|Publication number||USRE30765 E|
|Application number||US 05/960,997|
|Publication date||Oct 13, 1981|
|Filing date||Nov 15, 1978|
|Priority date||Sep 7, 1976|
|Publication number||05960997, 960997, US RE30765 E, US RE30765E, US-E-RE30765, USRE30765 E, USRE30765E|
|Inventors||Rudy C. Bussjager|
|Original Assignee||Carrier Corporation|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (15), Classifications (9)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates to a reversible refrigeration system which is adapted to deliver optimum performance in either a heating or a cooling mode of operation.
More specifically, this invention relates to a heat pump having control means associated therewith for automatically routing refrigerant to each of the heat exchangers in response to the exchangers' function whereby each exchanger operates efficiently when called upon to serve either as a condenser or as an evaporator.
Most air side heat exchangers employed in refrigeration systems are of the plate fin construction wherein refrigerant is directed through a number of heat transfer zones via flow circuits running through the unit. When the exchanger is used as a condenser, the flow of refrigerant is routed through the circuits so that it passes in series through each zone. On the other hand, when the exchanger is used as an evaporator, the refrigerant is generally routed through each circuit simultaneously to establish a parallel flow through the circuits. As can be seen, the flow geometry associated with a well designed condenser is not compatible with that of a well designed evaporator.
In a heat pump environment, it has been the usual practice to compromise the heat exchanger design in order to permit the exchangers to provide the double duty function required. This, in turn, limited the performance of the entire system.
It is therefore an object of the present invention to improve heat pump systems.
It is a further object of the present invention to provide a heat pump system for automatically controlling the flow of refrigerant through the system whereby the system performs effectively in either a cooling or a heating mode of operation.
These and other objects of the present invention are attained by means of a heat pump system having refrigerant flow control means associated therewith to produce a series flow geometry through the heat transfer zones of either of the heat exchangers when the exchanger is serving as a condenser and a parallel flow geometry through the zones when the exchanger is serving as an evaporator.
For a better understanding of the present invention as well as other objects and further features thereof, reference is had to the following detailed description of the invention to be read in connection with the accompanying drawings, wherein:
FIG. 1 is the schematic representation of a reversible refrigeration system utilizing the heat exchanger of the present inventon;
FIG. 2 is a partial perspective view showing a multi-circuit heat exchanger utilizing the teachings of the present invention;
FIG. 3 is a partial front view of the heat exchanger shown in FIG. 2;
FIG. 4 is an end view of the heat exchanger shown in FIG. 3;
FIG. 5 is a schematic representation illustrating the flow circuits of the exchanger shown in FIGS. 2 through 4; and
FIG. 6 is an enlarged view in section illustrating a capillary tube feeding one of the flow circuits of the exchanger shown in FIGS. 2 through 4.
FIG. 1 represents the simplest form of the invention being utilized in a reversible vapor compression system, generally referenced 10. The system includes a compressor 11 of any suitable design .Iadd.such as a motor compressor unit as is well known in the art .Iaddend.and two refrigerant heat exchangers 12, 13 which are typically plate fin coils which are specifically fabricated to exchange energy between air moving over the plates and refrigerant moving through the exchanger flow circuits. For purposes of this description, heat exchanger 12 shall be referred to as the indoor coil while heat exchanger 13 shall be referred to as the outdoor coil. The two coils are operatively connected to the compressor by a four-way valve 15 .Iadd.also known as a reversing valve.Iaddend., which enables the discharge vapor from the compressor to be selectively directed into either one of the exchangers. When the system is in a cooling mode of operation, the discharge is carried via line 16 into a primary header 17 associated with the outdoor coil.Iadd., said header acting as an inlet line.Iaddend.. At this time, the suction end of the compressor is operatively connected to the primary header 33 .Iadd.which may also act as an inlet line .Iaddend.by means of line 36. By cycling the four-way valve, the flow of refrigerant through the system is reversed and, accordingly, the role of the heat exchangers is also reversed.
The operation of the system shall be initially explained with the system in a cooling mode of operation wherein the outdoor coil 13 is called upon to serve as a condenser. The refrigerant vapor collected in the primary or upper header 17 flows downwardly through the outdoor coil 13. The refrigerant is caused to move through two heat tranfer zones, an upper zone A and a lower zone B. The two zones are separated by return bend 14 which functions as an intermediate header for passing refrigerant from one zone to the other.
After passing through the two heat transfer zones, the refrigerant enters a lower secondary header 18 .Iadd.or outlet line .Iaddend.associated with the outdoor coil. The lower header 18 is placed in fluid flow communication with secondary header 31 .Iadd.or outlet line .Iaddend.associated with the indoor coil by means of liquid line .Iadd.or conduit .Iaddend.23. It should also be noted that the lower header 18 is also placed in fluid flow communication with the upper header 17 by line 20 which by-passes the heat exchanger circuit. A check valve 21 is positioned in the by-pass line. The valve is held closed when the outdoor coil is operating as a condenser by the pressure difference established over the exchanger as the refrigerant changes from a vapor to a liquid. As a result, the liquid refrigerant collected in the lower or secondary header is prevented from flowing back into the primary header via line 20 when the exchanger is serving as a condenser.
