Source: http://www.google.com/patents/US6948321?dq=7,053,767
Timestamp: 2017-04-29 21:38:01
Document Index: 114999924

Matched Legal Cases: ['Application No. 60', 'Application No. 09', 'Application No. 09', 'Application No. 09', 'Application No. 09', 'Application No. 10', 'Application No. 10', 'Application No. 10', 'Application No. 10']

Patent US6948321 - Efficiency thermoelectrics utilizing convective heat flow - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inPatentsAn improved efficiency thermoelectric system is disclosed wherein convection is actively facilitated through a thermoelectric array. Thermoelectrics are commonly used for cooling and heating applications. Thermal power is convected through a thermoelectric array toward at least one side of the thermoelectric...http://www.google.com/patents/US6948321?utm_source=gb-gplus-sharePatent US6948321 - Efficiency thermoelectrics utilizing convective heat flowAdvanced Patent SearchTry the new Google Patents, with machine-classified Google Scholar results, and Japanese and South Korean patents.Publication numberUS6948321 B2Publication typeGrantApplication numberUS 10/632,235Publication dateSep 27, 2005Filing dateJul 31, 2003Priority dateFeb 9, 2001Fee statusPaidAlso published asUS6672076, US7421845, US7926293, US8375728, US20020148234, US20040020217, US20050210883, US20090007572, US20110162389, WO2002065029A1, WO2002065029A8Publication number10632235, 632235, US 6948321 B2, US 6948321B2, US-B2-6948321, US6948321 B2, US6948321B2InventorsLon E. BellOriginal AssigneeBsst LlcExport CitationBiBTeX, EndNote, RefManPatent Citations (43), Non-Patent Citations (19), Referenced by (51), Classifications (23), Legal Events (5) External Links: USPTO, USPTO Assignment, EspacenetEfficiency thermoelectrics utilizing convective heat flow
US 6948321 B2Abstract
at least one thermoelectric element with at least one first side and at least one second side exhibiting a temperature gradient between them during operation, wherein the at least one thermoelectric element is configured to permit flow of at least one convective medium through the at least one element to provide generally steady-state convective heat transport toward at least one side of the thermoelectric element. 2. The thermoelectric system of claim 1, wherein the at least one convective medium flows through the at least one thermoelectric element.
3. The thermoelectric system of claim 2, wherein the at least one thermoelectric element is permeable.
4. The thermoelectric system of claim 3, wherein the at least one thermoelectric element is porous.
5. The thermoelectric system of claim 2, wherein the at least one thermoelectric element is tubular.
6. The thermoelectric system of claim 2, wherein the at least one convective medium flows through the at least one thermoelectric element in a single general direction.
7. The thermoelectric system of claim 6, wherein the at least one convective medium flows generally from between the first and the second sides toward the first side or toward the second side.
8. The thermoelectric system of claim 2, wherein the at least one convective medium flows generally from the first side to the second side.
9. The thermoelectric system of claim 2, wherein the at least one convective medium flows generally from the second side to the first side.
10. The thermoelectric system of claim 2, wherein the at least one convective medium flows through the at least one thermoelectric element in at least two general directions.
11. The thermoelectric system of claim 10, wherein the at least one convective medium flows generally from between the first side and the second side toward the first side and toward the second side.
12. The thermoelectric system of claim 1, wherein the at least one convective medium flows along the at least one thermoelectric element.
13. The thermoelectric system of claim 12, wherein the at least one convective medium flows along the at least one thermoelectric element in a single general direction.
14. The thermoelectric system of claim 13, wherein the at least one convective medium flows generally from between the first side and the second side toward the first side or toward the second side.
15. The thermoelectric system of claim 12, wherein the at least one convective medium flows generally from the first side to the second side.
16. The thermoelectric system of claim 12, wherein the at least one convective medium flows generally from the second side to the first side.
17. The thermoelectric system of claim 12, wherein the at least one convective medium flows along the at least one thermoelectric element in at least two general directions.
18. The thermoelectric system of claim 17, wherein the at least one convective medium flows generally from between the first side and the second side toward the first side and toward the second side.
19. The thermoelectric system of claim 12, further comprising at least one additional thermoelectric element.
20. The thermoelectric system of claim 19, wherein the at least two thermoelectric elements form concentric tubes with the convective medium flow between the concentric tubes.
