US20150033771A1

US20150033771A1 - Modular refrigeration and heat reclamation chiller

Info

Publication number: US20150033771A1
Application number: US14/449,663
Authority: US
Inventors: John P. Meade; Alexander J. Meade
Original assignee: Emerald Environmental Technologies
Current assignee: Emerald Environmental Technologies
Priority date: 2013-08-02
Filing date: 2014-08-01
Publication date: 2015-02-05
Also published as: CA2858340A1

Abstract

The present technology provides a modular refrigeration and heat reclamation chiller system comprising an evaporator configured to vaporize a refrigerant to cool the refrigerant, a compressor coupled to the evaporator and configured to compress the refrigerant, a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor, a sub-cooler coupled to the condenser and configured to receive the refrigerant from the condenser so as to selectively extract heat from the refrigerant and to transfer the refrigerant to the evaporator, and an expansion valve coupled to both the sub-cooler and the evaporator.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

The present application claims priority to and the benefit of the filing date of U.S. Provisional Application No. 61/861,646 filed on Aug. 2, 2013, the entire disclosure of which is incorporated herein by reference.

FIELD

This technology relates to a modular refrigeration and heat reclamation chiller. The modular refrigeration and heat reclamation chiller contains a chiller system comprising a compressor in circuit with multiple heat exchangers. The compressor operates at a lowered compression ratio. More specifically, the modular refrigeration and heat reclamation chiller can be stacked to form a modular shape.

BACKGROUND OF THE INVENTION

A facility may be equipped with cooling and heating needs, such as an ice rink. The temperature of an ice rink is regulated to cool and maintain ice in the rink, but also, heating may be needed, for example to heat the inside of the building containing the ice rink or heat water for later usage.
Generally, conventional technologies for chilling fluids fail to reclaim heat and therefore fail to use both the chilled and heated fluids in facilities' operations. Moreover, chilling and/or heating devices may have any one of or a combination of the following undesirable characteristics: a large footprint; difficult to install, repair, and operate; and lack a compact size and/or shape. Thus, there is still a need for an alternative chiller system.

SUMMARY OF THE INVENTION

This technology relates to a modular refrigeration and heat reclamation chiller. The modular refrigeration and heat reclamation chiller contains a chiller system comprising a compressor in circuit with multiple heat exchangers.
In one aspect, the present technology provides a modular refrigeration and heat reclamation chiller system comprising an evaporator configured to vaporize a refrigerant to cool the refrigerant, a compressor coupled to the evaporator and configured to compress the refrigerant, a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor, a sub-cooler coupled to the condenser and configured to receive the refrigerant from the condenser so as to selectively extract heat from the refrigerant and to transfer the refrigerant to the evaporator, and an expansion valve coupled to both the sub-cooler and the evaporator.
In one embodiment, the condenser, the evaporator, and the expansion valve each have a refrigerant capacity, the refrigerant capacities of all of the condenser, the evaporator, and the expansion valve are greater than the refrigerant capacity of the compressor.
In one embodiment, the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 6:1 relative to the compressor.
In one embodiment, the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 4.5:1 relative to the compressor.
In one embodiment, the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 4:1 relative to the compressor.
In one embodiment, a heat transfer fluid processed by the system has a temperature drop of less than about 7° F. across the evaporator.
In one embodiment, the refrigerant processed by the system has a temperature drop of less than about 60° F. across the evaporator.
In one embodiment, the refrigerant processed by the system has a pressure drop of less than about 10 psig across the evaporator.
In one embodiment, the heat transfer fluid processed by the system has a temperature of less than about 8° F. at the compressor.
In one embodiment, the temperature of the refrigerant emerging from the evaporator is less than about 80° F.
In one embodiment, the refrigerant processed by the system has a temperature drop of at least than about 30° F. across the condenser.
In one embodiment, a pressure drop of the refrigerant across the condenser is less than about 11 psig.
In one embodiment, the heat transfer fluid processed by the system has a rise in temperature of less than about 10° F. at the condenser.
In one embodiment, the refrigerant processed by the system has a temperature drop of at least than about 40° F. across the sub-cooler.
In one embodiment, a pressure drop of the refrigerant across the sub-cooler is less than about 1.5 psig.
In one embodiment, the heat transfer fluid processed by the system has a drop in temperature of at least about 40° F. across the sub-cooler.
In one embodiment, the system further comprises a cabinet.
In one aspect, the present technology provides a method of using a modular refrigeration and heat reclamation chiller system comprising the step of circulating both a refrigerant and a heat transfer fluid through the system comprising an evaporator configured to vaporize a refrigerant to cool a refrigerant, a compressor coupled to the evaporator and configured to compress the refrigerant, a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor to the refrigerant, a sub-cooler coupled to the condenser and configured to receive the refrigerant from the condenser so as to selectively extract heat from the refrigerant and to transfer the refrigerant to the evaporator, and an expansion valve coupled to both the sub-cooler and the evaporator.
In one embodiment, the system provides a heated heat transfer fluid of about 100° F. and a refrigerated heat transfer fluid of about 10° F.
In one aspect, the present technology provides a method of manufacturing a modular refrigeration and heat reclamation chiller system comprising providing a modular refrigeration and heat reclamation chiller system comprising an evaporator configured to vaporize a refrigerant to cool a refrigerant, a compressor coupled to the evaporator and configured to compress the refrigerant, a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor to the refrigerant, a sub-cooler coupled to the condenser and configured to receive the refrigerant from the condenser so as to selectively extract heat from the refrigerant and to transfer the refrigerant to the evaporator, and an expansion valve coupled to both the sub-cooler and the evaporator.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates an exemplary embodiment of a front view of a chiller system.