The liquid refrigerant collected in header 18 moves along liquid line 23 through another check valve 24. Check valve 24 is arranged to open when the system is in a cooling mode of operation whereby the liquid refrigerant is directed toward the indoor coil 12. A second check valve 25 also is positioned in the liquid line close to the secondary header 31 associated with the indoor coil. The check valve 25 is arranged to operate in opposition with check valve 24 whereby the refrigerant is precluded from flowing directly from the liquid line into header 31. The refrigerant is thus forced to move into a distributor 27 positioned forward of check valve 25 in relation to the direction of flow.
In the distributor, the flow is split into two separate flow paths by means of a pair of capillary tubes 28, 29. As seen in FIG. 1, the capillary tubes are passed into centrally located return bend 30 which serves as an intermediate header in regard to the indoor coil. In practice the capillaries pass through the return bend and empty deeply into the circuit tubing connected thereto. As a result, a portion of the refrigerant is expanded into upper heat transfer zone C and a portion expanded into lower heat transfer zone D. Because of the pressures involved, a portion of the refrigerant flows upwardly through the indoor coil 12 into the primary header 33 and a portion of the refrigerant flows downwardly into the secondary header 31. As can be seen, the flow geometry of the indoor coil, which is functioning as an evaporator in the cooling mode of operation, consists of two distinct flow passages through which the refrigerant is moved simultaneously, one passage carrying refrigerant through heat transfer zone C and the other through heat transfer zone D.
As in the case of the outdoor exchanger, the indoor exchanger also has a by-pass line 34 associated therewith which places the primary header 33 in fluid flow communication with the secondary header 31. A check valve 35 is located in the by-pass line and is arranged to open when the exchanger 12 is operating as an evaporator. With check valve 35 open, the two headers 31, 33 are exposed to the suction side of the compressor by means of line 36 thereby completing the cycle.
Changing the system mode of operation, which is accomplished by cycling the four-way valve, reverses the flow of refrigerant through the system. This in turn changes the function of the two exchangers. At this time, the position of the four check valves changes. By-pass line 20 is thus opened while line 34 is closed. Similarly check valve 25 opens while check valve 24 closes.
The discharge from the compressor passes via line 36 and header 33 through the indoor coil, which is now acting as a condenser, into the lower header 31. The refrigerant, as it moves through the indoor coil, passes in series through the two heat transfer zones C and D. From the header 31, the refrigerant moves down the liquid line toward the outdoor coil. The flow is however blocked by closed check valve 24 causing the refrigerant to move into distributor 37 where the flow is split into two paths by means of capillary tubes 38, 39.
The capillaries pass through the intermediate header or tube bend 14 into the circuits associated with heat transfer zones A and B. Here again, the flow is split in two directions through the exchanger with part of the flow directed into secondary header 18 and part into primary header 17. The two headers are connected to the suction end of the compressor via open by-pass line 20 and line 16 to close the heating loop.
As should be clear from the description above, the flow of refrigerant through the heat exchangers is automatically controlled so that the flow geometry through each exchanger is changed depending on whether the exchanger is being used as a condenser or an evaporator. More specifically, when the heat exchanger is called upon to serve as a condenser, refrigerant is caused to flow in series through the exchanger heat zones. By the same token, the refrigerant is caused to flow simultaneously, or in parallel, through the heat zones when the exchanger is serving as an evaporator. In this manner, the performance of the system can be optimized for either a heating or cooling mode of operation, a result heretofore unattainable because of limitations placed upon the system as a result of the compromise necessitated by heat exchanger design.
It should be clear from the description above that the system is not necessarily limited by use of headers in connection with the exchangers when the invention is carried out in connection with a simple exchanger. In this regard the header can be replaced with standard tubing capable of facilitating the movement of refrigerant into and out of the exchangers.
Similarly, the present invention can be carried out in conjunction with a complex coil in which a multitude of circuits are passed back and forth through the exchanger unit. A complex coil, such as those typically utilized in larger refrigeration systems as illustrated in FIGS. 2 through 4. For purposes of explanation, the coil shall be deemed to be an outdoor coil utilized in a reversible refrigeration system similar to that described in FIG. 1.
A coil of complex circuitry containing a plurality of refrigerant flow circuits is illustrated in FIGS. 2 through 4. The coil includes two vertically aligned rows of finned tubes, an inner row 40 and outer row 41 which extend back and forth through the heat exchanger. The rows are interconnected by return bends 42 to form a number of individual refrigerant flow circuits of predetermined geometry. Typically, the two terminal ends of each circuit are brought out of the coil assembly through one of the assembly tube sheets as for example tube sheet 45, so that both the entrance and discharge opening to each circuit is conveniently located along one side of the exchanger.
In the complex coil herein described, the coil contains seven flow circuits that are arranged to pass through three heat transfer zones. It should become obvious, however, from the discussion below, that the number of circuits and heat transfer zones may vary depending upon the capacity of the unit involved and other design considerations.
