WO2007011324A1 - Bloc hydraulique pour systeme de refrigeration - Google Patents

Bloc hydraulique pour systeme de refrigeration Download PDF

Info

Publication number
WO2007011324A1
WO2007011324A1 PCT/US2005/018300 US2005018300W WO2007011324A1 WO 2007011324 A1 WO2007011324 A1 WO 2007011324A1 US 2005018300 W US2005018300 W US 2005018300W WO 2007011324 A1 WO2007011324 A1 WO 2007011324A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
hydraulic
blower
fluid
power unit
Prior art date
Application number
PCT/US2005/018300
Other languages
English (en)
Inventor
Eugene Holt
Original Assignee
Hydracool, Inc.
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 Hydracool, Inc. filed Critical Hydracool, Inc.
Priority to EP05857690A priority Critical patent/EP1904321A4/fr
Priority to AU2005334526A priority patent/AU2005334526A1/en
Priority to CA002576917A priority patent/CA2576917A1/fr
Priority to PCT/US2005/018300 priority patent/WO2007011324A1/fr
Priority to IL179574A priority patent/IL179574A0/en
Publication of WO2007011324A1 publication Critical patent/WO2007011324A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00421—Driving arrangements for parts of a vehicle air-conditioning
    • B60H1/00435—Driving arrangements for parts of a vehicle air-conditioning fluid or pneumatic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3222—Cooling devices using compression characterised by the compressor driving arrangements, e.g. clutches, transmissions or multiple drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2327/00—Refrigeration system using an engine for driving a compressor
    • F25B2327/001—Refrigeration system using an engine for driving a compressor of the internal combustion type