21. The thermoelectric system of claim 20, wherein the tubes concentrically alternate between p-type thermoelectric material and n-type thermoelectric material.
22. The thermoelectric system of claim 20, wherein a first set of concentric tubes are of the same first type of thermoelectric material, and a second set of concentric tubes are of the same second type of thermoelectric material.
23. The thermoelectric system of claim 1, wherein at least part of the convective medium is a thermoelectric material, said convective medium thermoelectric material also forming at least a portion of the thermoelectric element.
24. The thermoelectric system of claim 1, wherein at least part of the convective medium is a thermoelectric material, said convective medium thermoelectric material forming a first portion of at least a portion of the thermoelectric element, and a solid thermoelectric material forming a second portion of the thermoelectric element.
25. The thermoelectric system of claim 24, wherein the solid thermoelectric material is tubular, and the convective medium thermoelectric material flows through the solid tubular thermoelectric material, the combination forming the thermoelectric element.
26. The thermoelectric system of claim 1, wherein at least part of the convective medium is a fluid.
27. The thermoelectric system of claim 26, wherein at least a portion of the convective medium is air.
28. The thermoelectric system of claim 1, wherein at least part of the convective medium is a solid.
29. The thermoelectric system of claim 1, wherein at least part of the convective medium is a mixture of fluid and solid.
30. The thermoelectric system of claim 1, wherein at least a portion of the thermoelectric element comprises at least one heat transfer feature that improves heat transfer between at least some of the at least one convective medium and the at least one thermoelectric element.
31. The thermoelectric system of claim 30, wherein the at least one thermoelectric element is tubular, and wherein the heat transfer feature is inside the tubular thermoelectric element.
32. The thermoelectric system of claim 30 wherein the heat transfer feature is a convective medium flow disturbing feature.
33. The thermoelectric system of claim 1, wherein the system is used for cooling.
34. The thermoelectric system of claim 1, wherein the system is used for heating.
35. The thermoelectric system of claim 1, wherein the system is used for both cooling and heating.
36. A method of improving efficiency in a thermoelectric system having at least one thermoelectric element having at least one first side and at least one second side exhibiting a temperature gradient between them during operation, the method comprising the step of actively convecting heat through the at least one thermoelectric element in a generally steady-state manner.
37. The method of claim 36, wherein the step of convecting heat comprises flowing at least one convective medium through the at least one thermoelectric element.
38. The method of claim 37, wherein the at least one thermoelectric element is permeable.
39. The method of claim 38, wherein the at least one thermoelectric element is porous.
40. The method of claim 37, wherein the at least one thermoelectric element is tubular.
41. The method of claim 37, wherein the step of flowing comprises flowing the at least one convective medium generally from the first side to the second side.
42. The method of claim 37, wherein the step of flowing comprises flowing the at least one convective medium generally from between the first side and the second side toward the first side or toward the second side.
43. The method of claim 37, wherein the step of flowing comprises flowing the at least one convective medium in at least two general directions.
44. The method of claim 43, wherein the step of flowing comprises flowing the at least one convective medium generally from between the first side and the second side toward the first side and toward the second side.
45. The method of claim 44, wherein the step of flowing comprises flowing at least some of the convective medium through the at least one thermoelectric element.
46. The method of claim 44, wherein the step of flowing comprises flowing at least some of the convective medium along the at least one thermoelectric element.
47. The method of claim 37, wherein the step of flowing further comprises flowing at least some of the convective medium between a concentric tube formed by the at least one thermoelectric element with at least one other thermoelectric element having a similar shape.
48. The method of claim 37, wherein at least a portion of the convective medium is a fluid.
49. The method of claim 48, wherein at least a portion of the convective medium is air.
50. The method of claim 37, wherein at least a portion of the convective medium is a solid.
51. The method of claim 37, wherein at least a portion of the convective medium is a mixture of fluid and solid.
52. The method of claim 36, wherein the thermoelectric system is used for cooling.
53. The method of claim 36, wherein the thermoelectric system is used for heating.
54. The method of claim 36, wherein the thermoelectric system is used for both cooling and heating.
55. A thermoelectric system comprising:
at least one thermoelectric element having at least one first side and at least one second side exhibiting a temperature gradient between them during operation, wherein at least a portion of the thermoelectric element is configured to permit flow of at least one convective medium through the at least a portion of the element to provide generally steady-state convection toward at least one side of the thermoelectric element; and at least one control system, said control system comprising: at least one controller, at least one input coupled to at least one controller, and at least one output coupled to at least one controller and to said thermoelectric element, said output controllable by said controller to modify at least one characteristic of said thermoelectric element. 56. The thermoelectric system of claim 55, wherein the at least one characteristic impacts the convective heat transport, and wherein the adjustment improves efficiency by adjusting the characteristic.
