TECHNICAL FIELD
The present disclosure relates generally to an internal heat exchanger, and more specifically, to a co-axial tube heat exchanger adapted to be used in a heat recovery system of an air conditioning system.
BACKGROUND
Typically, an air conditioning system for an automotive application includes a plurality of devices such as a compressor, a condenser, an expansion device, and an evaporator to establish a refrigeration circuit. The plurality of devices is coupled to each other through tubes and hoses so that the refrigeration circuit can be operated while exchanging heat among these devices. Further, the air conditioning system includes one or more heat recovery systems to recover waste heat energy from these devices. The heat recovery systems assist in attaining a relatively higher level of performance and efficiency of the air conditioning system.
The one or more heat recovery systems includes an internal heat exchanger adapted to extract heat from a specific section of the refrigeration circuit operating between the condenser and the expansion valve to another section of the refrigerant circuit operating between the evaporator and the compressor. The internal heat exchanger exchanges heat between a high temperature refrigerant and a low temperature refrigerant. For example, when the internal heat exchanger is disposed within the compressor and the condenser, the internal heat exchanger exchanges heat between the high temperature refrigerant coming out of the condenser and the low temperature refrigerant entering in to the compressor.
Out of various internal heat exchangers, a co-axial tube heat exchanger is widely used as an internal heat exchanger. The co-axial tube heat exchanger includes an inner tube which is enclosed within an outer tube. A vapor refrigerant flows in an interior space of the inner tube and a liquid refrigerant flows in an

intermediate space between the inner tube and the outer tube in a counter flow fashion. As a result, heat exchange takes place between the vapor refrigerant and the liquid refrigerant.
However, the existing co-axial tube heat exchanger has several limitations in the design and a high manufacturing cost. For example, the existing co-axial tube heat exchanger incurs significant manufacturing cost and packaging space, due to a relatively lower heat rejection rate per unit length, and a higher pressure drop characteristics. Further as both the inner and outer pipes are secured to each other at their respective ends, the existing co-axial tube heat exchanger has a tendency of producing vibration noise during operating conditions. Furthermore, an annular space between the inner tube and the outer tube is significantly reduced beyond an optimum range during a bending operation in the existing co-axial tube heat exchanger. As a result, the heat exchanging capability of the co-axial tube heat exchanger is severally affected.
Therefore, in light of the foregoing discussion, there exists a need to overcome the aforementioned drawbacks in the heat exchanging capability, manufacturing cost and design of the co-axial tube heat exchanger.
SUMMARY
The present disclosure seeks to provide a co-axial tube heat exchanger adapted to be used in a heat recovery system of an air conditioning system.
In an aspect, the co-axial tube heat exchanger includes a first pipe of a first diameter. The first pipe includes an outer surface, an inner surface and a first cavity extending longitudinally along an axis of the first pipe. The outer surface of the first pipe is exposed to a surrounding environment and the inner surface of the first pipe is adapted to include a first ridge profile and a second ridge profile extending longitudinally along the axis of the first pipe. The inner surface of the first pipe is exposed to the first cavity. Further, the first ridge profile and the second ridge profile are disposed on the inner surface in a manner to maintain a predetermined angular distance between them.
The co-axial tube heat exchanger includes a second pipe of a second diameter and the second pipe is adapted to be co-axially disposed within the first cavity of the first pipe to create a first fluid flow path which is an area between the inner surface of the first pipe and an outer surface of the second pipe. The outer surface of the second pipe includes a surface profile extending longitudinally along the axis of the second pipe. The surface profile is adapted to provide support to the first ridge profile and the second ridge profile causing locking of the second pipe with the first pipe and creating two partitions within the first fluid flow path.