Definitions

  • the present invention relates to a hydraulic power unit for a refrigeration system
  • Refrigeration systems are commonly used in all types of transport vehicles for
  • conditioning systems such systems include a compressor for compressing a refrigerant
  • the compressed refrigerant is then passed into an evaporator where it is
  • the amount of cooling is controlled by controlling the speed
  • the refrigeration system attempts to provide and maintain a desired
  • the cooling output is controlled by controlling the output of the engine. While providing a straight-forward
  • the dedicated engine has the disadvantage that it adds cost
  • the power for the system is obtained from the vehicle engine.
  • the power is typically taken
  • Heat from the vehicle's cooling system can be used
  • the hydraulic transmission
  • the system has not been known to function in a truck or other land transport vehicle.
  • Refrigeration systems also typically employ a blower for blowing air through the
  • blowers are directly connected to the compressor, although older units employed electrical power. When connected to the compressor, the blower speed
  • Precise temperature control of the entire interior of the box can be critical.
  • the present invention provides for a hydraulic power unit for a refrigeration
  • the power unit is provided for driving
  • the refrigeration system has a compressor for compressing a
  • the unit comprises a pump, a compressor motor, and a hydraulic circuit.
  • the pump is
  • the compressor motor is adapted for driving the compressor in response to
  • the hydraulic circuit is adapted for conducting the hydraulic fluid from the pump to the compressor motor and for conducting the
  • a temperature control portion having a heat exchanger and adapted for diverting
  • temperature indication indicating the temperature of the fluid.
  • the refrigeration system furthermore
  • the power unit includes a blower for blowing air through the evaporator.
  • the power unit comprises a
  • the pump is adapted for pumping
  • the blower motor is adapted for driving the blower in response to receiving hydraulic fluid
  • the hydraulic circuit is adapted for conducting the hydraulic fluid from the pump.
  • the hydraulic circuit includes a temperature control portion
  • Figure 1 is a schematic diagram of a hydraulic power unit for a refrigeration
  • Figure 2 is a pictorial, partially cut-away view of a preferred land transport vehicle
  • Figure 3 is a schematic diagram of a compressor motor control module according
  • Figure 4 is a schematic diagram of a blower motor control module according to
  • the present invention for use with a pump having a substantially constant power output.
  • Figure 5 is a schematic diagram of a blower motor control module according to
  • Figure 6 is a schematic diagram of a generalized oil temperature control module
  • FIG. 7 is a schematic diagram of the oil temperature control module of Figure 6
  • Figure 8 is a schematic diagram of a preferred hydraulic power unit according to
  • Figure 9 is a schematic diagram of a preferred oil temperature control module
  • Figure 10 is a schematic diagram of a means for coupling a hydraulic compressor
  • Figure 1 is a schematic view of a hydraulic power unit 10 for transmitting power
  • refrigeration system are all contained on a land transport vehicle 9, particularly in the
  • the truck has a cargo volume 11 which is referred to as a standard semi-trailer truck.
  • the truck has a cargo volume 11 which is referred to as a standard semi-trailer truck.
  • the engine 12 is used for propelling the truck and is typically a large internal
  • combustion engine most typically a diesel engine.
  • the engine provides a torque output
  • the torque output of the engine is made available for powering
  • PTO power take off
  • the PTO 15 may be coupled directly to the engine
  • the hydraulic power unit 10 includes a hydraulic pump
  • pump is adapted to pump hydraulic fluid, typically (and hereinafter) oil, through a
  • the hydraulic pump 24 may be any standard type of pump used in hydraulic systems such as earthmoving equipment. However, preferably,
  • the pump 24 is of the type known in the art of hydraulic systems as variable volume
  • VVPC pressure compensated
  • the refrigeration system 14 includes a compressor 16, a condenser
  • the hydraulic power unit 10 includes a hydraulic
  • the hydraulic circuit 17 includes hydraulic oil carrying lines 17a that carry and
  • the hydraulic circuit routes the hydraulic oil that is pressurized by the pump 24.
  • the hydraulic circuit routes the hydraulic oil that is pressurized by the pump 24.
  • control module 26 for controlling the amount of the hydraulic oil that is provided to the
  • compressor motor The compressor motor 22 and the control module 26 are coupled in parallel.
  • both the compressor motor 22 and the control module 26 receive hydraulic
  • the control module 26 controls the amount of oil provided to
  • the compressor motor 22 by accepting (shunting) more or less of the oil through the
  • control module 26 In a preferred embodiment of the invention, the control module 26
  • control module 26 includes a signal input "I COMP " for
  • the signal "S C0MP" may be generated electrically, mechanically, hydraulically, or
  • pneumatically and is selected by a user of the system such as by use of a toggle or rotary
  • a binary state, flow control valve 23 of the control module 26 is either "open" or
  • valve 23 When the signal indicates "low cool” mode, the valve 23 is opened so that a set amount of the hydraulic oil is shunted away from the compressor motor 22.
  • a set amount of the hydraulic oil is shunted away from the compressor motor 22.
  • flow-set valve 25 is used to set the proportion of the oil that is accepted through the control module 26 rather than being provided to the compressor motor 22.
  • the valve 25 is used to set the proportion of the oil that is accepted through the control module 26 rather than being provided to the compressor motor 22.
  • valve 25 may also provide for
  • additional cooling modes may provide for a continuous range of adjustment
  • motor 22 may turn 1800 rpm in high cool mode and only 1400 rpm in low cool mode.
  • valve 25 is best determined empirically.
  • the hydraulic power unit 10 also includes a fan or- blower for blowing
  • the 10 includes a hydraulic blower motor 28 for mechanically driving a blower 29.
  • hydraulic circuit 17 routes the pressurized hydraulic oil to the blower motor 28 as well as
  • blower motor control module 30 for controlling the amount of the hydraulic oil that is
  • the blower motor 28 and the blower control module 30 are coupled in parallel. Particularly, both the blower motor 28 and the blower control module 30 receive hydraulic oil from the circuit
