DUAL PURPOSE REFRIGERANT PRESSURE VESSEL

Abstract

The present disclosure relates to a refrigerant pressure vessel having multiple purposes as both an accumulator and a receiver. When the refrigerant pressure vessel is configured in a first, horizontal orientation, it functions as a receiver. When the refrigerant pressure vessel is configured in a second, vertical orientation, it functions as an accumulator.

Description

FIELD OF DISCLOSURE

The present disclosure relates to modular heating, ventilation, and air conditioning (HVAC) systems and components thereof, and more particularly, to a component that can be used in an HVAC system to provide the functionality of two conventional devices.

BACKGROUND

HVAC systems are integral to modern infrastructure—providing essential heating, cooling, and ventilation to enclosed spaces and ensuring that individuals inside modern structures remain comfortable. However, HVAC systems are oftentimes large, bulky, and difficult to configure to smaller spaces. This is in part due to the large number of individual components, including a compressor system, an evaporator system, a condenser system, and the appropriate valves, regulators, filters, and electrical monitors to ensure that the HVAC system operates properly. These components must all be connected and located relatively close to one another. The result is a bulky HVAC system that is difficult to fit into smaller spaces or into spaces with existing physical obstructions. Furthermore, many of the individual components in HVAC systems and refrigerant systems are single-purpose, highly specialized, and large, further limiting available space.

Therefore, there is a long-felt need for HVAC system components that can be configured once and perform different functions when installed in an HVAC system.

SUMMARY

The present disclosure relates to a dual purpose refrigerant pressure vessel (referred to herein as the “refrigerant pressure vessel”) which can be operatively configured in a horizontal orientation or a vertical orientation to perform two different functions in an HVAC system depending on the orientation. When oriented horizontally, the refrigerant pressure vessel may operate as a receiver, and when oriented vertically, the refrigerant pressure vessel may operate as a suction accumulator. Although the same individual refrigerant pressure vessel cannot simultaneously function as both a receiver and a suction accumulator in the same HVAC system, the same refrigerant pressure vessel embodiment disclosed herein may be installed as either a receiver or as an accumulator, or both, by turns, in the same HVAC system.

The dual purpose refrigerant pressure vessel generally comprises a first end, a second end, a body, mounting hardware affixed to the body, a pair of end caps, a first tube which extends out of the body on the first end, and a second tube which extends out of the body on a second end.

The refrigerant pressure vessel may be oriented in a substantially horizontal configuration or a substantially vertical configuration. When the refrigerant pressure vessel is in a horizontal configuration, it can act as a high pressure liquid refrigerant holding tank, also known as a receiver. A receiver generally stores excess high pressure refrigerant liquid. When the refrigerant pressure vessel is in a vertical configuration it can act as a low-pressure liquid vapor separation tank, also known as an accumulator. Accumulators generally prevent liquid from entering a compressor, which typically intake only gases. The refrigerant pressure vessel can serve a dual purpose depending on how the refrigerant pressure vessel is oriented and can be utilized in an HVAC system according to the needs of an individual user. This enables a single part number to be used for either functionality, thereby increasing efficiency of operation in the construction of HVAC units.

In one embodiment of the present disclosure, the dual purpose refrigerant pressure vessel is a tubular body extending between a first end cap and a second end cap. The first end cap is connected to a first end of the tubular body. The second end cap is connected to the second end of the tubular body. A first tube is connected to the first end cap and extends therethrough such that the first tube has an internal portion inside of the tubular body and an external portion outside of the tubular body. A second tube is connected to the second end cap and extends therethrough such that the second tube has an internal portion inside of the tubular body and an external portion outside of the tubular body. The internal portion of the first tube has a distal end which is adjacent to the first end cap and the internal portion of the second tube has a distal end which is adjacent to the first end cap.

In an embodiment, the internal portion of the second tube extends greater than a majority of the length along the longitudinal axis of the tubular body without making contact with the first end cap.