The co-axial tube heat exchanger includes a first set of inlet and outlet ports disposed on the first pipe for the first fluid, wherein the first fluid flows within the partitions of the first fluid flow path. Further, a first opening and a second opening on the second pipe is provided for the second fluid. The second fluid flows within a second fluid flow path disposed within an inner cavity of the second pipe, wherein heat exchange between the first fluid and the second fluid occurs while the first and second fluids flow through the respective fluid flow paths.
In an embodiment, the inner surface of the first pipe includes a cavity profile extending longitudinally along the axis of the first pipe and an outer surface of the second pipe includes a third ridge profile, wherein the cavity profile is adapted to mate with the third ridge profile to create a third partition within the first fluid flow path.
The present disclosure provides a co-axial tube heat exchanger that has enough annular space between the co-axially aligned first and second tube even at bending points so that efficiency of the co-axial tube heat exchanger is not affected at the bending points which are normally required in a piping layout of the internal heat exchanger. As a result, the efficiency of the co-axial tube heat exchanger is substantially increased.
Additional aspects, advantages, features and objects of the present disclosure would be made apparent from the drawings and the detailed description of the illustrative embodiments construed in conjunction with the appended claims that follow.
It will be appreciated that features of the present disclosure are susceptible to being combined in various combinations without departing from the scope of the present disclosure as defined by the appended claims.
BRIEF DESCRIPTION OF THE DRAWINGS
The summary above, as well as the following detailed description of illustrative embodiments, is better understood when read in conjunction with the appended drawings. For the purpose of illustrating the present disclosure, exemplary constructions of the disclosure are shown in the drawings. However, the present disclosure is not limited to specific methods and instrumentalities disclosed herein. Moreover, those in the art will understand that the drawings are not to scale. Wherever possible, like elements have been indicated by identical numbers.
Embodiments of the present disclosure will now be described, by way of example only, with reference to the following diagrams wherein:
Figure1 is a schematic Illustration of an exemplary block diagram of a co-axial tube heat exchanger in accordance with the embodiment of the disclosure;
Figures 2A and 2B are schematic illustrations of exploded perspective views of a first embodiment and a second embodiment of the co-axial tube heat exchanger respectively in accordance with an embodiment of the present disclosure;
Figures 3Aand 3B are schematic illustrations of cross-sectional views of the first and second embodiments of the co-axial tube heat exchanger respectively in accordance with an embodiment of the present disclosure; and
Figures 4A-C are schematic illustrations of sectional views of the first embodiment of the co-axial tube heat exchanger along cutting planes A-A, B-B, and C-C of Figure 1 respectively, in accordance with an embodiment of the present disclosure; and
Figure 5 is a schematic illustration of sectional view of the second embodiment of the co-axial tube heat exchanger along a cutting plane C-C of Figure 1 in accordance with an embodiment of the present disclosure.
In the accompanying drawings, an underlined number is employed to represent an item over which the underlined number is positioned or an item to which the underlined number is adjacent. A non-underlined number relates to an item identified by a line linking the non-underlined number to the item. When a number is non-underlined and accompanied by an associated arrow, the non-underlined number is used to identify a general item at which the arrow is pointing.
DETAILED DESCRIPTION
The following detailed description illustrates embodiments of the present disclosure and ways in which they can be implemented. Although some modes of carrying out the present disclosure have been disclosed, those skilled in the art would recognize that other embodiments for carrying out or practicing the present disclosure are also possible.
FIG. 1 is a schematic Illustration of an exemplary block diagram of a co-axial tube heat exchanger 100 in accordance with the embodiment of the disclosure. The co-axial tube heat exchanger 100 includes a first pipe 102 and a second pipe 104. The first pipe 102 may also be referred to as an outer pipe and the second pipe 104 may also be referred to as an inner pipe of the co-axial tube heat exchanger 100. The first pipe 102 has a first diameter and the first pipe 102 includes a first cavity extending longitudinally along an axis of the first pipe 102. The second pipe 104 has a second diameter and the second pipe 104 is adapted to be co-axially disposed within the first cavity of the first pipe 102.