FIG. 2 illustrates an exemplary embodiment of a rear view of a chiller system.

FIG. 3 illustrates an exemplary embodiment of a left side view of a chiller system.

FIG. 4 illustrates an exemplary embodiment of a right side view of a chiller system.

FIG. 5 illustrates a schematic view of a chiller system.

FIG. 6 illustrates an exemplary embodiment of a front view of a chiller system.

FIG. 7 illustrates an exemplary embodiment of a rear view of a chiller system.

FIG. 8 illustrates an exemplary embodiment of a left side view of a chiller system.

FIG. 9 illustrates an exemplary embodiment of a top view of a chiller system.

DETAILED DESCRIPTION

Reference will now be made in detail to embodiments of the technology, examples of which are illustrated in the accompanying drawings. It is to be understood that other embodiments may be utilized and structural and functional changes may be made without departing from the respective scope of the technology.
Reuse of heated and cooled fluids from a chiller system 100 produces an environmentally conscious process and reduces waste otherwise released from the system. Non-limiting examples of places a chiller system 100 can be used include an ice rink facility, an airplane hangar, a commercial building, a residential home, apartment and/or condominium buildings, restaurants, food trucks, portable food and/or beverage dispensing carts, etc. Other suitable locations may include a location having a need to both cool and heat fluids.
The term fluid or heat transfer fluid may refer to at least one gaseous fluid, a liquid fluid, a superheated fluid, a supercooled fluid, a frozen fluid, or any combination thereof. For example, the fluid may be comprised of glycols, methanol, ethanol, water, waste fluids, steam, snow or other precipitation, and any combination thereof.
With reference to FIG. 1, a front view of a chiller system 100 is depicted. The chiller system 100 generally includes a power source 102. The power source 102 may include for example, an electrical source, batteries and/or fuel cells, electromechanical systems such as generators and alternators, solar power, and any combination thereof.
Although depicted on the front of the chiller system 100, at least one status light 104 and user interface 106 may optionally be provided at any location on the exterior or interior of cabinet 150 of the chiller system 100.
The at least one status light 104 may indicate whether the chiller system is on or off. In addition the status light 104 may be a plurality of lights. Status light 104 may be a display for operational information based on the chiller system 100.
User interface 106 may be used to show operations indicia, such as energy levels, capacity, output, measurement of time to complete a cycle, warnings, status updates, etc. Other known display information may be shown on the user interface 106. User interface 106 may be a screen, such as an LCD, LED, touch panel, keypad, sensor, etc. In an embodiment, user interface 106 may be partially or fully removable and/or remotely accessible to provide an operator information on the status of the chiller system 100. In an embodiment, user interface 106 may serve as a control system for controlling and protecting a motor of a compressor 300 and an expansion valve 250, depending on facility needs.
Cabinet 150 may further be equipped with at least one door 152 and handle 154. In an embodiment, cabinet 150 is in a modular enclosure, such as a cube-shaped enclosure. In an embodiment, cabinet 150 has removable doors and/or walls. In an embodiment, cabinet 150 has removable front, right, and left walls. The cabinet 150 may optionally include a top.
Cabinet 150 may be used to cover all the interior components of the chiller system 100. The cabinet 150 may be insulated, e.g., with a ¾ inch closed-cell insulation, fiberglass, polyurethane, cotton, wool, a combination thereof, and may further be made of other known and suitable materials. The cabinet 150 may be further insulated with insulation, e.g. weather stripping, on adjoining portions of the chiller 100 to contain any noise created in the cabinet 150. The compressor 300 inside of the cabinet 150 may also be insulated to ensure further noise absorption. The cabinet 150 may be formed of metal, e.g. stainless steel, plastic, wood, a combination thereof, and may further be made of other known and suitable materials. In an embodiment, cabinet 150 is formed by metal sheets with steel reinforcements, having removable panels for ease of access and service.