In an embodiment, the internal portion of the first tube extends less than the majority of the length along the longitudinal axis of the tubular body.

In an embodiment, the distal end of the internal portion of the second tube extends along the longitudinal axis of the tubular body beyond the distal end of the internal portion of the first tube.

In an embodiment, the distal end of the internal portion of the second tube and the distal end of the internal portion of the first tube each comprise an angled configuration with respect to the longitudinal axis of the tubular body. In an embodiment, the angle formed by the distal ends of the first tube and second tube are between 30 and 60 degrees, and the angled portions face opposing sides of the tubular body.

In an embodiment, the dual purpose refrigerant pressure vessel also includes a mounting flange extending from the tubular body. In an embodiment, the mounting flange is integrally formed with the tubular body.

In an embodiment, when the longitudinal axis of the tubular body is disposed in a vertical orientation, the first end cap is disposed above the second end cap and a center of the first end cap and a center of the second end cap are aligned along the vertically disposed longitudinal axis.

In an embodiment, when tubular body is disposed in a horizontal orientation, the first end cap is disposed across from the second end cap and a center of the first end cap and a center of the second end cap are aligned along the horizontally disposed longitudinal axis.

In an embodiment, the internal portion of the second tube includes a passageway that extends through the second tube. In an embodiment, the passageway is disposed adjacent the second end cap.

In an embodiment, the length of the portion of the internal portion of the second tube is contiguous with a portion of the first tube within the cavity of the vessel.

Accordingly, it is an object of the disclosure not to encompass within the disclosure any previously known product, process of making the product, method of using the product, or method of treatment such that Applicants reserve the right and hereby disclose a disclaimer of any previously known product, process, or method. It is further noted that the disclosure does not intend to encompass within the scope of the disclosure any product, process, or making of the product or method of using the product, which does not meet the written description and enablement requirements of the USPTO (35 U.S.C. § 112, first paragraph) or the EPO (Article 83 of the EPC), such that Applicants reserve the right and hereby disclose a disclaimer of any previously described product, process of making the product, or method of using the product disclosed herein.

It is noted that in the present disclosure and particularly in the claims and/or paragraphs, terms such as “comprises,” “comprised,” “comprising” and the like can have the meaning attributed to them in U.S. patent law; e.g., they can mean “includes,” “included,” “including,” and the like; and that terms such as “consisting essentially of” and “consists essentially of” have the meaning ascribed to them in U.S. patent law; e.g., they allow for elements not explicitly recited, but exclude elements that are found in the prior art or that affect a basic or novel characteristic of the invention.

These and other embodiments are disclosed or are obvious from and encompassed by the following Brief Description of the Drawings and Detailed Description.

DESCRIPTION OF THE DRAWINGS

FIG. 1 is an embodiment of the present disclosure and depicts a dual purpose refrigerant pressure vessel with a first end, a second end, mounting hardware, a body, a first tube, a second tube, and a pair of end caps.

FIG. 2 is an embodiment of the present disclosure and depicts a dual purpose refrigerant pressure vessel with a first end, a second end, mounting hardware, a body, a first tube, a second tube, and a pair of end caps.

FIG. 3 is an embodiment of the present disclosure and depicts a sectional view of a dual purpose refrigerant pressure vessel.

FIG. 4 is an embodiment of the present disclosure and depicts a sectional view of a dual purpose refrigerant pressure vessel.

FIG. 5 is an embodiment of the present disclosure and depicts an end view of a dual purpose refrigerant pressure vessel.

FIG. 6 is an embodiment of the present disclosure and depicts an end view of a dual purpose refrigerant pressure vessel.

FIG. 7 is an embodiment of the present disclosure and depicts a partial view of a dual purpose refrigerant pressure vessel in a vertical configuration to function as an accumulator.

FIG. 8 is an embodiment of the present disclosure and depicts an end view of a dual purpose refrigerant pressure vessel oriented in a horizontal configuration to function as a receiver.