The second diameter of the second pipe 104 is smaller than the first diameter of the first pipe 102 so that an intermediate space exists between an inner surface of the first pipe 102 and an outer surface of the second pipe 104 when the second pipe 104 is co-axially disposed within the first pipe 102. The intermediate space acts as a first fluid flow path so that a first fluid flows through the intermediate space between the first pipe 102 and the second pipe 104.
Further, the first pipe 102 includes a first port cavity 106 and a second port cavity 108. In an embodiment, the first port cavity 106 and the second port cavity 108 are formed on the first pipe 102 using a stamping process. In another embodiment, the first port cavity 106 and the second port cavity 108 are formed on the first pipe 102 through a drilling process. As illustrated in Figure 1, an inlet pipe 112 is coupled to an inlet port 116 which is disposed on the first port cavity 106 and an outlet pipe 114 is coupled to an outlet port 118 which is disposed on the second port cavity 108.The inlet pipe 112 is used for receiving the first fluid within the intermediate space between the first pipe 102 and the second pipe 104. The outlet pipe 114 is used for delivering out the first fluid from the intermediate space between the first pipe 102 and the second pipe 104.
In an embodiment, the second pipe 104 includes a first opening 122, a second opening 124 and an inner cavity extending along a longitudinal axis of the second pipe 104. The inner cavity of the second pipe 104 defines a second fluid flow path in such a way that a second fluid enters the second pipe 104 through the first opening 122 and flows through the inner cavity of the second pipe 104 and leaves the second pipe 104 through the second opening 124.
During working of the co-axial tube heat exchanger 100, the first fluid flows through the intermediate space between the first pipe 102 and the second pipe 104 in a first direction and the second fluid flows through the inner cavity of the second pipe 104 in a direction opposite to the first direction. As a result, heat exchange takes place between the two fluids while flowing through respective fluid flow paths within the co-axially aligned first pipe 102 and the second pipe 104.
In an embodiment, the co-axial tube heat exchanger 100 is installed within a condenser and a thermal expansion valve of the air conditioning system. Accordingly, the first pipe 102 is disposed between the condenser and the thermal expansion valve in a manner such that the inlet pipe 112 is coupled to an outlet port of the condenser and an outlet pipe 114 is coupled to an inlet port of the thermal expansion valve. Further, second pipe 104 is disposed within an evaporator and a compressor in a manner such that the first opening 122 is coupled to an outlet of the evaporator and the second opening 124 is coupled to an inlet of the compressor. The first fluid from the condenser enters the co-axial tube heat exchanger 100 through the inlet pipe 112, flows through the intermediate space between the first pipe 102 and the second pipe 104 and leaves the co-axial tube heat exchanger 100 through the outlet pipe 114 and proceeds toward the inlet port of the thermal expansion valve. The second fluid from the evaporator enters the co-axial tube heat exchanger 100 through the first opening 122, flows through the inner cavity of the second pipe 104, and leaves toward the inlet of the compressor through the second opening 124. While passing through the intermediate space, the first fluid transfers heat to the second fluid which is flowing in an opposite direction in the inner cavity of the second pipe 104.As a result, the co-axial tube heat exchanger 100 recovers excess heat from the first fluid and the temperature of the first fluid after passing through the co-axial tube heat exchanger 100 is reduced substantially before entering the thermal expansion valve.
Figure 1 further illustrates enlarged views of the ends of the first pipe 102. A first enlarged view 126 illustrates an enlarged view of a first end 132 and a second enlarged view 128 illustrates an enlarged view of a second end 134 of the first pipe 102. The first end 132 and the second end 134 are crimped on the outer surface of the second pipe 104 so that the opposing ends of the intermediate space between the inner surface of the first pipe 102 and the outer surface of the second pipe 104 are properly sealed. The crimped ends 132 and 134 of the first pipe 102 avoids any loss of the first fluid while flowing through the first fluid flow path in the co-axial tube heat exchanger 100. Specifically, a process of crimping is performed before a brazing process is performed at the first end 132 and the second end 134. In an embodiment, the first pipe 102 and second pipe 104 are locked with each other at the first end 132 and the second end 134 using at least one of a clinching process, a deforming process, a pressing process or a combination thereof. Such type of locking of the first pipe 102 with the second pipe 104 creates a single sub-assembly before processing the co-axial tube heat exchanger 100 for a furnace brazing or a manual brazing operation. The completion of the brazing operation results into a leak proof joint between the first pipe 102 and the second pipe 104.