In addition, other optional components that may be incorporated with the chiller system 100 include at least one door 152, at least one door handle 154, a base 156, and legs and/or wheels 158. The at least one door 152 may allow an operator access to the interior portion of the chiller system 100. In an embodiment, door 152 is mounted on a front panel of the cabinet 150 and is hinged to the right in order to provide access to a control panel 106 mounted on an interior of the door. A base 156 may include legs and/or wheels 158 for increased portability of the chiller system 100.
With reference to FIG. 2, a rear view of a chiller system 100 is depicted. The chiller system 100 may optionally be equipped with at least one ball valve connection sub-cooler/preheater 108 and a valve wiring box 110. In an embodiment as illustrated by FIG. 2, various inlets and outlets for components of the chiller system 100 are generally depicted at 210, 220, 410, 420, which will be discussed further herein. A base 156 is depicted as having legs for supporting the chiller system 100.
FIG. 3 illustrates a left side view of the chiller system 100. On the left side of the chiller system 100, there may be a handle 154 on cabinet 150.
FIG. 4 illustrates a right side view of the chiller system 100. There may be a connection a power source 102, such as two voltage in lines as depicted in FIG. 4. On the right side of chiller system 100, there may be a handle 154 on cabinet 150. In another embodiment, the power source 102 may be connected to another portion and/or side of the cabinet 150.
FIG. 5 illustrates a schematic view of the chiller system 100. The chiller system 100 is comprised of at least three heat exchangers 200, 400, 500 and a compressor 300. In particular, a first heat exchanger may be an evaporator 200, a second heat exchanger may be a condenser 400, and a third heat exchanger may be a sub-cooler 500. In an alternative embodiment, the heat exchangers 200, 400, 500 may be selected from any one of an evaporator, condenser, and sub-cooler.
Evaporator 200 includes an inlet 210, an outlet 220, a refrigeration inlet 230, and a refrigeration outlet 240. The evaporator 200 may be in connection with an expansion valve 250. Expansion valve 250 can be selected from a suitable electronic expansion valve assembly. Generally, evaporator 200 selectively processes fluids by evaporating liquid to gas, or removing liquids from a mixture of fluids. Non-limiting examples of evaporators include, but are not limited to: natural circulation evaporators; falling film evaporator; rising film evaporator; multiple-effect evaporators; and climbing and falling-film plate evaporators.
In an embodiment, the evaporator 200 has a series of parallel plates dividing the evaporator 200 into two paths between the plates. In an embodiment, evaporator 200 may have a single plate or multiple plates.
In an embodiment, the temperature drop across the evaporator 200 of the liquid to be cooled is approximately 7° F. or less. In another embodiment, the temperature drop across the evaporator 200 of the liquid to be cooled is approximately 6.6° F. or less. In yet another embodiment, the temperature drop across the evaporator 200 of the liquid to be cooled is approximately 10° F. or less. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
In an embodiment, the temperature drop across the evaporator 200 of the refrigerant (not shown) is approximately 60° F. or less. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
In an embodiment, the pressure drop in the refrigerant across the evaporator 200 is equal to or less than 10 psig. In another embodiment, the pressure drop in the refrigerant across the evaporator 200 is equal to or less than 9 psig. In yet another embodiment, the pressure drop in the refrigerant across the evaporator 200 is equal to or less than 8.9 psig. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
In an embodiment, the expansion valve 250 may further connect with a sub-cooler 500, as will be described in more detail below; expansion valve 250 may connect a refrigeration outlet 540 of the sub-cooler 500 to the refrigeration inlet 430 of the condenser 400. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
