US20110138829A1

US20110138829A1 - Heat Pump System

Info

Publication number: US20110138829A1
Application number: US13/058,178
Authority: US
Inventors: David Sooil Koh
Original assignee: SAVE ENERGY Inc
Current assignee: SAVE ENERGY Inc
Priority date: 2008-08-08
Filing date: 2009-08-08
Publication date: 2011-06-16
Also published as: WO2010017536A4; WO2010017536A3; WO2010017536A2

Abstract

In a conventional heat pump system which has a space heat exchanger, a motor (717) driven compressor (106), a refrigerant, a suction line (104) for feeding refrigerant to the compressor, and a waste heat exchanger (720) for adding or removing heat from the heat pump system, the improvement uses various devices to optimize a temperature of the refrigerant in the suction line (104), where the refrigerant enters the compressor. The preferred device is a Peltier thermocouple (500), which can be controlled by current, in response to a sensor (502) in the suction line, to heat or cool the suction line to minimize the load of incompressible liquid or high gas pressure on the compressor. An improved auxiliary heat exchanger also can improve efficiency.

Description

This application is a US National Stage Patent Application of pending international PCTUS0953236, filed on 2009 Aug. 8 (2009 Aug. 8) and takes benefit of that application's filing date of 2009 Aug. 8 and of its priority dates of two provisional applications listed below.
This application also takes benefit of provisional application 61/087,467 filed 2008 Aug. 8 (2008 Aug. 8), and its priority date of 2008 Aug. 8, which now expired provisional was pending when PCTUS0953236 was filed as a non-provisional thereof.
This application also takes benefit of provisional application 61/103,311 filed 2008 Oct. 7 (2008 Oct. 7), and its priority date of 2008 Oct. 7, now expired, which provisional was pending when PCTUS0953236 was filed as a non-provisional thereof.
In other words, this application takes benefit of International PCTUS0953236 and takes benefit of all that application's priorities, including:

- PCTUS0953236's filing date of 2009 Aug. 8, and
- PCTUS0953236's provisional priority dates of:
  - provisional application 61/087,467 and its priority date of 2008 Aug. 8; and
  - provisional application 61/103,311 and its priority date of 2008 Aug. 7.

We hereby incorporate by reference all those above applications and disclosures.

BACKGROUND OF INVENTION

1. The present invention relates to a heat pump for and cooling and or heating.
2. Heat pumps have been particularly useful for refrigeration and for air conditioning and heating.
U.S. Pat. No. 3,071,935 to Kapeker refers to an automatic refrigeration and defrost system which uses an additional heat exchanger within the system in the order to improve efficiency of the system.
A United States Patent Application by Han, published as 20060196225, refers to the use of heat exchangers in a refrigeration cycle.

BRIEF SUMMARY OF THE INVENTION

The present invention includes a heat exchanger having an improved flow within for greater heat transfer efficiency.
The present invention improves efficiency by placing a heat exchanger between an output line and a suction line of a heat pump system.
The present invention also may include an electronic suction pressure control which optimizes the suction line temperature, and thereby limits pressure on the suction line.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a block diagram a refrigeration system embodiment of the present invention.

FIG. 2 is a block diagram another embodiment the refrigeration system of the present invention.

FIG. 3 is a flow diagram in the nature of a simplified elevation in section of an improved heat exchanger of the present invention.

FIG. 4 is a flow diagram in the nature of a simplified elevation in section of an improved but less expensive embodiment of a heat exchanger.

FIG. 5 is a block diagram another embodiment the refrigeration system which optimizes suction line temperature.

FIG. 6 is a block diagram another embodiment the refrigeration system which optimizes suction line temperature.

FIG. 7 is an elevation in section of the Peltier thermocouple device shown twice in FIG. 6, which optimizes suction line temperature.

FIG. 8 is a block diagram of the present invention in heating mode.

FIG. 9 is a block diagram of the present invention in air-conditioning mode.