Referring to Figure 2A, an exploded perspective view of a first embodiment of the co-axial tube heat exchanger 100 is illustrated in accordance with an embodiment of the present disclosure. The first pipe 102 includes a first cavity 202 extending longitudinally along the axis of the first pipe 102. Further, an outer surface of the first pipe 102 is exposed to the surrounding environment and the inner surface of the first pipe 102 is adapted to include a plurality of ridge profiles such as a first ridge profile 204a, and a second ridge profile 204b collectively referred herein to as a ridge profile 204. The plurality of ridge profiles 204 extends longitudinally along the axis of the first pipe 102. In addition, the plurality of ridge profiles 204 are disposed on the inner surface of the first pipe 102 in a manner so that a predetermined angular distance is maintained between the plurality of ridge profiles 204 along the axis of the first pipe 102.
During assembly of the co-axial tube heat exchanger 100, the second pipe 104 is disposed within the first cavity 202 of the first pipe 102 wherein the plurality of ridge profiles 204 coincides with the outer surface of the second pipe 104. The outer surface of the second pipe 104 includes a surface profile extending longitudinally along the axis of the second pipe 104 wherein the surface profile is adapted to provide support to the ridge profiles 204 causing locking of the second pipe 104 with the first pipe 102. Further, the inner surface of the first pipe 102 includes a cavity profile 206 extending longitudinally along the axis of the first pipe 102 and the outer surface of the second pipe 104 includes a third ridge profile 204c.
During an assembly process of this embodiment of the co-axial tube heat exchanger 100, the two ridge profiles 204a and 204b coincides with the outer surface of the second pipe 104 and creates two partitions in the first fluid flow path. The mating of the cavity profile 206 with the third ridge profile 204c causes an additional i.e., a third partition within the first fluid flow path. Thus, the plurality of ridge profiles 204 (i.e., 204a, 204b and 204c) partitions the intermediate space i.e., the first fluid flow path between the inner surface of the first pipe 102 and the outer surface of the second pipe 104 into multiple partitions along the length of the first pipe 102. Consequently, the first fluid flow path has multiple partitions and the first fluid flows through these multiple partitions. In an embodiment, an area between the multiple partitions of the first fluid flow path is determined using the angular distance maintained between the plurality of ridge profiles 204.

In addition, the mating of the third ridge profile 204c with the cavity profile 206 causes a sealing along the length of the first pipe 102. The sealing prevents leakage of the first fluid between multiple partitions of the first fluid path. Moreover, mating of the cavity profile 206 with the third ridge profile 204c avoids rotation of the second pipe 104 within the first pipe 102.
Further, the outer surface of the second pipe 104 includes at least two rows of a plurality of turbulent zones 212. Referring to the Figure 2A, a row 210a of the plurality of turbulent zones 212 is illustrated. Another row 210b (not shown) of the plurality of turbulent zones 212 is disposed in an opposite direction of the row 210a. In an embodiment, the at least two rows 210a and 210b of the plurality of turbulent zones 212 are disposed at an angular orientation of 180 degrees relative to each other on both sides of the at least one of the first and second ridge profiles. The plurality of turbulent zones 212 are designed and configured in such a manner so that a turbulent flow can be generated within the multiple partitions of the first fluid flow path. The turbulent flow increases heat transfer from the first fluid to the second fluid while the first fluid is flowing in a first direction in the multiple partitions of the first fluid flow path and the second fluid is flowing in a direction opposite to the first direction in the inner cavity of the second pipe 104.