Compressor 300 includes an inlet 310, an outlet 320, a refrigeration inlet 330, and a refrigeration outlet 340. For example, inlet 310 may be compressor suction. The compressor 300 may further include a first vibration absorber 350 and a second vibration absorber 351. Compressor 300 may have any one of a variety of pressures, such as a low pressure, medium pressure, high pressure, and/or super high pressure. Compressor 300 may have any one of a variety of capacities, such as a low capacity, medium capacity, and/or a high capacity. Generally, compressor 300 compresses and pressurizes a fluid, and releases the fluid in a controlled manner. Non-limiting examples of compressors include, but are not limited to: reciprocating compressor; rotary screw compressor; turbo compressor; air cooled compressor; and water cooled compressor. In an embodiment, the compressor 300 connects the refrigeration outlet 240 of the evaporator 200 to the refrigeration inlet 430 of the condenser 400.
In an embodiment, the compression ratio of the compressor 300 is reduced to a level of less than 6:1. In yet another embodiment, the compression ratio of the compressor 300 is reduced to a level of less than 5:1. In yet another embodiment, the compression ratio of the compressor 300 is reduced to a level of less than 4.5:1. In another embodiment, the compression ratio of the compressor 300 is reduced to a level of less than 4:1. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
The superheat at the compressor 300 is less than 8° F. In another embodiment, the superheat at the compressor 300 is less than less than 12° F., less than 10° F., or even less than 6° F. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
The compressor 300 may be a scroll compressor having a lower decibel (dB) level as compared to a reciprocating compressor. Scroll compressor technology may also refuse the sound emission in lower bands levels, levels which are annoying to a human ear. Two chiller systems 100 may emit less than approximately 60 dB at a distance of three feet. A conventional plant may emit approximately 100 dB at the same distance.
Condenser 400 includes an inlet 410, an outlet 420, a refrigeration inlet 430, and a refrigeration outlet 440. Generally, condenser 400 is a device used to condense a fluid into liquid through cooling. Non-limiting examples of condensers include, but are not limited to: surface condenser; Liebig condenser; Graham condenser; Allihn condenser; direct contact condenser, etc.
In an embodiment, the condenser 400 has a series of parallel plates dividing the condenser 400 into two paths between the plates. In an embodiment, condenser 400 may have a single plate or multiple plates.
The temperature drop in a refrigerant across the condenser 400 is substantially maintained so the refrigerant emerging through the refrigeration outlet 440 is less than 80° F. In another embodiment, the refrigerant emerging through the refrigeration outlet 440 of the condenser 400 is less than 90° F., less than 85° F., less than 82° F., less than 78° F., or less than 75° F. In another embodiment, the temperature drop in a refrigerant across the condenser 400 is substantially equal to or greater than 28° F. In yet another embodiment, the temperature drop in a refrigerant across the condenser 400 is substantially equal to or greater than 30° F. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
The temperature rise across the condenser 400 of the liquid to be heated is approximately 10° F. or less. In yet another embodiment, the temperature rise across the condenser 400 of the liquid to be heated is approximately 15° F. or less. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
The pressure drop of the refrigerant across the condenser 400 is equal to or less than 11 psig. In another embodiment, the pressure drop of the refrigerant across the condenser 400 is equal to or less than 11 psig. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
Sub-cooler 500 includes an inlet 510, an outlet 520, a refrigeration inlet 530, and a refrigeration outlet 540. Generally, sub-cooler 500 cools a refrigerant below its saturation temperature, forcing the fluid to change its phase. Sub-cooling may be performed inside or outside the heat exchanger represented by sub-cooler 500. Non-limiting examples of sub-coolers include condenser sub-cooling; total sub-cooling; artificial sub-cooling; natural sub-cooling; and mechanical sub-cooling; etc.