  • blower control module 30 controls the amount of oil provided to the blower
  • motor 28 to be substantially constant, or at least independent of the speed of the engine 12
  • VVPC type pump 24 employs a VVPC type pump 24 to accomplish this purpose.
  • blower control module 30 configured for the simple case where the VVPC pump 24 is used. In that case, the blower control
  • module 30 may simply provide for a “blower on” and a “blower off mode of operation,
  • blower control module 30 The blower control module 30
  • a binary state, flow control valve 33 of the control module 30 is either "open" or
  • blower control module 30 may
  • blower speeds may be modified to provide for two blower speeds, or additional blower speeds, and may
  • blower output either manually or automatically, remotely or locally.
  • control module may include a variable flow-set valve 35 that is automatically controlled
  • blower motor is defined by the rate of flow of the oil to the blower motor
  • control module 30 may provide a transducer 36 tor measuring the ml pressure and. a compensating controller ⁇ $
  • control module 26 can be similarly adapted to compensate for variable pump output.
  • control module 26 may be considered to define a compressor portion 40 (shown in Figure
  • blower motor control module 30 define a blower portion 42 (shown in Figure 1 between
  • circuit 17 are shown in series in Figure 1, it should be understood that they may be provided in parallel with no loss of generality.
  • the temperature control portion 44 of the circuit 17. The temperature control portion 44
  • 17 includes an oil temperature control module 46, a heat exchanger 48 and an oil
  • a hydraulic line 17a, ( Figure 1) routes the hydraulic oil from the blower
  • the heat exchanger is provided for cooling oil that is too hot, however the heat exchanger could be used for heating oil that is too cold, and two heat exchangers could be
  • the temperature control module 46 as will be readily apparent to persons of ordinary skill.
  • the heat exchanger can exchange heat with the air cooled by the refrigeration system 14
  • the oil is preferably always passed through the reservoir 50, however this is not
  • the reservoir 50 provides room for the oil to expand as it is
  • the control module 46 receives oil from the pump 24 and senses the oil
  • the temperature control module 46 provides a controller 56 including three valves V 1 , V 2 , and V 3 that together define three different flow configurations, or patterns of oil flow F 1 , F 2 , and F 3 , depending on the sensed temperature
  • the controller defines a warm-up flow configuration whereby the valve V 1 is closed to
  • valve V 2 is also closed to prevent
  • valve V 3 is open to recirculate the oil to the pump 24, in
  • valve V 2 is opened to permit oil to flow through the heat exchanger
  • the compressor and blower portions 40 and 42 of the circuit 17 may also be closed.
  • valves "V” may be solenoid controlled in response to electrical signals issued
  • an electrical controller 56 where the electrical controller receives an electrical signal
  • V are provided in the form of "three-way thermostatic control valves" that provide the advantage of automatic control without the need for any electrical or other source of
  • valves are commercially available, e.g., from Fluid Power Energy, Inc. of
  • diverter valves Three-way thermostatic control valves (hereinafter "diverter valves") employ a
  • valves are factory set at predetermined
  • a single diverter valve provides for a "straight-through" fluid flow path
  • valve V is closed when the oil temperature is below T L .
  • valve V 2 is closed when the oil temperature is below T H , and the valve V 3 is closed
  • Two diverter valves V D , and V 02 may be employed to be responsive to the two different temperatures as shown in Figure 7.
  • the diverter valve V D has a wax set-point temperature of T H and defines a straight-through fluid flow path "STRAIGHT-THROUGH,” and a bypass fluid flow path "BYPASS,.”
  • the diverter valve V D2 has a wax set-point temperature of T L and defines a straight-through fluid flow path "STRAIGHT-THROUGH 2 " and a bypass fluid
  • valve V 01 received from the valve V 01 is diverted to the reservoir 50 through the path STRAIGHT-
  • FIG 8 shows a preferred hydraulic power unit 100 for the refrigeration system 14 of Figure 1.
  • the power unit 100 is substantially the same as the power unit 10 of
  • Ha 2 routes the hydraulic oil from the blower portion 42 of the hydraulic circuit 17 to a
  • temperature control module 46a rather than to the reservoir 50.
  • FIG. 9 shows the oil temperature control module 46a of the preferred embodiment
  • the temperature control module 46a includes a valve V la
  • valve V a routes the oil through a flow path F la leading to the compressor
  • the valve may variably apportion the flow between the two paths but is preferably a binary state valve that provides for full flow through a selected one of the flow paths while completely
  • valve is preferably simply
  • valve V ]a is set to route oil to either the heat exchanger 48 or the
  • the oil is caused to flow through the path F jb to a diverter valve V 03 .
  • diverter valve V 03 has a wax set-point temperature of T H and defines a straight-through
  • Oil received from point C ( Figure 1) through the hydraulic line 17a 2 is also provided to the input "I" of the diverter valve V D3 for processing through the diverter valve.
  • the compressor motor 22 typically has a motor shaft 22a and
  • the compressor 16 has a compressor shaft 16a.
  • prior art compressors that are
  • not coupled directly to an internal combustion engine include a pulley adapted to receive
  • a belt couples the first pulley to the second pulley.
  • the pulley has been provided for the purpose of adjusting the gearing ratio between the two shafts.
  • an axial coupler is typically used to coaxially couple the shaft of the compressor 16
  • the rotating mass of the internal combustion engine provides
  • a coupler 62 is preferably employed that
  • a vibration dampener 64 is preferably
  • the vibration dampener is preferably a
  • metal disk or flywheel that is mounted to either the shaft 16a or the shaft 22a but may
  • the hydraulic motor 22 has a relatively
  • vibration dampener is highly desirable in practice.
  • the vibration dampener is also desirable.
  • the compressor motor 22 and the compressor 16 are preferably both mounted, e.g., by bolting or welding, to a rigid mount 60 so that alignment between the compressor
  • the coupler 62 is preferably flexible, such as by having at
  • enclosure 66 is provided to prevent inadvertent access to rotating parts.
  • SUBSTITUTE SHEET (JRULE 26) be implemented by various means, automatic, semi-automatic, or manual, distributed or