In an embodiment, outer surface of the second pipe has concave passages 214 formed on it, in such a way that concave passages 214 are oriented towards the first port cavity 106 and second port cavity 108 of first pipe 102. In addition, each of the inlet pipe 112 and the outlet pipe 114 has an expanded portion. The expanded portions of the inlet pipe 112 and the outlet pipe 114 rest on to the first port cavity 106 and the second port cavity 108 respectively. Alternatively, each of the inlet pipe 112 and the outlet pipe 114 has a bulge profile which acts as a stopper and ensures limited entry of the inlet pipe 112 and outlet pipe 114 within the first pipe 102.
Further, a flow dispersal chamber and a flow collector chamber is formed at the entry and exit of the first fluid flow path. The flow dispersal chamber and the flow collector chamber will be explained later in reference to Figure 4 of the description.
Referring to Figure 2B, an exploded perspective view of a second embodiment of the co-axial tube heat exchanger 100 is illustrated in accordance with an embodiment of the present disclosure. The first pipe 102 includes the plurality of ridge profiles such as the first ridge profile 204a, the second ridge profile 204b and the third ridge profile 204c. The plurality of ridge profiles 204 extends longitudinally along the axis of the first pipe 102. In addition, the plurality of ridge profiles 204 are disposed on the inner surface of the first pipe 102 in a manner so that a predetermined angular distance is maintained between the plurality of ridge profiles 204 along the axis of the first pipe 102.
In an embodiment, multiple rows such as the row 210a, 210b of the plurality of turbulent zones 212 are disposed at an angular orientation of 120 degrees in such a manner so that each row of the plurality of turbulent zones 212 is surrounded by two ridge profiles 204 to create a tri-partition flow arrangement having equal free flow area within the first fluid flow path.
During assembly of this embodiment of the co-axial tube heat exchanger 100, the second pipe 104 is disposed within the first cavity 202 of the first pipe 102, wherein the plurality of ridge profiles 204 coincides with the outer surface of the second pipe 104. As a result, the plurality of ridge profiles 204 provides support to positioning of the second pipe 104 within the first cavity 202 and partitions the first fluid flow path into multiple partitions.
In an alternate embodiment, the outer surface of the second pipe 104 is adapted to include a plurality of cavity profiles such as a first cavity profile, a second cavity profile and a third cavity profile extending longitudinally along the axis of the second pipe 104. The plurality of cavity profiles on the outer surface of the second pipe 104 are adapted to respectively mate with the plurality of ridge profiles 204 of the first pipe 102. For example, each cavity profile of the plurality of cavity profiles includes a cavity along the longitudinal axis of the second pipe 104 so that any protruding portion of the ridge profile 204 fits within the cavity disposed on the outer surface of the second pipe 104. Such mating of the cavity profile and the ridge profile causes a relatively strong support for the positioning of the second pipe 104 within the first cavity 202 of the first pipe 102.
During a working of the co-axial tube heat exchanger 100, the first fluid is passed through the inlet pipe 112 and is flown through the partitioned first fluid flow path. The first fluid exchanges heat with the second fluid flowing within the inner cavity of the second pipe 104. After exchanging the heat with the second fluid, the first fluid is drawn out of the partitioned first fluid flow path from the outlet pipe 114. Due to the heat transfer from the first fluid toward the second fluid within the co-axial tube heat exchanger 100, a temperature of the first fluid exiting the outlet pipe 114 is substantially lower than a temperature of the first fluid entering the inlet pipe 112.