In an embodiment, the sub-cooler 500 has a series of plates dividing the sub-cooler 500 into two paths between the plates. In an embodiment, sub-cooler 500 may have a single plate or multiple plates.
In an embodiment, the temperature of the refrigerant at the refrigeration outlet 540 of the sub-cooler 500 is approximately equal to or less than 80° F.
In an embodiment, the pressure drop in the refrigerant across the sub-cooler 500 is equal to or less than 1.5 psig. In another embodiment, the pressure drop in the refrigerant across the sub-cooler 500 is equal to or less than 1.43 psig. In yet another embodiment, the pressure drop in the refrigerant across the sub-cooler 500 is equal to or less than 3 psig. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
In an embodiment, the temperature drop in the refrigerant across the sub-cooler 500 is approximately 40° F. and the temperature rise in the fluid between the inlet 510 and outlet 520 is up to 40° F. Here as elsewhere in the specification and claims, numerical values may be combined to form new or undisclosed ranges.
In an embodiment, the sub-cooler 500 has the capacity to reduce the refrigerant temperature by up to 40° F. while increasing the inlet fluid 510 temperature by up to 40° F., thus decreasing the horsepower of the cooling capacity of the chiller system 100 by approximately 20% per ton.
A refrigerant is at least one working fluid which transfers heat from or to the system, which is desirably excluded from environments where its presence or the presence of a relatively toxic refrigeration fluid would present health or safety concerns. Refrigerant may be circulated in the chiller system 100 using a refrigeration inlet 610 and a refrigeration outlet 620. The term refrigerant generally refers to, but is not limited to, one or more refrigerants, which may be present in one or more phases, e.g. liquid, gaseous, solid, and can include other non-refrigerant materials) in one or more phases. For example, the refrigerant mixture can include a liquid refrigerant present in gaseous and liquid form, as well as a lubricant material such as oil or another refrigerant serving also as a lubricant material. As another example, the refrigerant mixture can be distributed into the shell of an evaporator, such as by using a distributor to distribute the gaseous portion of the refrigerant mixture in a manner of flow that is different relative to the distribution and manner of flow of the liquid portion of the refrigerant mixture. In an embodiment, the manner of flow of the gaseous portion may be optimized to achieve a desired flow to facilitate heat transfer, such as in a uniform flow through the distributor, while the manner of flow of the liquid portion may be concentrated, and distributed by the distributor from a designated area, such phase biased distribution of the liquid versus the gaseous portion of the refrigerant mixture can be achieved.
The chiller system 100 may optionally include a sight glass 710, and/or a filter dryer 720.
FIG. 6 illustrates an embodiment of a front view of an assembled modular chiller system 100. In FIG. 6, a front view shows an evaporator refrigeration inlet 230, evaporator refrigeration outlet 240, expansion valve 250, compressor outlet 320, sight glass 710, and filter dryer 720.
FIG. 7 illustrates an embodiment of a rear view of an assembled modular chiller system 100. In FIG. 7, a rear view shows an evaporator 200, evaporator inlet 210, evaporator outlet 220, condenser 400, condenser inlet 410, condenser outlet 420, condenser inlet 410, sub-cooler inlet 510, and sub-cooler outlet 520.
FIG. 8 illustrates an embodiment of a side view of an assembled modular chiller system 100. In FIG. 8, a side view shows an evaporator 200, expansion valve 250, compressor 300, condenser 400, sub-cooler 500, sight glass 710, filter dryer 720, and vibration absorbers 350, 351. Further, FIG. 8 illustrates evaporator inlet 210, evaporator outlet 220, compressor inlet 310, condenser inlet 410, condenser outlet 420, condenser refrigeration inlet 430, condenser refrigeration outlet 440, sub-cooler inlet 510, and sub-cooler outlet 520.