DETAILED DESCRIPTION OF THE DRAWINGS

Present Invention

FIG. 1 illustrates an embodiment of the invention, installed in s system for cooling a refrigeration case, such as in a retail food store. Inserted into a conventional suction line 100 coming from a refrigeration case 100, is a Heat Exchanger 102, of the present invention, which raises the temperature and the vapor ratio in the suction line. This relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid. The less liquid, the less compressor load, and the less power consumption by compressor 106.
Compressor 106 outputs through line 108 through three alternative heat absorbers: Hot water tank 110 supplies hot water to the building. In winter, Heat reclaimer 111 heats the building. Any heat not so absorbed is sent to outside condenser 112 for dissipation outdoors.
Receiver tank 114 receives the outflow of those heat absorbers 110-112. From receiver tank 114, mostly liquid refrigerant at 75 to 90 degrees F. is output at pipe 116 towards the refrigeration case [not shown] to cool the case. But, in the present invention, diverter valve 118 may be closed to send refrigerant through heat exchanger 102, to be further cooled, and to heat refrigerant that is output through output 104, to make the fluid more vapor and less liquid, to relieve strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
For convenience, valves 119 and 120 may be used with the diverter valve 118, for testing, bypass, and repair purposes. If an operator opens valve 118 to bypass the heat exchanger 102, the operator should close valves 119 & 120; and visa-versa. The system will be more efficient with valve 118 closed, and valves 119 & 120 open.
FIG. 2 shows a similar arrangement as FIG. 1, but where heat exchanger 102 is mounted in output line 116 towards the refrigeration case, rather than in suction line 100 & 104. But the flow, through valve 119, around closed bypass valve 138, through heat exchanger 102, and through valve 120, also results in a similar flow pattern to FIG. 1. Thus heat transfer between output line 116 and suction line 104 may be similar between FIGS. 1 & 2. This again relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
Valves 138, 119, 120, 140, and 142 allow heat exchanger 102 to be bypassed.
FIG. 3 shows an improved heat exchanger 102 of the present invention. Fluid such as R-22 refrigerant from, in FIG. 1, the refrigeration case, flows through inlet 200, FIGS. 1 & 3, through manifold 202 (FIG. 3), through a plurality of distribution holes, such as 205-206. The presently preferred embodiment has from sixteen to twenty such holes 205-206. Fluid flows from the holes through a corresponding number of sealed large-diameter tubes 207-208. As the fluid passes through tubes 207-8 some heat transfers between chamber 210 and the large diameter tubes such as 207-208. Hot compressor output fluid from line 116 enters through inlet 212 into hot liquid filled middle chamber 214, where heat is transferred to large diameter tubes 207-207 and small diameter tubes 220-222.
Fluid in tubes 207-208 passes through chamber 230, where more heat is transferred through the tube walls into the tubes 207-8, which then turn 180 degrees back, to flow towards middle chamber 214, through middle chamber 214, transferring more heat from middle chamber 214 to tubes 207-208. The fluid discharges from tubes 207-208 through outlets 247-248 into chamber 210. Fluid then flows through chamber 210, warming tubes 207-208, out through about forty smaller diameter tubes such as 220-222, wherein fluid in chamber 214 heats smaller diameter tubes 220-222 and thereby the fluid in those tubes 220-222, which is next discharged into chamber 230 to heat larger tubes 207-208 and then flow out through outlet 250.
This improved heat exchanger has about three times the heat transfer efficiency of a similar sized conventional heat exchanger: wherein in input chamber communicates with through a plurality of tubes, through a middle chamber, to an output chamber, having no designed-in backflow.
FIG. 4 is a less expensive but still effective mode of heat exchanger 102 from FIG. 1. Suction line 100-104 is partly replaced by exchanger section 122A of FIG. 4. In exchanger section 122A, refrigerant flows from compressor 106 through pipe 116 through valve 120 into chamber 300, where manifold 304 splits flow through several copper coils, preferably three coils, of about 30 turns each, shown here as coil 311, and the other two coils shown in part as 312-313. Where refrigerant flows through coiled tubes 311-313 and is cooled by fluid in chamber 300. Fluid in chamber 300 is thereby heated so that it leaves chamber 300 as mostly vapor, about 97% vapor, with the refrigerant flowing from line 104 to compressor 106. This again relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
Additional improvements were disclosed in the PCT application PCTUS0953236, after the priority provisional applications, U.S. 61/087,467, filed Aug. 8, 2008 and 61/103,311 filed Oct. 7, 2008.
In FIG. 5, this embodiment optimizes the temperature of the fluid in the suction line 104, for maximum efficiency, to maximize vapor without overheating it. For each refrigerant, there will be different such optimum temperatures, all between 40 and 88 degrees F. Using the R22 that the prototype uses, the literature indicates that optimum temperature is 40 to 60 degrees F. Thermostat 400 is set to, above 60 degrees F., close a circuit 401 and open solenoid valve 404, admitting cold 5 degree F. gas to mixing chamber 405, and cooling the fluid flowing into suction line 104 to the optimum 60 degrees F., plus about 5 degrees for hysteresis. Thermostat 400 is set to, below 40 degrees F., close a circuit 408 and open solenoid valve 409, admitting hot 131 degree F. gas from output line 108 to mixing chamber 405, and heating the fluid in suction line 104 to the optimum 40 degrees F. plus about 5 degrees for hysteresis.
Where the refrigerators supplied by the compressor 106 are spread over a large area, the fluid lines can be difficult to install, and can be vulnerable.
A presently preferred embodiment of suction temperature control is in FIG. 6.
FIG. 7 shows the Peltier heating/cooling device in detail.
Here a self-contained suction vapor heating/cooling block 500 with a thermoelectric Peltier module is wrapped around suction line 104, and a temperature sensor 502, within, is inserted into a hole 503 drilled in suction line 104, to sense the temperature of the refrigerant fluid, such as R-22. Sensor 502 is then soldered 504 into place to seal the hole to keep the R-22 refrigerant within tube 104. Conductors 506-507 conduct the temperature signal to power supply 508 FIG. 6, which polarizes and adjusts the current of direct current from power supply 508 across conductors 511-512 to the thermocouple 516 to heat or cool the suction tube 104, as needed to achieve an optimum 40 to 60 degrees F. As of Feb. 8, 2011, additional experimentation has given us a best mode where the optimum is 65 degrees F. with R-22 refrigerant.
Heat from or to cooler 516 is conducted across thermal epoxy 518 to heat pipe 520, which is a copper conduit with acetone sealed inside. The acetone evaporates in response to heat and almost instantly transmits the heat efficiently up through the heat pipe 520, to be transmitted via thermal epoxy 522 to heat sink 524. Coiling fan 526 is driven by motor 527 to move air across fins 530 of heat sink 524, so that the Peltier cooler 516 gives or takes heat to or from the air.
To install the heating/cooling block on suction line 104:

