figure 10 illustrates one current embodiment of a flow path for cleaning fluid 117 through the washing plant 110.
  • An operator fills the storage tank 116 with cleaning fluid
  • This cleaning fluid 117 undergoes a first temperature rise, or first preheat, as it receives heat through an outer shell of the first heat exchanger 212.
  • the water pump 118 imparts a pressure rise to the cleaning fluid 1 i 7 while drawing from the storage tank 116 for pumping fluid 177 to the regulator 191.
  • the regulator 191 may expel the cleaning fluid 117 for safety's sake as discussed above. Otherwise, the regulator 191 sends the portion required for immediate cleaning through the first heat excnanger 212, and conveys the remainder back into the storage tank 1 16.
  • Cleaning fluid 1 1 7 in the first heat exchanger 212 circulates through the tubes (e.g. coils) of the first heat exchanger 212 to receive a second temperature rise, or second preheat.
  • the cleaning fluid 117 exits the first heat exchanger 212 to enter the second heat exchanger 152, where it circulates to receive a third temperature rise, or top heat. After the top heating stage in the second heat exchanger 152, the cleaning fluid 117 flows through the first 122 or second wand 123 to strike the surface of a carpet.
  • Figure 1 1 depicts one embodiment of a flow path of air through the washing plant 110.
  • Air surrounding the surface of a carpet is drawn through the first 122 or second wand 123 and into the dump tank 128.
  • the air hits the cyclone baffle 234, creating a cyclone separator. Air then crosses the deflector 238, and moves through the filters 240 before being drawn into the blower 124.
  • the blower 124 imparts a pressure rise to the air, which then passes through the muffler 134 before exiting the washing plant 110.
  • Figures 10 and 1 The transfer of energy into the working fluid is, however, only one step in an energy delivery and conversion process that begins in the engine 138.
  • Figures 12-15 show how one embodiment for passing energy from the engine 138 to the flows of air and water shown in Figures 10 and 1 1 .
  • the initial conversion of chemical energy in an internal combustion engine increases the temperature and pressure of gases inside a cylinder of the engine.
  • Part of the released thermal energy enters the wall of the cylinder and passes into a coolant stream moving past the cylinder in the block.
  • Part of the released mechanical energy is transferred to move a piston in the cylinder.
  • Figure 13 focuses on the thermal energy from the engine 138 that passes into the coolant 165.
  • thermal energy from a cylinder of the engine 138 enters the coolant 165 in the line 166 leading to the valve 168.
  • the valve 168 sends the coolant 165 with its associated thermal energy into the radiator 142.
  • the thermal energy then passes through the wall of the radiator 142 and into the ambient air by convection.
  • the valve 168 shunts the coolant 165 through the line 170 to convey thermal energy through the first heat exchanger 212. Some of the thermal energy passes through the shell 213 of the first heat exchanger 212 to preheat the cleaning fluid 1 17 in the tank 116. The remaining thermal energy travels into the walls of the coiled tubing 151 inside the first heat exchanger 212 to be discharged inside the shell 213. Thermal energy in the cleaning fluid 117 in the tank 116 is drawn into the water pump 218 with the cleaning fluid 117 via a line 190. The thermal energy next passes into the regulator 191 as heat in the cleaning fluid 1 17. In response to an obstruction, the regulator 91 may optionally expel an amount of cleaning fluid 1 17 with its associated thermal energy.
  • cleaning fluid 117 needed for immediate use passes, with its associated thermal energy, into a line 210 in the tank 116.
  • the line 210 leads into the first heat exchanger 212, where the cleaning fluid 117 receives more thermal energy from the vehicle engine coolant 165 through the walls of coiled tubing.
  • the cleaning fluid 117 leaving the first heat exchanger 212 conveys thermal energy through the second heat exchanger 152, through the first or second wand 122 or 123, and to the carpet.
  • Figure 14 is directed to the flow of mechanical energy from a piston of the engine 138. Tne mechanical energy in the piston is transferred to a crank shaft, where it is converted from a translation to rotational motion.
  • the crank shaft conveys the mechanical energy to the transmission system 140, which further transmits it to a drive train of the truck 1 12, the PTO 158, or both. If the clutch 160 is not engaged, the mechanical energy from the PTO 158 goes unused. However, if the clutch 160 is engaged, mechanical energy passes to the blower 1 4, the water pump 118, and the intermediate heat transfer fluid pump 150.
  • the blower 124 pressurizes air, thereby converting the rotational energy provided by the dutch 158 into potential energy, in the form of a co ⁇ esponding vacuum (with respect to gage pressure) and compressed air, and kinetic energy, in the form of moving air. as a result, a pressure gradient is formed through the dump tank 128, the first or second conduit 130 oi 131, and the first or second wand 122 or 123.
  • the blower 124 uses mechanical energy to extract energy from air, thereby creating an airflow useful to remove soil and fluid.
  • the water pump 1 18 transfers mechanical energy in the form of a pressure rise to the cleaning fluid 117.
  • the cleaning fluid 117 exiting the water pump 118 through the line 192 enters the regulator 191.
  • Tne regulator 191 bleeds off any excess mechanical energy, only in emergency conditions.
  • the mechanical energy passes with cleaning fluid 117 into the tank 1 16 and into the line 210 to the first heat exchanger 212.
  • the pressurized cleaning fluid 117 continues on through the first heat exchanger 212, the second heat exchanger 152, and the first 122 or second wands 123 to strike the surface of a carpet at high pressure.
  • the intermediate heat transfer fluid pump 150 transfers a small amount of mechanical energy to the intermediate heat transfer fluid 151 to induce a pressure rise.
  • the intermediate heat transfer fluid 151 circulates between the first and second heat exchangers 212 and 152. As the intermediate heat transfer fluid 151 leaves the intermediate heat transfer fluid pump 151, pressure drops due to frictional losses (head loss), until it once again reaches the intermediate heat transfer fluid pump 151. Thus, the mechanical energy transferred to the intermediate heat transfer fluid 151 acts simply to maintain the motion thereof.
  • thermal energy in the exhaust 147 leaves through a manifold of the engine 138 to reach the line 146. From there, the hot exhaust 147 enters the third heat exchanger 148, where thermal energy is transferred to the tubes 205 and fins 206 (e.g. thread 206) in the third heat exchanger 148 by convection, intermediate heat transfer fluid 151 flowing through the third heat exchanger 148 absorbs the thermal energy, once again by convection.
  • the intermediate heat transfer fluid 151 is pumped into the second heat exchanger 152, where thermal energy moves by convection into the walls of the coiled tubing 226.
  • Cleaning fluid 117 moving through the second heat exchanger 152 absorbs the thermal energy by convection and conveys it through the first or second wands 122 or 123 to the carpet surface.
  • the entire energy delivery and conversion process is improved because every energy transfer step may be properly balanced. If too much energy is transferred in a single step, the equipment could fail or the cleaning fluid 117 could exceed safe temperatures and pressures for carpet cleaning. For example, if the intermediate heat transfer fluid 151 in tne second heat exchanger 152 is too hot, thermal breakdown may occur. Also, the cleaning fluid 1 17 may become too hot for pressure containment or even too hot as it exits the first 122 or second wand 123. Damage to the carpet may result. The cleaning fluid 117 may also corrode the second heat exchanger 152 due to local nucleate boiling. If the coolant 165 in the first heat exchanger 212 is too hot, the cleaning fluid 117 may likewise cause corrosion or each a dangerously high pressure.
  • the cleaning fluid 117 and air may not reach the flow rates, pressures, and temperatures necessary for effective cleaning.
  • the energy flows depicted in Figures 12-15 are unique. For example, they provide a balance of energy transfers.
  • the engine 138 provides sufficient energy to raise the cleaning fluid 117 and air to the appropriate temperatures, pressures, and flow rates for effective carpet cleaning. This energy is converted to the proper form and applied in stages to the cleaning fluid 117 and air.
  • the invention has the proper mechanisms to ensure that the energy transferred with each step does not exceed the operating limits of the equipment. As a result, the apparatus and method of the invention provides a degree of effectiveness, reliability, durability, and convenience nonexistent in the prior art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Cleaning By Liquid Or Steam (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention se rapporte à un système de nettoyage destiné à des applications de nettoyage à haute température telles que le nettoyage de tapis ou moquette, qui assure une température cohérente du fluide de nettoyage. Ce système de nettoyage met en oeuvre de multiples échangeurs thermiques et de multiples trajets thermiques. La source de puissance et de chaleur est fournie par un moteur diesel moyennement résistant. Le chauffage par étapes multiples implique un transfert thermique du liquide de refroidissement du moteur vers le fluide de nettoyage et un transfert thermique des gaz d'échappement du moteur vers le fluide de nettoyage par le biais d'un milieu intermédiaire. Ledit système comporte également un embrayage à fluide assurant un démarrage à puissance réduite du moteur pour la mise en oeuvre de la pompe et la soufflerie de l'équipement de nettoyage. Un dispositif à sécurité intégrée de coupure de l'alimentation sert à dévier le flux d'échappement de manière à empêcher le contact thermique avec une huile de transfert de chaleur intermédiaire.
PCT/US1999/029770 1998-12-17 1999-12-15 Equipement de nettoyage portable, a haute pression et haute temperature WO2000035329A2 (fr)