FIG. 9 is an embodiment of the present disclosure and depicts a view of a dual purpose refrigerant pressure vessel in a horizontal configuration acting as a receiver in an HVAC or refrigeration system.

FIG. 10 is an embodiment of the present disclosure and depicts a view of a dual purpose refrigerant pressure vessel in a horizontal configuration acting as a receiver in an HVAC or refrigeration system.

FIG. 11 is an embodiment of the present disclosure and depicts a view of a dual purpose refrigerant pressure vessel in a vertical configuration acting as a suction accumulator in an HVAC or refrigeration system.

FIG. 12 is an embodiment of the present disclosure and depicts a view of a dual purpose refrigerant pressure vessel in a vertical configuration acting as a suction accumulator in an HVAC or refrigeration system.

DETAILED DESCRIPTION

The following detailed description, given by way of example, but not intended to limit the invention solely to the specific embodiments described, may best be understood in conjunction with the accompanying drawings.

FIGS. 1-12 depict a dual purpose refrigerant pressure vessel 100. The dual purpose refrigerant pressure vessel 100 may function as either an accumulator or as a receiver in an HVAC system depending on the refrigerant pressure vessel's orientation within an HVAC or refrigeration system.

In traditional HVAC systems the receiver and the accumulator serve different purposes and are distinct components which cannot be interchanged. In general, the accumulator is operatively connected with a suction line upstream of a compressor and downstream of an evaporator. The purpose of the accumulator is to prevent liquid from entering the compressor, which generally is limited only to intake of refrigerant vapors. In general, the receiver is typically positioned on the liquid line downstream from the condenser. The receiver stores excess liquid not needed during circulation.

In the present disclosure, when the dual purpose refrigerant vessel 100 is configured in a substantially horizontal configuration, the vessel is capable of serving as the receiver for an HVAC or refrigeration system. When the dual purpose refrigerant vessel 100 is configured in a substantially vertical configuration the vessel 100 is capable of serving as the accumulator for an HVAC or refrigeration system. Because the same component can be installed to serve as either an accumulator or as a receiver, the overall complexity of an HVAC system is reduced, allowing a user to purchase a smaller variety of different components, thereby increasing efficiency.

FIGS. 1-12 generally depict a dual purpose refrigerant vessel 100. The vessel 100 comprises a first end 102, a second end 104, a body 108 having a first end 102 and a second end 104.

In the embodiment depicted in FIGS. 1-12, the body 108 is comprised of a substantially cylindrical perimeter wall. In the embodiment shown in FIGS. 1-12, a cavity is formed between the first end 102, second end 104, and perimeter wall of the body 108.

In alternative embodiments, the body 108 may comprise any shape as may be required or desired to operate in an HVAC or refrigeration system.

In the embodiment depicted in FIGS. 1-12, end caps 114a, 114b are affixed to both ends of the body 108. In the embodiment depicted in FIGS. 1-12, each end cap 114a, 114b includes an aperture configured to receive a tube 110, 112, as described herein.

In the embodiment depicted in FIGS. 1-12, the vessel 100 further comprises a first tube 110 and a second tube 112. In this embodiment, the first tube 110 is disposed within the aperture of an end cap 114a, and the second tube 112 is disposed within the aperture of the opposite end cap 114b. The first tube 110 comprises an internal portion 120a disposed within the cavity of the vessel 100 and an external portion 120b extending away from the end cap 114a and exposed outside of the vessel 100. The second tube 112 comprises an internal portion 120a disposed within the cavity of the vessel 100 and an external portion 122b extending away from the end cap 114b and exposed outside of the vessel 100.

In an embodiment, the vessel 100 and all of its components, including the first and second tubes 110, 112 are comprised of a combination of metal materials including, but not limited to, copper and steel. In alternative embodiments, the vessel 100 may be comprised of any other material capable of withstanding high pressures without rupturing, including, but not limited to, hard plastics, composites, and other materials.