Positioned along the side of the coil adjacent to the tube sheet 45 is a header network adapted to operate in conjunction with two check valves to route the flow of refrigerant through the heat exchanger in a prescribed manner when the exchanger is acting in the system as a condenser and in a different manner when it is acting as an evaporator. The header includes a primary header 47, a dummy or intermediate header 48, a secondary header 49 and a liquid header 46. It should be noted that the primary and secondary headers are axially aligned with the interior chambers of each header being separated by means of a check valve 51. The lower end of primary header 47 is joined in fluid flow communication with a compressor line 50 that is operatively connected to the compressor by means of a four way valve (not shown).
When the coil is serving as a condenser, high temperature and pressure vapor is delivered into the primary header via line 50 thereby causing check valve 51 to close. The closing of the valve in effect isolates the chamber of header 47 from that of header 49. The now isolated primary header is thus caused to feed refrigerant into four flow circuits by means of feeder tubes 52 operatively associated therewith. The four circuits fed by header 47 are positioned in the lower section of the coil make up a first heat transfer zone, herein referenced zone E.
A simplified schematic illustration of the flow through the heat exchanger is shown in FIG. 5. It is believed that the use of the schematic in conjunction with the drawing of FIGS. 2 through 4 will help in better understanding the flow geometry through the exchanger. After passing through the four flow circuits making up heat transfer zone E, the refrigerant is passed into the dummy header 48 via discharge lines 53. Because of the pressure differential involved, the refrigerant moves upwardly through the dummy header and is discharged into the two uppermost circuits in the coil by means of feeder tubes 54. The two upper refrigerant flow circuits combine to establish a second, smaller heat transfer region F.
After passing through the coil assembly, the refrigerant from the two upper circuits is routed to the secondary header 49 via discharge line 56. The refrigerant is collected in header 49 and fed into the last flow circuit by means of a single feeder tube 58. The last circuit passes through the third and final heat transfer zone, zone G, and is discharged into the liquid header 46.
Preferably, the final heat transfer zone is located in the central portion of the coil to enhance the heat transfer characteristics of the coil. For the purpose of clarity, the final heat transfer zone is illustrated at the top of the heat exchanger assembly.
The refrigerant, which is now in a liquid phase is collected in the liquid header 46 and is passed through opened check valve 61 into a T-connector 62. At the connector, the refrigerant moves down liquid line 60 toward the indoor coil (not shown).
As can be seen from the description above, the header network, acting in concert with the check valves, operates to direct the refrigerant from the compressor through the heat transfer zones in a series flow progression. Furthermore, the number of flow circuits in each zone diminishes in the direction of flow. By zoning the coil in this manner, the flow geometry of the coil is regulated in response to the increase in density of the fluid to obtain optimum coil performance when operating as a condenser.
When the systems mode of operation is reversed, the coil's function is similarly reversed. In the heating mode, liquid refrigerant is moved along liquid line 60 toward check valve 61. The valve, however, is automatically moved to a closed position because of the change in pressure felt over the valve. The refrigerant is thus forced to move into distributor 63 that is connected to T-connector 62. At the distributor, the flow is separated into seven flow paths by means of capillary tubes 65. It should be noted that the number of capillary tubes are equal in number to the number of flow circuits passing through the coil.
As best illustrated in FIG. 6, six of the capillary tubes pass through the dummy header 48 and pass into feeder tubes 54 associated with the four circuits contained in heat transfer zone E and the discharge tubes 53 associated with the two circuits associated with heat transfer zone F. The capillary tubes extend deeply into the various flow circuit tubes to insure that the refrigerant passing through the capillaries is expanded well within each circuit. This in turn, precludes the refrigerant from being passed between circuits in the dummy header. Because the dummy header is at a substantially uniform pressure, the refrigerant is fed evenly into each circuit.
The seventh capillary tube is passed into the liquid header 46 which is at relatively the same pressure as the dummy header. Header 46, in turn, feeds into the circuit associated with heat transfer zone G.
It should be noted that at this time check valve 51, positioned between the primary and secondary headers 47 and 49 is now moved to an open position so that the headers are cojoined to establish a single flow passage leading to the compressor via line 50. As best illustrated in FIG. 5, the seven flow circuits are arranged to empty into the headers 47, 49 when the coil is serving as an evaporator. The circuits associated with zones G and F empty into header 49 via lines 56 and 58 while the four circuits associated with zone E empty into header 47 via lines 52.
Accordingly, when the heat exchanger is called upon to serve as an evaporator in the system, the flow geometry through the coil is automatically changed whereby refrigerant is caused to flow through all the circuits, and thus all the heat transfer zones, simultaneously in a parallel flow arrangement. By maintaining this parallel flow arrangement through the coil, optimum performance of the exchanger can be obtained when utilized as an evaporator.
While this invention has been described with reference to the structure herein disclosed, it is not confined to the specific details as set forth. For example, in place of the capillary tubes wherein employed any expansion device capable of carrying out the flow splitting and throttling process can be similarly employed provided such modifications come within the scope of the following claims.
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|U.S. Classification||62/115, 62/160, 62/324.1|
|International Classification||F25B13/00, F25B39/00|
|Cooperative Classification||F25B39/00, F25B13/00|
|European Classification||F25B13/00, F25B39/00|