57. The thermoelectric system of claim 55, wherein the control system varies movement of at least some of the convective medium in response to said input.
58. The thermoelectric system of claim 55, wherein the control system varies at least the current through the at least one thermoelectric element.
59. The thermoelectric system of claim 55, wherein the at least one input comprises at least one external sensor.
60. The thermoelectric system of claim 55, wherein the at least one input comprises at least one sensor internal to the at least one thermoelectric element.
61. The thermoelectric system of claim 55, wherein the at least one input comprises at least one sensor internal to the thermoelectric element, at least one external sensor and at least one user selectable input.
62. The thermoelectric system of claim 55, wherein the at least one input is a user selectable input.
63. The thermoelectric system of claim 55, wherein at least one controller operates in accordance with at least one algorithm responsive to the at least one input to control the at least one output.
This Application is a continuation of application Ser. No. 09/860,725, filed May 18, 2001, now U.S. Pat. No. 6,672,076, and is related to and claims the benefit of the filing date of prior filed U.S. Provisional Patent Application No. 60/267,657, filed Feb. 9, 2001.
q c =αIT c−½I 2 R−KΔT (1) q in =αIΔT+I 2 R (2) q h =αIT h+½I 2 R−KΔT (3) where qc is the cooling rate (heat content removal rate from the cold side), qin is the power input to the system, and qh is the heat output of the system, wherein:
α=Seebeck Coefficient I=Current Flow Tc=Cold side absolute temperature Th=Hot side absolute temperature R=Electrical resistance K=Thermal conductance Herein α, R and K are assumed constant, or suitably averaged values over the appropriate temperature ranges.
q c +q in =q h (4) Further, to analyze performance in the terms used within the refrigeration and heating industries, the following definitions are needed: β = q c q i n = Cooling Coefficient of Performance ( COP ) ( 5 ) γ = q h q i n = Heating COP ( 6 ) From (4); q c q i n + q i n q i n = q h q i n ( 7 ) β+1=γ (8)
If β maximum is designated by βm, and the COP for qc maximum by βc, the results are as follows: β m = T c Δ T c ( 1 + ZT m - T h T c 1 + ZT m + 1 ) ( 9 ) β c = ( 1 2 ZT c 2 - Δ T ZT c T h ) ( 10 ) where; Z = α 2 RK = α 2 ρ λ = Figure of Merit ( 11 ) T m = T c + T h 2 ( 12 ) R=ρ×length/area (13)
K=λ×area/length (14) λ=Material Thermal Conductivity (15); and ρ=Material Electrical Resistivity (16) βm and βc depend only on Z, Tc and Th. Thus, Z is named the figure of merit and is basic parameter that characterizes the performance of TE systems. The magnitude of Z governs thermoelectric performance in the geometry of FIG. 1, and in most all other geometries and usages of thermoelectrics today.
The limitation becomes apparent when the maximum thermoelectric efficiency from Equation 9 is compared with Cm, the Carnot cycle efficiency (the theoretical maximum system efficiency for any cooling system); β m C m = T c Δ T ( 1 + ZT m - T h T c 1 + ZT m + 1 ) T c Δ T = ( 1 + ZT m - T h T c 1 + ZT m + 1 ) Note , as a check if Z → ∞ , β → C m . ( 17 ) Several commercial materials have a ZTA approaching 1 over some narrow temperature range, but ZTA is limited to unity in present commercial materials. Typical values of Z as a function of temperature are illustrated in FIG. 4. Some experimental materials exhibit ZTA=2 to 4, but these are not in production. Generally, as better materials may become commercially available, they do not obviate the benefits of the present inventions.
FIG. 17 depicts an existing device used to both heat and cool that can be improved in its efficiency by convective heat transfer in accordance with the present invention; and
FIG. 18 depicts an embodiment with convective heat transfer of an improvement of the device of FIG. 17 in accordance with the present invention.
FIG. 19 illustrates a control system for use with thermoelectric systems of the present invention.