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

La présente invention a trait à un bloc hydraulique pour un système de réfrigération. Selon un aspect de l'invention, le bloc hydraulique est agencé pour la commande du système de réfrigération d'un camion comprenant un moteur pour la propulsion du camion et une prise de force à partir du moteur. Le système de réfrigération comporte un compresseur pour la compression d'un réfrigérant et un évaporateur qui est refroidi par le réfrigérant comprimé. Le bloc hydraulique comporte une pompe, un moteur de compresseur, et un circuit hydraulique. La pompe est adaptée pour le pompage de fluide hydraulique et pour être reliée à la prise de force pour la commande de la pompe. Le moteur de compresseur est adapté pour l'entraînement du compresseur suite à la réception de fluide hydraulique provenant de la pompe. Le circuit hydraulique est adapté pour le transport du fluide hydraulique depuis la pompe jusqu'au moteur de compresseur et pour le transport en retour du fluide hydraulique depuis le compresseur vers la pompe.
PCT/US2005/018300 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration WO2007011324A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP05857690A EP1904321A4 (fr) 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration
AU2005334526A AU2005334526A1 (en) 2005-07-18 2005-07-18 Hydraulic power unit for a refrigeration system
CA002576917A CA2576917A1 (fr) 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration
PCT/US2005/018300 WO2007011324A1 (fr) 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration
IL179574A IL179574A0 (en) 2005-07-18 2006-11-26 Hydraulic power unit for a refrigeration system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2005/018300 WO2007011324A1 (fr) 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration

Publications (1)

Publication Number Publication Date
WO2007011324A1 true WO2007011324A1 (fr) 2007-01-25

Family

ID=37669104

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2005/018300 WO2007011324A1 (fr) 2005-07-18 2005-07-18 Bloc hydraulique pour systeme de refrigeration

Country Status (5)

Country Link
EP (1) EP1904321A4 (fr)
AU (1) AU2005334526A1 (fr)
CA (1) CA2576917A1 (fr)
IL (1) IL179574A0 (fr)
WO (1) WO2007011324A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11685225B2 (en) 2019-12-20 2023-06-27 Lovis, Llc Power takeoff-driven refrigeration

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016203733A1 (de) * 2015-03-09 2016-10-06 Hanon Systems Klimaanlagensystem für Motorfahrzeuge

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4352455A (en) * 1979-08-10 1982-10-05 Klockner-Humboldt-Deutz Ag Arrangement for heating the service cabin of a machine driven by an internal combustion engine
US4352456A (en) * 1980-06-09 1982-10-05 J. I. Case Company Cab heating system
US4487364A (en) * 1982-12-27 1984-12-11 Kl/o/ ckner-Humboldt-Deutz AG Arrangement for heating the operator's cabin of a machine driven by an internal combustion engine
US5085269A (en) * 1989-10-23 1992-02-04 Sanden Corporation Hydraulically driven heating and air conditioning system for vehicles such as mobile cranes
US6308665B1 (en) * 1997-05-02 2001-10-30 Valeo, Inc. Vehicle hydraulic component support and cooling system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2832103B1 (fr) * 2001-11-15 2004-05-28 Laurence Verot Dispositif de climatisation et vehicule a moteur ainsi equipe
US7086241B2 (en) * 2004-05-28 2006-08-08 Hydracool, Inc. Hydraulic power unit for a refrigeration system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4352455A (en) * 1979-08-10 1982-10-05 Klockner-Humboldt-Deutz Ag Arrangement for heating the service cabin of a machine driven by an internal combustion engine
US4352456A (en) * 1980-06-09 1982-10-05 J. I. Case Company Cab heating system
US4487364A (en) * 1982-12-27 1984-12-11 Kl/o/ ckner-Humboldt-Deutz AG Arrangement for heating the operator's cabin of a machine driven by an internal combustion engine
US5085269A (en) * 1989-10-23 1992-02-04 Sanden Corporation Hydraulically driven heating and air conditioning system for vehicles such as mobile cranes
US6308665B1 (en) * 1997-05-02 2001-10-30 Valeo, Inc. Vehicle hydraulic component support and cooling system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1904321A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11685225B2 (en) 2019-12-20 2023-06-27 Lovis, Llc Power takeoff-driven refrigeration

Also Published As

Publication number Publication date
EP1904321A4 (fr) 2009-08-05
CA2576917A1 (fr) 2007-01-25
IL179574A0 (en) 2008-03-20
AU2005334526A1 (en) 2007-01-25
EP1904321A1 (fr) 2008-04-02

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