The creation of the multiple partitions within the first fluid flow path i.e., within the intermediate space between the inner surface of the first pipe 102 and the outer surface of the second pipe 104 provides several advantages. The multiple partitions provide additional contact surfaces for the first fluid with the second pipe 104 causing an increase in the heat transfer efficiency of the co-axial tube heat exchanger 100. Additionally, the multiple partitions support the second pipe 104 within the first cavity 202 of first pipe 102 throughout the longitudinal axis of the first pipe 102. Consequently, minimal vibration noise is generated and the co-axial tube heat exchanger 100 becomes a relatively strong and stable internal heat exchanger.
Figure 3A illustrates a cross sectional view of the first embodiment of the co-axial tube heat exchanger 100 of Figure 2A, wherein out of three partitions two partitions include two rows of the plurality of turbulent zones 212 spaced at angular orientation of 1800 on the outer surface of second pipe 104.The cross-sectional view indicates a width LT of turbulent zone and distance PT between the two consecutive turbulent zones 212 of the co-axial tube heat exchanger 100. Figure 3B illustrates a cross sectional view of the second embodiment of the co-axial tube heat exchanger 100 of Figure 2B when the first fluid is flowing through the multiple partitioned first fluid flow path. As illustrated, turbulent patterns 302 are formed in the flow path of fluid flowing through each partition formed by the assembly of the first pipe 102 and the second pipe 104.
Figure 4A illustrates a sectional view of the first embodiment of the co-axial tube heat exchanger 100 along a cutting plane A-A of Figure 1. Figure 4A illustrates flow dispersal chambers 402 at an entry of the first fluid path disposed within the intermediate space between the inner surface of the first pipe 102 and the outer surface of the second pipe 104. Further, two flow dispersal chambers402 can be observed in Figure 4A.In addition, a direction of an entry of the fluid within the flow dispersal chambers is illustrated using arrows 404 and 406.
Figure 4B illustrates a sectional view of the first embodiment of the co-axial tube heat exchanger 100 along a cutting plane B-B of Figure 1. Figure 4B illustrates flow collector chambers412 at an exit of the first fluid path disposed within the intermediate space between the inner surface of the first pipe 102 and the outer surface of the second pipe 104. Further, two flow collector chambers412 can be observed in Figure 4B.In addition, a direction of an exit of the fluid from the flow collector chambers is illustrated using arrows 414 and 416.
Figure 4C illustrates a sectional view of the first embodiment of the co-axial tube heat exchanger 100 along a cutting plane C-C of Figure 1. Figure 4C illustrates a cavity profile 206 of the first pipe 102, a first and second ridge profiles 204a & 204b on the first pipe 102, a third ridge profile 204c on the second pipe 104. Further, the first fluid is flowing through the tri-partitioned first fluid flow path wherein a predetermined area ratio (A1, A2, A3) is characterized by an angular orientation (?1, ?2, ?3) in such a way that ?2 = ?3 & ?1 < 40% of ?2.
Figure 5 illustrates a sectional view of the second embodiment of the co-axial tube heat exchanger 100 along a cutting plane C-C of Figure 1. Figure 5 illustrates a first ridge profile 204a on the first pipe 102, a second ridge profile 204bon the first pipe 102, and a third ridge profile 204c on the first pipe 102. Further, the first fluid is flowing through the tri-partitioned first fluid flow path wherein the tri-partitioned have equal area ratios (A11 = A22 = A33), in such a way that ?11= ?22 = ?33= 120 degrees.
The present disclosure offers several advantages. The present disclosure directs the fluid from which heat energy is to be extracted into a bounded and partitioned flow path along the longitudinal axis of the outer pipe of the co-axial tube heat exchanger. Specifically, the flow path for the first fluid is partitioned into at least three flow paths. Because of an increased interaction of the fluid with the surface area of the inner tube, heat exchange ability of the co-axial tube heat exchanger is improved in a considerable manner. Further, inner tube of the co-axial tube heat exchanger is supported across the length of the outer tube causing a stable and a robust heat exchanger which can be employed in mobile working conditions. As a result, reliability and durability of the co-axial tube heat exchanger is substantially improved. Moreover, an overall cost of manufacturing of the co-axial tube heat exchanger is also reduced.