The invention is introduced using examples and particular embodiments for descriptive purposes. A variety of examples are presented to illustrate how various configurations can be employed to achieve the desired improvements. In accordance with the present invention, the particular embodiments are only illustrative and not intended in any way to restrict the inventions presented. In addition, it should be understood that the terms cooling side, heating side, cold side, hot side, cooler side and hotter side and the like do not indicate any particular temperature, but are relative terms. For example, the “hot,” “heating” or “hotter” side of a thermoelectric element or array may be at ambient temperature, with the “cold,” “cooling” or “cooler” side at a cooler temperature than ambient. Conversely, the “cold,” “cooling” or “cooler” side may be at ambient with the “hot,” “heating” or “hotter” side at a higher temperature than ambient. Thus, the terms are relative to each other to indicate that one side of the thermolectric is at a higher or lower temperature than the counter-designated side. Similarly, the terms “cooling side” and “heating side” are not intended to designate the particular use for a thermoelectric system in any given application.
The present invention is based on the concept that the conductive/loss heat transport terms in Equations 1 and 3 which contain K and R, can be modified by the use of steady state convection through the array so as to diminish their overall effect on system performance. How this can be accomplished can be understood by first looking at the equations that govern heat generation and flow in a conventional TE. For simplicity, assume that material properties do not change with current and temperature, heat and current flow are one-dimensional, and that conditions do not vary with time. For this case: - K ⅆ 2 T ⅆ x 2 = I 2 R L ( 18 ) where;
FR/L=the resistive heat generation per unit length (19) For TE systems with typical boundary conditions, Equation 18 has Equations 1 and 3 as solutions. From Equation 3, the heating source term (αITh) contributes to heat output at the hot side as does ½FR, that is, one-half of the TE element resistive heating. Note that the other one half goes out the cold side, as seen in Equation 1 (where it has the minus sign since it subtracts from cooling). Further the heat output at the hot side is reduced by the conductive loss, KΔT. Thus, Equation 3 shows that qh is reduced by KΔT and ½ of the I2R heating within the TE elements.
Consider a comparison between conventional thermoelectric heating, and systems that employ steady state convective heat transport. If convection is added and the other assumptions are retained, Equation 18 becomes: - K ⅆ 2 T ⅆ x 2 = - CpM ⅆ T ⅆ x + I 2 R L ( 20 ) where;
CpM=Thermal mass of fluid transported per unit time (21) The extra term leads to a new parameter δ, which is the ratio of convective to conductive heat transport. If it is assumed that the convective transport goes toward the hot end in the heating mode and the cold end in cooling, and appropriate boundary conditions are used, the solutions to Equation 20 for cooling and heating become; q C = α I T c - ξ ( δ ) 2 I 2 R - K ( δ ) Δ T ( 21 ) q h = α I T h + ξ ( δ ) 2 I 2 R - K ( δ ) Δ T ( 22 ) where; δ = CpM K ( 23 ) ξ ( δ ) = ( 2 δ ) ( δ + e - δ - 1 ) ( 1 - e - δ ) ( 24 ) K ( δ ) = K ( δ e - δ 1 - e - δ ) ( 25 ) Notice that K(δ) is a function of δ and approaches the conductive value K for δ®0. Also, for δ>0 a larger portion of the I2R heating is transported to the hot (in heating) or cold (in cooling) end. The term ξ(δ)/2®½ when δ®0 as expected. Approximate values for ξ(δ) and K(δ)/K are given in Table 1. Note from Equation 2, that qin is not a direct function of δ. Also, a condition is imposed on δ by the energy balance requirement that CpMΔT (the power required to heat or cool the fluid) cannot exceed qh (the heat generated by the TE) or qc (the heat absorbed by the TE). Typically, this restricts δ to less than 5. Actual improvement in COP for allowable values for δ ranges up to about 100%. Similarly, qc improves by up to about 50%.
The situation is more complex in cooling. To best understand cooling operation, consider the case where the waste side is a heat sink at ambient temperature. The convective medium enters at the waste side and exits out the cold side. Thus the TE elements extract heat content from the medium thereby cooling it as it moves toward the cold side. The parameter K(δ)<K for δ>0 as in heating, so the conduction term diminishes with increased δ as in heating. However this advantage is partially offset by an increase in the fraction of heating transported to the cold end by I2R heating. Nevertheless, the change in K(δ) can be greater than ξ(δ) for increasing δ, so that under most conditions qc increases with increased convection. The effect can be enhanced further by a decrease of the current I to a minimum optimum value from a higher value. While the thermal cooling decreases proportionally to the reduction in I, the resistive heating term decreases as the square of I and hence more rapidly. such current reduction can be utilized to offset further the increase in the resistive heating term from convection. The net result is that under many important practical operating conditions, cooling efficiency increases. Calculations for specific TE systems are required to determine conditions that exhibit gain when utilizing convective transport.