FIG. 9 illustrates an embodiment of a top view of an assembled modular chiller system 100. In FIG. 9, a top view shows an evaporator 200, compressor 300, vibration absorbers 350, 351, condenser 400, sub-cooler 500, sight glass 710, and filter dryer 720.
In an embodiment, the following are provided for the chiller system 100: a compressor 300, having 20 tons of refrigeration capacity; a condenser 400, having a capacity of 22.2 tons of refrigeration; an expansion valve 250, having 49 tons of capacity; and an evaporator 200, having 29 tons of capacity.
In one embodiment, the chiller system 100 includes an evaporator 200, sub-cooler 500, expansion valve 250, filter dryer 720, and a sight glass 710. A fluid, such as a compressed vapor at outlet 320 is supplied to the refrigeration inlet 430 of the condenser 400, which forms a refrigerant condensate discharging from refrigeration outlet 440. The condensate from the condenser 400 at the refrigeration outlet 440 passes through piping to a liquid line sub-cooler refrigeration inlet 530. The liquid refrigerant is sub-cooled by 40° F. where it exits at refrigeration outlet 540. Through piping systems the liquid refrigerant then passes through a refrigeration sight glass 710 and a filter dryer 720, and then is metered by an electronic expansion valve 250. The saturated liquid is metered through the expansion valve 250 and supplied to refrigeration inlet 230 of the evaporator 200. In the evaporator 200, the saturated liquid completes its phase changes to a super-heated vapor and exits at the refrigeration outlet 240. A low temperature super-heated vapor is now connected through piping to the inlet 310 of the compressor 300. Within the compressor 300, the low temperature super-heated vapor is compressed and converted to a high pressure, high temperature vapor. This vapor exits the compressor at outlet 320. Although this generally forms a complete refrigeration circuit of the chiller system 100, additional processes may be included in this circuit. In the condenser 400 a high temperature super-heated refrigerant vapor has a phase change to a refrigerant liquid, wherein the heat produced by this phase change is absorbed by the fluid pumped through the condenser 400 from inlet 410 through outlet 420. In the sub-cooler 500, as the liquid refrigerant passes through the sub-cooler 500, the pumped fluid from the inlet 510 to the outlet 520 absorbs the heat sub-cooling the liquid refrigerant. In the evaporator 200, heat is extracted from the fluid pumped from inlet 210 and through outlet 220, and the fluid that emerges from the evaporator 200 is chilled. The evaporator 200, sub-cooler 500, and condenser 400 may each use more than one flat plate so fluid passing through transfers heat through these plates.
In an embodiment, the efficiency of the chiller system 100 is greater than 0.9 tons/hp. In an embodiment, the chiller system 100 is assembled in the cabinet 150 such that the evaporator 200 and condenser 400 are at opposing walls of the cabinet 150. The compressor 300 is located between the condenser 400 and evaporator 200, and is mounted on legs with a rubber mounting device, although an alternative mounting device may be envisioned. Within cabinet 150, a filter for the refrigerant is located in front of the compressor 300. Generally, the chiller system is contained within the cabinet 150.
FIGS. 1-9 illustrate non-limiting exemplary embodiments of the chiller system. Other examples of locations for placement, containment, and access to a chiller system may be envisioned. Other configurations and shapes, other than a substantially modular or cube shape may also be envisioned. Those skilled in the art will readily appreciate that changes and/or modifications may be made thereto without departing from the spirit and scope of the chiller system.
Other functionally inconsequential additives or steps may also be included without departing from the principles of this technology. While these articles expressly cover all foreseeable equivalents of the elements recited above, additional variations are possible. For example, it is possible to include a remote control for operating the chiller system.
The foregoing detailed description has been given for clearness of understanding only and no unnecessary limitations should be understood therefrom as some modifications will be obvious to those skilled in the art without departing from the scope and spirit of the appended claims.