The body 108 also includes mounting hardware 106. In the embodiment depicted in FIGS. 1-6 & 8-12, the mounting hardware 106 comprises two legs which extend from the body 108. In this embodiment, the mounting hardware 106 is integral with and comprised of the same material as the body 108. The mounting hardware 106 may be any apparatus or device that facilitates the body 108 being installed in an HVAC or refrigeration system. The mounting hardware 106 permits the vessel 100 to be installed in a desired orientation (i.e., horizontal or vertical) with a desired operability. The mounting hardware 106 may be formed separate from the body 108 and connected thereto by conventional apparatus or devices.

In an embodiment, the mounting hardware 106 may be comprised of any material that is suitable to secure the vessel 100 to an evaporator unit or condenser unit. FIGS. 1-12 depict an embodiment of the vessel 100 wherein the mounting hardware 106 is depicted as a pair of “legs.” In alternative embodiments, the vessel 100 may comprise any geometry of appropriate strength to secure the vessel 100.

As depicted in FIG. 5, the first tube 110, second tube 112 are disposed within the vessel 100 in the same sector as the mounting hardware 106. In an embodiment, the sector is defined and enclosed by two radii having an angle β (beta) and extending from the longitudinal axis y to the lateral outer edge of the mounting hardware 106. In an embodiment, angle β is between 60 degrees and 120 degrees. In an embodiment, the angle β is between 85 to 95 degrees.

The vessel 100 permits refrigerant to pass through the first tube 110 and/or second tube 112 and into the cavity of the vessel. The refrigerant may be any refrigerant, and is preferably a refrigerant used in an HVAC system or refrigeration system. Refrigerant may move through the vessel in either direction depending on the vessel's orientation and use.

When used as a receiver (i.e., horizontal orientation), as depicted in FIGS. 9-10, liquid refrigerant enters the vessel 100 via the second tube 112 proximate the second end 104, and may exit the vessel 100 via the first tube 110 proximate the first end 102.

When used as an accumulator (i.e., vertical orientation), as depicted in FIGS. 11-12, liquid and vapor enter the vessel 100 via the first tube 110 proximate the first end 102 and vapor exits the vessel 100 via the second tube 112 proximate the second end 104 and into a compressor.

In each of the embodiments depicted in FIGS. 9-12, the external portion 120b of the first tube 110 is proximate the first end 102 and may connect to a condenser when the vessel is in a horizontal configuration and to a compressor when the vessel is in a vertical configuration. The internal portion 120a of the first tube 110 is adjacent to the internal portion 122a of the second tube 112.

FIGS. 9-12 depict embodiments which show the flow of fluid through the first and second tubes 110, 112 in horizontal and vertical orientation. In alternative embodiments, the flow of fluid may be reversed. As depicted in FIGS. 3-4, the internal portion 120a of the first tube 120 and the internal portion 122a of the second tube 112 are offset and may be contiguous along an exterior surface thereof. As depicted in FIGS. 11-12, when the vessel 100 is in a vertical orientation, the external portion 122b of the second tube 112 may connect to a compressor to function as an accumulator. As depicted in FIGS. 9-10, when the vessel 100 is in the horizontal orientation, the external portion 122b of the second tube 112 may connect to a condenser to receive high pressure liquid refrigerant.

In an embodiment, the internal portions 120a, 122a of the first and second tubes 110, 112 comprise different lengths. The internal portion 120a of the first tube 110 is shorter in length than the internal portion 122a of the second tube 112.