Modifications to embodiments of the present disclosure described in the foregoing are possible without departing from the scope of the present disclosure as defined by the accompanying claims. Expressions such as “including”, “comprising”, “incorporating”, “have”, “is” used to describe and claim the present disclosure are intended to be construed in a non-exclusive manner, namely allowing for items, components or elements not explicitly described also to be present. Reference to the singular is also to be construed to relate to the plural.

WE CLAIM:
1. A co-axial tube heat exchanger comprising:
a first pipe of a first diameter, including an outer surface, an inner surface and a first cavity extending longitudinally along an axis of the first pipe, wherein the outer surface is exposed to a surrounding environment, the inner surface is adapted to include a first ridge profile and a second ridge profile extending longitudinally along the axis of the first pipe and the inner surface is exposed to the first cavity, wherein the first ridge profile and the second ridge profile are disposed on the inner surface in a manner to maintain a predetermined angular distance there between;
a second pipe of a second diameter, adapted to be co-axially disposed within the first cavity of the first pipe to create a first fluid flow path which is an area between the inner surface of the first pipe and an outer surface of the second pipe, wherein the outer surface of the second pipe includes a surface profile extending longitudinally along the axis of the second pipe, wherein the surface profileis adapted to provide support to the first ridge profile and the second ridge profile causing locking of the second pipe with the first pipe and creating two partitions within the first fluid flow path;
a first set of inlet and outlet ports disposed on the first pipe for the first fluid, wherein the first fluid flows within the partitions of the first fluid flow path; and
a first opening and a second opening on the second pipe for the second fluid, wherein the second fluid flows within a second fluid flow path disposed within an inner cavity of the second pipe, wherein heat exchange between the first fluid and second fluid occurs while the first and second fluids flow through the respective fluid flow paths.

2. The co-axial tube heat exchanger as claimed in claim 1, wherein the inner surface of the first pipe includes a cavity profile extending longitudinally along the axis of the first pipe and an outer surface of the second pipe includes a third ridge profile, wherein the cavity profile is adapted to mate with the third ridge profile to create a third partition within the first fluid flow path.

3. The co-axial tube heat exchanger as claimed in claim 2, wherein the outer surface of the second pipe includes at least two rows of a plurality of turbulent zones being axially aligned and spaced apart along the longitudinal axis of the second pipe.

4. The co-axial tube heat exchanger as claimed in claim 3, wherein the at least two rows of the plurality of turbulent zones are disposed at an angular orientation of 180 degrees on both sides of the at least one of the first, second and third ridge profiles.

5. The co-axial tube heat exchanger as claimed in claims 1 or 2, wherein the angular distance between the ridge profiles determines an area of the partitions of the first fluid flow path.

6. The co-axial tube heat exchanger as claimed in claim 1, wherein the first pipe includes a first port cavity and a second port cavity for an inlet pipe and an outlet pipe respectively, wherein the inlet pipe is coupled to the inlet port of the first pipe and the outlet pipe is coupled to the outlet port of the first pipe for receiving in and delivering out the first fluid from the partitioned first fluid flow path.

7. The co-axial tube heat exchanger as claimed in claim 6, wherein the first pipe is disposed between a condenser and a thermal expansion valve; and the second pipe is disposed between an evaporator and a compressor.

8. The co-axial tube heat exchanger as claimed in claims 6 or 7, wherein second pipe has concave passages at an entry and exit of the first fluid flow path.

9. The co-axial tube heat exchanger as claimed in claim 8, wherein a flow dispersal chamber and a flow collector chamber is formed at the entry and exit of the first fluid flow path.

10. The co-axial tube heat exchanger as claimed in claim 1, wherein ends of the first pipe and the second pipe are locked with each other using at least one of a clinching process, a deforming process, a pressing process or a combination thereof.