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AU21854/00A AU2185400A (en) 1998-12-17 1999-12-15 Portable, high-temperature, high-pressure washing plant
US09/868,350 US6675437B1 (en) 1999-12-15 2000-12-15 Portable high-temperature, high-pressure washing plant

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US60/112,638 1998-12-17

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US10293383B2 (en) 2014-07-18 2019-05-21 Alfred Kärcher SE Co. KG Mobile high-pressure cleaning apparatus

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US4109340A (en) * 1977-01-27 1978-08-29 Bates Leonard Eugene Truck mounted carpet cleaning machine
US4158248A (en) * 1977-02-14 1979-06-19 Palmer Michael C Mobile cleaning unit
US4284127A (en) * 1979-06-01 1981-08-18 Syd W. Collier Company Limited Carpet cleaning systems
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US5056601A (en) * 1990-06-21 1991-10-15 Grimmer John E Air compressor cooling system
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Publication number Priority date Publication date Assignee Title
US10293383B2 (en) 2014-07-18 2019-05-21 Alfred Kärcher SE Co. KG Mobile high-pressure cleaning apparatus
CN105179078A (zh) * 2015-09-28 2015-12-23 百发动力（无锡）有限公司 热电联产内燃机发电机组

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Publication number Publication date
WO2000035329A9 (fr) 2000-11-02
AU2185400A (en) 2000-07-03
WO2000035329A3 (fr) 2000-09-14

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