- drill hole 503 in line 104;
- solder sensor 502 to secure and seal it into the hole 503;
- Connect sensor 502 via wires 506-507 to power supply 508.
- Coat a surface of tube 104 with thermal epoxy 518.
- Bend legs 531-532 of cooler 516 and refrigeration or heat pipe 520 around tube 104 to make a snug thermoconductive fit with the epoxy.
- Connect cooler 516 by wires 511-512 to power supply 508.
- Coat a surface of heat pipe 520 with thermal conductive epoxy 522.
- Slide heat sink 524 onto heat pipe 520, and keep snug until the thermoconductive epoxy 522, there-between, sets and joins sink 524 to pipe 520.
- Connect the fan wires 541-542 from fan 527 to power supply 508, FIG. 6.

In FIG. 6, a similar or identical self-contained liquid cooling block 502A with a thermoelectric Peltier module is wrapped around expansion valve feed line 545, and a temperature sensor similarly placed within line 545, senses said fluid's temperature. Power supply 508 polarizes and adjusts the current of direct current from power supply 508 across the Peltier device 502A to heat or cool the line 522 as needed to achieve an optimum 60 degrees F., into expansion valve TVX 550.

Space Heating Mode

FIG. 8 shows how improved auxiliary heat exchanger 102 results in a dramatic efficiency improvement, in which the building heating system heat pump works at lower ambient temperatures, e.g.: 20° F., than the 35° F. of a conventional heat pump, in the heating mode.
FIG. 8 shows the present heat pump system, generally designated 690 in its heating mode. The heat pump system 690 comprises an indoor unit 704, and an outdoor unit 706. Indoor unit 704 includes heat exchanger 708, and fan 711 which blows indoor air across heat exchanger 708, to heat or cool an indoor space. In this drawing it is heating.
Within the outdoor unit 706, motor 717 driven compressor 106 compresses a refrigerant, such as R-22, to drive the refrigerant towards 4-way-valve 719, which switches the system between heating (shown here) and cooling modes. An out door heat exchanger 720 adds (in this heating mode) or removes heat from the system. Auxiliary heat exchanger 102 is an improved unit as in FIG. 3.
Compressor 106 pumps out refrigerant as a high pressure hot gas, at perhaps 140° Fahrenheit through compressor output tube 730 through 4-way valve 19, which is switched in its heating mode to send the refrigerant through tube 732 towards indoor heat exchanger 708. This 140° gas enters indoor heat exchanger 708, where it transfers its heat to the indoor air, which fan 11 blows across heat exchanger 708. Refrigerant exits heat exchanger 708 through tube 734 as high-pressure mid-temperature (perhaps 75 degrees) gas and liquid. These pass through capillary tube 736, which drops their pressure and temperature to about 45 degrees F.
Throughout this specification, temperatures and pressures are approximate, and may vary with time. These temperatures assume an increased efficiency that occurs in this system after the compressor has been running for an interval.
Refrigerant is about 45° F. as it enters the improved auxiliary heat exchanger 102, at inlet 200 as in FIG. 3.
The improved heat exchanger 102 tends to more efficiently equalize the temperature, so that the gas exits output 216 at perhaps 35° F., and the liquid exits through outlet 250 at about 30° F., from whence it flows through tube 779, towards outside heat exchanger 720.
At the inlet of outside heat exchanger 720 is a orifice 774. Orifice 774 is a restriction in pipe 779's diameter, which restriction decompresses the liquid refrigerant and drops its pressure and temperature towards R-22's −41° F. vaporization temperature, as it flows through heat exchanger 720.
The combination of:

- improved heat exchanger 102, and
- orifice 774
  make a colder refrigerant within outside air heat exchanger 720. Thus, this colder R-22 can extract more heat from outside air at lower temperatures than the conventional outside air heat exchanger. The present invention in FIG. 8 will extract heat from outside ambient air down to 20° F., making heat pumps economically usable in higher latitudes than before.

Assuming a 20° F. ambient outdoor air, heated R-22 exits heat exchanger 720 at outlet line 778, at about 15° F. The R-22 flows through 4-way valve 719, which in the heating mode directs it to gas input 212 of auxiliary heat exchanger 102, shown also in FIG. 3, where in middle chamber 214 it flows around tubes 207-208 and 220-222, to cool the liquid in those tubes and absorb heat so that it exits outlet 62 at about 35° F.
Gas outlet 216 is the suction line of FIG. 8, leading warm mostly gas to input 104 of compressor 106. If this gas is too hot, it tends to burden the compressor 106. On warmer days, this system might prove too efficient and warm the suction line to a temperature that over-pressures the suction line 104, and thus overburdens the compressor.
Because improved auxiliary heat exchanger 102 is so much more efficient, this gas can exceed optimum temperatures. We have therefore inserted a novel suction pressure control switch 794 to sense if the pressure of this gas is at or above 22 kg. per square centimeter. If so, the suction pressure control switch 94 switches off a relay which controls fan 776, to limit heat absorption at heat exchanger 720, and thus reduce the downstream temperature and pressure of the gas at inlet 104 of compressor 106.
This limits the temperature of gas exiting compressor 106 at outlet 730 to 140° F.
Alternatively, and preferably, we can use the mixing valve arrangement 400 to 408 described in FIG. 5, to optimize the suction temperature at suction tube 104.
As the presently preferred embodiment, we can use the peltier device 500 of FIG. 6 to optimize the suction temperature at suction tube 104.
The result of this increased efficiency is:

1. Lower energy consumption, by as much as 40%;
2. The ability to use the heat pump to heat indoor air when outside ambient air temperatures are as low as 20° F.; which is 15° F. lower than with conventional heat pumps; and
3. The resulting ability to economically use heat pumps for heating at higher latitudes than previously economic.

Air-Conditioning Mode
When 4 way valve 719 is switched to the air-conditioning mode, as in FIG. 9, similar efficiencies are also available.
In the air-conditioning mode, the reversed flow will happen with the auxiliary heat exchange 102 structure of FIG. 3. 200 becomes the outlet, and 250 becomes the inlet.

Claims

1. In a conventional heat pump system, said heat pump system including a space heat exchanger 708, for heating or cooling a space, a motor 717 driven compressor 106, a refrigerant, a suction line 104 for feeding refrigerant to the compressor, and a waste heat exchanger 720 for adding or removing heat from the heat pump system, an improvement comprising:

means for optimizing a temperature of the refrigerant in the suction line, where said refrigerant enters the compressor.

2. A heat pump system, according to claim 1, in which the means for optimizing a temperature of the refrigerant in the suction line comprises:

a Peltier thermocouple 516, malleable, as means for being cooperatively shaped to make close thermoconductive contact with said suction line 104;

a temperature sensor 502, sealable within suction line 104, for sensing said refrigerant's temperature;

a controller 508 for polarizing and adjusting a current across the Peltier thermocouple 516 to heat or cool the suction tube 104 as needed to achieve an optimum refrigerant temperature at the compressor 106 for minimizing compressor load.

