초록 ▼

The invention is directed to a heat exchanger with optimal performance and a method of optimizing the performance of a heat exchanger. The heat exchanger has a first manifold, a second manifold and tubes extending therebetween. The tubes have at least one opening which extends through the entire len

The invention is directed to a heat exchanger with optimal performance and a method of optimizing the performance of a heat exchanger. The heat exchanger has a first manifold, a second manifold and tubes extending therebetween. The tubes have at least one opening which extends through the entire length of the tubes. The method may include: governing the pressure drop in the heat exchanger by selecting different size openings or configurations of the tubes depending upon the type of refrigerant used and the properties thereof; optimizing the dimensions of the first manifold and second manifold, such that the ratio of manifold to tube size or manifold to tube opening cross sectional area yields low pressure drops and minimized the effects of pressure drop in the manifold and tube combination; and optimizing the ratio of the mass flow capacity of the first and second manifolds to the tubes flow capacity such that the first manifold has minimal or negligible mal-distribution effect when providing refrigerant to the tubes, thereby improving the overall performance of the heat exchanger.

대표청구항 ▼

1. A heat exchanger which optimizes the heat exchanger capacity, the heat exchanger comprising: a first manifold;a second manifold;a liquid baffle is provided in the second manifold, the liquid baffle allowing the second manifold to behave as a receiver and orifice, allowing excess liquid refrigeran

1. A heat exchanger which optimizes the heat exchanger capacity, the heat exchanger comprising: a first manifold;a second manifold;a liquid baffle is provided in the second manifold, the liquid baffle allowing the second manifold to behave as a receiver and orifice, allowing excess liquid refrigerant to continually accumulate in the second manifold;vertically oriented tubes extending in fluid communication between the first manifold and the second manifold;a ratio of the tube width to the effective cross sectional diameter of the first manifold and the second manifold (an “effective cross sectional ratio”) is less than 1.20;wherein the heat exchanger is capable of operating in either a condenser mode or an evaporator mode with virtually no adverse effect on system performance;wherein the heat exchanger has an inlet provided in the first manifold and an outlet provided in the second manifold, the second manifold having the liquid baffle to create a first chamber and a second chamber, and an opening proximate the liquid baffle, the opening extending from the first chamber to the second chamber;wherein the liquid baffle and orifice opening are configured and disposed to allow refrigerant liquid to pass through the opening, whereby gas accumulated in the second chamber is substantially trapped and prevented from passing through the opening. 2. The heat exchanger of claim 1 wherein multiple openings are provided in each tube, the openings extend the length of the tubes and are substantially evenly spaced in a single row and are of uniform size. 3. The heat exchanger of claim 1 wherein multiple openings are provided in each tube, the openings extend the length of the tubes and are unevenly spaced in a one or more rows and are of different size or shape. 4. A heat exchanger which optimizes the heat exchanger capacity, the heat exchanger comprising: a first manifold;a second manifold;a liquid baffle is provided in the second manifold, the liquid baffle allowing the second manifold to behave as a receiver and orifice, allowing excess liquid refrigerant to continually accumulate in the second manifold;vertically oriented tubes extending in fluid communication between the first manifold and the second manifold;a ratio of the tube width to the effective cross sectional diameter of the first manifold and the second manifold (an “effective cross sectional ratio”) is less than 1.20;wherein the heat exchanger is capable of operating in either a condenser mode or an evaporator mode with virtually no adverse effect on system performance;wherein the receiver and orifice, allowing excess refrigerant to continually accumulate in the second manifold, thereby providing additional heat transfer surface for condensing, whereby a refrigeration system to which the heat exchanger is attached achieves increased energy efficiency at partially loaded conditions. 5. The heat exchanger of claim 4 wherein the refrigerant is drawn into the tubes from a lowest vertical portion of the second manifold. 6. The heat exchanger of claim 1 wherein the liquid baffle in the second manifold separates the second manifold except a narrow opening at the bottom of the second manifold, thereby creating two chambers in the second manifold, the first chamber serves as a refrigerant receiver and the second chamber serves as a transition chamber and passage to and from a refrigerant connection. 7. The heat exchanger of claim 1 wherein the tubes extend between the first manifold and the second manifold in a vertical orientation, such that refrigerant flow is influenced by gravity or capillary effects within the tubes. 8. The heat exchanger of claim 1, wherein the heat exchanger is capable of operating in either the condenser mode or the evaporator mode with virtually no adverse effect on system performance, while simultaneously not requiring bypass valves to circumvent the receiver. 9. The heat exchanger of claim 1, wherein the effective cross sectional ratio is between about 0.90 to about 1.18. 10. The heat exchanger of claim 1, wherein the effective cross sectional ratio is less than 1.18. 11. The heat exchanger of claim 1, wherein the effective cross sectional ratio is less than 0.90.