In the preferred embodiment, each of internal end of the tubes 120a, 122a features an angled cut depicted in FIG. 7 as σ (theta) and σ′ (theta prime). The angled cuts σ, σ′ at the end of each of the internal tubes 120a and 122a improves the flow of fluid through the vessel 100 by providing a larger flow area at the ends of the tubes 120a, 122a which reduces turbulence of fluid. In an embodiment, the angled cuts σ, σ′ at the end of each of the internal tubes is approximately 45 degrees. In another embodiment the angle cut is between 30 and 60 degrees. In an embodiment, the angled cuts σ, σ′ are not the same angle, but collectively add up to 90 degrees. In an embodiment, the angled cuts σ, σ′ face in opposite directions from one another (as depicted in FIG. 7). In alternative embodiments, the internal ends of the tubes 120a, 122a do not feature an angled cut.

Receiver Configuration

FIGS. 9-10 depict the vessel 100 in a substantially horizontal orientation to function as a receiver. The vessel (functioning as a receiver) 100 of FIGS. 9-10 intakes high pressure hot refrigerant liquid from the condenser and stores excess refrigerant that is not needed for the heat exchange circulation. The high pressure hot refrigerant liquid may then exit the receiver as required and is transported to an evaporator through valves and other flow controls.

As depicted in FIGS. 9-10, the external portion 122b of the second tube 112 receives high pressure hot liquid from a condenser. The high pressure hot liquid enters the cavity of the vessel 100 by means of the second tube 112. The refrigerant exits the internal portion 122a of the second tube 112 and pools within the cavity of the vessel 100. When high pressure hot liquid refrigerant is required by the HVAC system, the refrigerant may move through vessel 100 from the internal portion 122a of the second tube 112, into the internal portion 120a of the first tube 110, and then can exit the vessel 100 through the external portion 120b of the first tube 110.

FIG. 8 depicts an end view of a dual purpose refrigerant vessel 100 oriented in a horizontal configuration to function as a receiver. In FIG. 8, the bottom horizontal line is the minimal liquid level 200 required for the vessel 100 to operate as a receiver. The liquid level needs to be fully above the internal openings of both tubes 110, 112 or else gas can enter the vessel, negating the separation and liquid storage function. The tubes 110, 112 may or may not have the same diameter. The top horizontal line reflects a general industry safety guideline which states that receivers should not be sized to hold more refrigerant than 80% of their total volume (i.e., a maximal liquid level 202). As known to those having ordinary skill in the art, the volume of the vessel 100 may be calculated from the radius 204 and length of the vessel. Each jurisdiction may have specific rules regarding this safety factor. FIG. 8 also depicts the radii of the vessel, which would be used for sizing purposes, dictating the bottom line's position. FIG. 8 is not related to the accumulator configuration discussed below.

In an embodiment, when the vessel 100 is in an horizontal orientation to act as a receiver, liquid refrigerant is consistently fed into the second tube 112 to ensure that the volume of liquid refrigerant stay above the minimal liquid level. The minimal liquid level is above the first and second tubes 110, 112 which allows gravity to naturally remove the liquid refrigerant from the vessel 100 via the first tube 110 (i.e., without any suction force). So long as the volume of liquid refrigerant is maintained above the minimal liquid level, gas may accumulate above the liquid refrigerant. In an embodiment, the external portion of the first tube 110b may attach to various valves to control the flow of refrigerant exiting the vessel 100.

When the vessel 100 is in the receiver configuration, the refrigerant liquid may include oil or other impurities without malfunctioning the vessel 100 or HVAC system.

Accumulator Configuration

FIGS. 11-12 depict the vessel 100 in a substantially vertical orientation to function as an accumulator. The vessel (functioning as an accumulator) 100 of FIGS. 11-12 intakes low pressure cool gas refrigerant and excess liquid from the evaporator. The accumulator 100 is configured to prevent too much liquid from exiting the accumulator 100 and entering a compressor. As depicted in FIGS. 11-12, low pressure gas enters the vessel 100 through the external portion 120b of the first tube 110. The vessel 100 restricts the flow of liquid out of the vessel 100, while gas refrigerant is removed from the vessel 100 via the second tube 112. Specifically, liquids accumulate along the bottom of the vessel 100 (i.e., proximate the second end cap). Upon exiting the internal portion 120a of the first tube 110, gas/vapor refrigerant accumulates within the cavity of the vessel 100, and may exit the vessel 100 by entering the internal portion 122a, and flowing out the external portion 122b of the second tube 112. Upon exiting the vessel 100, the vapors may enter a compressor.