Claims

Having thus described the invention, we claim:

1. A modular refrigeration and heat reclamation chiller system comprising:

an evaporator configured to vaporize a refrigerant to cool the refrigerant;

a compressor coupled to the evaporator and configured to compress the refrigerant;

a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor;

a sub-cooler coupled to the condenser and configured to receive the refrigerant from the condenser so as to selectively extract heat from the refrigerant and to transfer the refrigerant to the evaporator; and

an expansion valve coupled to both the sub-cooler and the evaporator.

2. The system of claim 1, wherein the condenser, the evaporator, and the expansion valve each have a refrigerant capacity, the refrigerant capacities of all of the condenser, the evaporator, and the expansion valve are greater than the refrigerant capacity of the compressor.

3. The system of claim 2, wherein the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 6:1 relative to the compressor.

4. The system of claim 2, wherein the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 4.5:1 relative to the compressor.

5. The system of claim 2, wherein the refrigerant capacity of the condenser, evaporator, sub-cooler, and expansion valve produce a compression ratio of less than about 4:1 relative to the compressor.

6. The system of claim 2, wherein a heat transfer fluid processed by the system has a temperature drop of less than about 7° F. across the evaporator.

7. The system of claim 6, wherein the refrigerant processed by the system has a temperature drop of less than about 60° F. across the evaporator.

8. The system of claim 7, wherein the refrigerant processed by the system has a pressure drop of less than about 10 psig across the evaporator.

9. The system of claim 8, wherein the heat transfer fluid processed by the system has a temperature of less than about 8° F. at the compressor.

10. The system of claim 9, wherein the temperature of the refrigerant emerging from the evaporator is less than about 80° F.

11. The system of claim 10, wherein the refrigerant processed by the system has a temperature drop of at least than about 30° F. across the condenser.

12. The system of claim 11, wherein a pressure drop of the refrigerant across the condenser is less than about 11 psig.

13. The system of claim 12, wherein the heat transfer fluid processed by the system has a rise in temperature of less than about 10° F. at the condenser.

14. The system of claim 13, wherein the refrigerant processed by the system has a temperature drop of at least than about 40° F. across the sub-cooler.

15. The system of claim 14, wherein a pressure drop of the refrigerant across the sub-cooler is less than about 1.5 psig.

16. The system of claim 15, wherein the heat transfer fluid processed by the system has a drop in temperature of at least about 40° F. across the sub-cooler.

17. The system of claim 16 further comprising a cabinet.

18. A method of using a modular refrigeration and heat reclamation chiller system comprising the step of:

circulating both a refrigerant and a heat transfer fluid through the system comprising:

an evaporator configured to vaporize a refrigerant to cool a refrigerant;

a condenser coupled to the compressor and configured to condense the refrigerant compressed by the compressor to the refrigerant;

an expansion valve coupled to both the sub-cooler and the evaporator.

19. The method of claim 18 wherein the system provides a heated heat transfer fluid of about 100° F. and a refrigerated heat transfer fluid of about 10° F.

20. A method of manufacturing a modular refrigeration and heat reclamation chiller system comprising:

providing a modular refrigeration and heat reclamation chiller system comprising:

an evaporator configured to vaporize a refrigerant to cool a refrigerant;

an expansion valve coupled to both the sub-cooler and the evaporator.