3. A heat pump system, according to claim 2, in which a heat pipe 520 thermally couples to the Peltier thermocouple 516 to a heat sink 524.

4. A heat pump system, according to claim 3, in which a fan 527 moves air across heat sink 524 to add or remove heat.

5. A heat pump system, according to claim 1, further comprising means for optimizing a temperature of the refrigerant at the expansion valve feed line 522, said expansion valve optimizing means including:

a Peltier thermocouple 516, malleable, as means for being cooperatively shaped to make close thermoconductive contact with said expansion valve feed line 522;

a temperature sensor 502, sealable within expansion valve feed line 522, for sensing said refrigerant's temperature;

a controller 508 for polarizing and adjusting a current across the Peltier thermocouple 516 to heat or cool the expansion valve feed line 522 as needed to achieve an optimum refrigerant temperature at the compressor 106 for minimizing compressor load.

6. A heat pump system, according to claim 5, in which:

a heat pipe 520 thermally couples to the Peltier thermocouple 516 to a heat sink 524.

7. A heat pump system, according to claim 6, in which a fan 527 moves air across heat sink 524 to add or remove heat.

8. A heat pump system, according to claim 1, in which the means for optimizing a temperature of the refrigerant in the suction line comprises:

thermostat 400 having a temperature sensor in suction line 104, at the compressor's input;

mixing chamber 405 in suction line 104, upstream of the compressor's input;

said thermostat 400, having a high temperature limit switch for closing a circuit 401 to open solenoid valve 404, admitting cold gas to mixing chamber 405, and thereby cooling the fluid flowing into suction line 104 to an optimum temperature for the refrigerant to minimize compressor load; and

said thermostat 400, having a low temperature limit switch for closing a circuit 408 to open solenoid valve 409, admitting hot gas from output line 108 to mixing chamber 405, and thereby heating the fluid in suction line 104 to the optimum temperature for refrigerant to minimize compressor load.

9. A heat pump system, according to claim 1, further comprising heat exchanger 102, for transferring heat:

from a first temperature refrigerant,

from a second temperature refrigerant,

said heat exchanger 102 in which:

the first temperature refrigerant, flows:

through an inlet 200,

through a sealed large-diameter tube 207 which tube 207 runs through chamber 210, and as the first temperature refrigerant passes through the tube 207 some heat transfers between chamber 210 and the tube 207,

through the sealed large-diameter tube 207 which tube runs through chamber middle chamber 214, and as the first temperature refrigerant passes through 207 some heat transfers between chamber 214 and the large diameter tubes 207,

through the sealed large-diameter tube 207 which tube runs through chamber output chamber 230, and as the first temperature refrigerant passes through 207 some heat transfers between output chamber 214 and the large diameter tube 207,

said large diameter tube 207 bends 180 degrees and returns to carry the first temperature refrigerant back through middle chamber 214, and as the first temperature refrigerant passes through 207 some heat transfers between chamber 214 and the large diameter tube 207,

said large-diameter tube 207 extends into chamber 210, and opens to dump first temperature refrigerant into chamber 210,

said first temperature refrigerant then flows through a second tube 220 from chamber 210, through middle chamber 214, into output chamber 230;

a second temperature refrigerant enters and passes through middle chamber 214 and exchanges heat with the large diameter tube and the second tube 220 as they pass through middle chamber 214;

the first temperature refrigerant leaves via an output chamber output 256, and the second temperature refrigerant leaves via a middle chamber output 216, both the first temperature refrigerant, and the second temperature refrigerant having exchanged heat to render their temperatures less different than upon their entry into the heat exchanger.

10. A heat pump system, according to claim 9, in which there is a plurality 207-208 of the large diameter tube 207; and there is a plurality 220-222 of the second tube 220.

11. A heat pump system, according to claim 10, in which the plurality 207-208 of the large diameter tube 207 includes at least sixteen tubes; and the second tube 220, is of a smaller diameter, and the plurality is about twice the number of the large diameter tube.

12. In a conventional heat pump system, said heat pump system including a space heat exchanger 708, for heating or cooling a space, a motor 717 driven compressor 106, a refrigerant, a suction line 104 for feeding refrigerant to the compressor, and a waste heat exchanger 720 for adding or removing heat from the heat pump system, an improvement comprising:

heat exchanger 102, for transferring heat:

from a first temperature refrigerant,

from a second temperature refrigerant,

said heat exchanger 102 in which:

the first temperature refrigerant, flows:

through an inlet 200,

13. A heat pump system, according to claim 12, in which there is a plurality 207-208 of the large diameter tube 207; and there is a plurality 220-222 of the second tube 220.