In an embodiment, the compressor is in fluid connection with the vessel 100 such that when the vessel 100 is in a vertical orientation to function as an accumulator, gaseous refrigerant (and excess liquid and/or oil) is pulled into the vessel 100 via the first tube 110. The excess liquid and/or oil accumulate within the cavity of the vessel 100, proximate the second end cap 114b. The suction force from the compressor pulls a desired flow of gaseous refrigerant into the internal portion of the second tube 122a and out of the vessel 100 via external portion of the second tube 122b before entering the compressor.

A hole 124 is formed on the internal portion 122a of the second tube 112 proximate the second end cap. The hole 124 shown in FIG. 12 forms a passageway for any oil that has flowed into the accumulator to exit the vessel 100 via the second tube 112 at a rate controlled by the diameter of the hole 124. When the gaseous refrigerant enters the first tube 110 and into the vessel 100 it may be accompanied by a small stream of excess liquid and/or oil. The hole 124 allows a marginal stream of oil to exit from the vessel 100 via second tube 112. This marginal stream prevents too much oil from exiting the vessel 100 and entering the compressor at one time, which if unmetered, could damage the compressor.

The hole 124 is sized to meet a desired mass flow rate of oil and/or liquid from the vessel 100 which will not damage a compressor. The desired mass flow rate of oil can be determined by the relationship between the diameter of the tubing, the diameter of the hole 124, and the properties of the refrigerant and oil flowing therethrough and is known to one of skill in the art.

The lengths of the first tube 110 and second tube 112 are integral to the function of the vessel 100 as an accumulator. As shown in FIGS. 1-12, the internal portion 122a of the second tube 112 extends nearly the entire length of the vessel 100 along the longitudinal axis y of the vessel 100 without contacting the first end cap 114a. This configuration ensures that liquids flow to the bottom (second end cap 114b) of the vessel 100 and prevents the liquids from entering the mouth of the internal portion 122a of the second tube 112. In an embodiment, the internal portion 122a of the second tube 112 extends greater than half the length of the vessel 100, but less than the full length of the vessel 100 along its longitudinal axis y. In another embodiment, the internal portion 122a of the second tube 112 extends greater than three quarters of the length of the vessel 100, but less than the full length of the vessel 100 along its longitudinal axis y.

For similar reasons, the length of the first tube 110 is substantially shorter than the second tube 112. This configuration prevents the internal portion 120a of the first tube 110 from being submerged in liquid. In an embodiment, the internal portion 120a of the first tube 110 extends less than half the length of the vessel 100 along its longitudinal axis y. In another embodiment, the internal portion 120a of the first tube 110 extends less than one quarter of the length of the vessel 100 along its longitudinal axis y. In another embodiment, the collective lengths of the internal portion 120a of the first tube 110 and the internal portion 122a of the second tube 112 add up to approximately the entire length of the vessel 100 along its longitudinal axis y.

Although the present invention and its advantages have been described in detail, it should be understood that various changes, substitutions, and alterations can be made herein without departing from the spirit and scope of the invention as defined in the appended claims. Having thus described in detail preferred embodiments of the present invention, it is to be understood that the invention defined by the above paragraphs is not to be limited to particular details set forth in the above description as many apparent variations thereof are possible without departing from the spirit or scope of the present invention.