14. A heat pump system, according to claim 13, in which there the plurality 207-208 of the large diameter tube 207 includes at least 16 tubes; and the second tube 220, is of a smaller diameter, and the plurality is about twice the number of the large diameter tube.

15. In a conventional heat pump system, said heat pump system including a space heat exchanger 708, for heating or cooling a space, a motor 717 driven compressor 106, a refrigerant, a suction line 104 for feeding refrigerant to the compressor, and a waste heat exchanger 720 for adding or removing heat from the heat pump system, an improvement comprising:

means for optimizing a temperature of the refrigerant in the suction line, where said refrigerant enters the compressor;

in which the means for optimizing a temperature of the refrigerant in the suction line comprises:

a controller 508 for polarizing and adjusting a current across the Peltier thermocouple 516 to heat or cool the suction tube 104 as needed to achieve an optimum refrigerant temperature at the compressor 106 for minimizing compressor load;

a heat pipe 520 thermally couples to the Peltier thermocouple 516 to a heat sink 524;

a fan 527 moves air across heat sink 524 to add or remove heat;

means for optimizing a temperature of the refrigerant at the expansion valve feed line 522, said expansion valve optimizing means including:

a second Peltier thermocouple 516, malleable, as means for being cooperatively shaped to make close thermoconductive contact with said expansion valve feed line 522;

a controller 508 for polarizing and adjusting a current across the second Peltier thermocouple 516 to heat or cool the expansion valve feed line 522 as needed to achieve an optimum refrigerant temperature at the compressor 106 for minimizing compressor load;

a heat pipe 520 thermally couples to the second Peltier thermocouple 516 to a second heat sink 524.

a second fan 527 moves air across heat sink 524 to add or remove heat;

a heat exchanger 102, for transferring heat:

from a first temperature refrigerant,

from a second temperature refrigerant,

said heat exchanger 102 in which:

the first temperature refrigerant, flows:

through an inlet 200,

through a manifold 202,

through a between sixteen and twenty distribution holes 205-206,

from the holes through a corresponding number of sealed large-diameter tubes 207-208, which tubes run through chamber 210,

as the fluid passes through tubes 207-8 some heat transfers between chamber 210 and the large diameter tubes;

through the sealed large-diameter tube 207 which tube runs through middle chamber 214, and as the first temperature refrigerant passes through 207 some heat transfers between chamber 214 and the large diameter tubes 207,

through the sealed large-diameter tubes 207-8 which tubes runs through chamber output chamber 230, and as the first temperature refrigerant passes through 207 some heat transfers between output chamber 214 and the large diameter tube 207,

said large diameter tube 207 bends 180 degrees and returns to carry the first temperature refrigerant back through middle chamber 214, and as the first temperature refrigerant passes through the large diameter tubes, some heat transfers between chamber 214 and the large diameter tubes;

said large-diameter tubes extend into chamber 210, and open to dump first temperature refrigerant into chamber 210;

said first temperature refrigerant then flows through about forty smaller diameter tubes 220-222 from chamber 210, through middle chamber 214, transferring more heat with middle chamber 214;

said first temperature refrigerant then flows into output chamber 230;

a second temperature refrigerant enters and passes through middle chamber 214 and exchanges heat with the large diameter tubes and the forty smaller diameter tubes 220-222 as they pass through middle chamber 214;

the first temperature refrigerant leaves via an output chamber output 256, and the second temperature refrigerant leaves via a middle chamber output 216, both the first temperature refrigerant, and the second temperature refrigerant having exchanged heat to render their temperatures less different than upon their entry into the heat exchanger;

this improved heat exchanger has about three times the heat transfer efficiency of a similar sized conventional heat exchanger.

16. A heat pump system according to claim 1 in which the suction line 104 is partly replaced by exchanger section 122A which exchanger section 122A comprises:

manifold 304, which splits flow through several copper coils 311-313, of multiple turns each, 311

where refrigerant flows through coiled tubes and is cooled by fluid in chamber 300, to thereby heat fluid in chamber 300 so that it leaves chamber 300 as mostly vapor, about 97% vapor, to go to compressor 106, said mostly vapor state functioning to relieve strain on compressor 106, which strain would occur from trying to compress incompressible liquid.