Claims

1. A dual purpose refrigerant pressure vessel comprising: a tubular body extending between a first end cap connected to a first end of the tubular body and a second end cap connected to a second end of the tubular body;wherein the first end cap includes a first tube connected thereto and extending therethrough and including an internal portion disposed inside the tubular body and an external portion disposed outside the tubular body;wherein the second end cap includes a second tube connected thereto and extending therethrough and including an internal portion disposed inside the tubular body and an external portion disposed outside the tubular body; andwherein the internal portion of the first tube includes a distal end disposed adjacent the first end cap and the internal portion of the second tube includes a distal end disposed adjacent the first end cap.

2. The dual purpose refrigerant pressure vessel of claim 1, wherein the internal portion of the second tube extends greater than a majority of a length along a longitudinal axis of the tubular body without contacting the first end cap.

3. The dual purpose refrigerant pressure vessel of claim 2, wherein the internal portion of the first tube extends less than the majority of the length along the longitudinal axis of the tubular body.

4. The dual purpose refrigerant pressure vessel of claim 3, wherein the distal end of the internal portion of the second tube extends along the longitudinal axis of the tubular body beyond the distal end of the internal portion of the first tube.

5. The dual purpose refrigerant pressure vessel of claim 4, wherein the distal end of the internal portion of the second tube and the distal end of the internal portion of the first tube each comprise an angled configuration with respect to the longitudinal axis of the tubular body.

6. The dual purpose refrigerant pressure vessel of claim 1, further comprising a mounting flange extending from the tubular body.

7. The dual purpose refrigerant pressure vessel of claim 6, wherein, when the longitudinal axis of the tubular body is disposed in a vertical orientation the first end cap is disposed above the second end cap and a center of the first end cap and a center of the second end cap are aligned along the vertically disposed longitudinal axis.

8. The dual purpose refrigerant pressure vessel of claim 6, wherein the tubular body is disposed in a horizontal orientation, the first end cap is disposed across from the second end cap and a center of the first end cap and a center of the second end cap are aligned along the horizontally disposed longitudinal axis.

9. The dual purpose refrigerant pressure vessel of claim 1, wherein the internal portion of the second tube includes a passageway that extends through the second tube.

10. The dual purpose refrigerant pressure vessel of claim 9, wherein the passageway is disposed adjacent the second end cap.

11. A refrigerant pressure vessel comprising: a first end, a second end, and a perimeter wall extending therebetween,a cavity defined within the first end, second end, and perimeter wall,a first tube extending through the first end and into the cavity of the vessel,a second tube extending through the second end and into the cavity of the vessel,wherein, a portion of the second tube disposed within the cavity of the vessel has a length that is greater than a majority of a length of the perimeter wall along a longitudinal axis of the perimeter wall and has a distal free end that is disposed adjacent to without contacting the first end cap and is contiguous with a portion of the first tube within the cavity of the vessel.

12. The refrigerant pressure vessel of claim 11, wherein the portion of the second tube disposed within the cavity extends greater than three quarters of the length between the second end and first end of the perimeter wall along the longitudinal axis of the perimeter wall.

13. The refrigerant pressure vessel of claim 12, wherein the portion of the first tube disposed within the cavity extends the length between the first end and the distal free end of the second tube.

14. The refrigerant pressure vessel of claim 13, wherein the portions of the first and second tubes disposed within the cavity have distal free ends with angled cuts facing opposing sides of the perimeter wall, the angled cuts being between 30 and 60 degrees.

15. The refrigerant pressure vessel of claim 11, further comprising a passageway extending through an outer surface of the second tube, the passageway disposed adjacent to the second end of the refrigerant pressure vessel.

16. The refrigerant pressure vessel of claim 11, wherein the refrigerant pressure vessel is integrally formed from a single piece of material.

17. The refrigerant pressure vessel of claim 11, wherein the refrigerant pressure vessel is formed from a mixture of metals.

18. The refrigerant pressure vessel of claim 11, wherein the refrigerant pressure vessel is formed from a hard plastic.

19. The refrigerant pressure vessel of claim 11, further comprising a mounting surface.

20. The refrigerant pressure vessel of claim 19, wherein the mounting surface is integrally formed with the perimeter wall.