An enlarged view of section B—B of the assembly 701 is depicted in FIG. 7B with a corresponding temperature profile (not to scale), 711 within the TE elements 704. The location x=0 is the interface between the TE elements 704 and circuitry 705 on the cold side substrate 703. Similarly, x=L is interface between the TE elements 704 and circuitry 705 on the hot side substrate 702. The temperature 711 is TA at x=0 and TH at x=L.
Assuming α, R and K are the same for TE systems 700 and 820, the movement of the air 709 in FIG. 8 causes three profound changes. First, as the TE elements 824 are heated by the I2R (resistive heating), a portion of the heat is convected toward the hot side and so a fraction of I2R heating larger than ½ I2R will move to the hot side. As a result, more of the I2R heating will contribute to the qh term of Equation 3 resulting in more heat transfer to the heated fluid. Second, the conduction loss at x=0 is lower because the slope of the temperature profile is less at x=0. Third, the air exiting the system at x=L carries up to all of the heat content qh. In some cases of interest, the air carries all the heat content, and when it does, efficiency gain is greatest.
FIG. 8B illustrates an enlargement of a portion along section 8B—8B of the TE array assembly 821 shown alongside the graph of temperature vs. position along the length of a TE element 824 for this configuration. Air flow 709 through the TE elements 824 is depicted. A corresponding temperature profile 831 of both the air 709 and the porous elements 824 (preferably assumed to be near equilibrium or equilibrium at all positions, x) is shown to the right. The temperature profile 831 in the graph in FIG. 8B shows that while the temperature reaches Th at L, just like the profile 711 for the TE system 700 in FIG. 7B, its shape for TE system 820 has greater curvature with less temperature rise near x=0. Generally, the TE system 820 offers greater efficiency, and hence has lower power consumption and operating costs to achieve a temperature TH for the same amount of air flow as compared to the system in FIG. 7A.
The pumps 909 cause the heat transfer fluids to move through the channels 910, forming the thermoelectric elements 902 as they flow between the substrates 922, 923, and to flow through the finned heat tubes 908. In the present embodiment, the flow of the heat transfer fluids 911, 912 convects heat from the cool side heat sink 906 to the hot side heat exchanger 907 under the action of the pumps 909. Within the hot side heat exchanger 907, heat is transferred to air or gas 932 entering at the left at temperature TH, and exiting at the right at temperature TH. The two pumps 909 and two separate finned tubes 908 carry, electrically isolated from one another, the two heat transfer fluids 911, 912. The heat transfer fluids' 911, 912 paths each are constructed to have high electrical resistance between the several connected fluid paths so that the required voltages can be applied across the TE elements 902 and the circuitry 925, without significant parasitic losses.
FIGS. 12A and 12B depict a construction of a TE array 1201 in which the TE elements form concentric tubes 1214-1216. FIG. 12A depicts a top view of the thermoelectric elements 1214, 1215 and 1216 only. FIG. 12B shows a cross-section through B—B of FIG. 12A, and adds the substrates 1202, 1203 and circuitry 1206 along with fluid flow from bottom to top. The TE array 1201 has hot and cool side substrates 1202 and 1203, circuitry 1206, and the concentric tubes 1214, 1215, and 1216. The holes in the circuitry and substrate 1205 are aligned with the annular gaps 1217 between the concentric tubes 1214, 1215, 1216. Heat transfer fluid 1218 passes through the annular gaps 1217. In FIG. 12, three concentric tubes are shown as an example. In this example, the tubes may alternate concentrically between p-type and n-type. Alternatively, the concentric tubes may each be of the same conductivity type, with the counter-type thermoelectric elements formed of another set of concentric tubes of the opposite type of thermoelectric material. The number of concentric tubes can be any practical number. Furthermore, the heat transfer fluid 1218 can also be directed along the outside diameter of the largest tube. Again, the tubes 1214, 1215, and 1216 are designed to be close to thermal equilibrium with the fluid 1218 along any line 1219 parallel to and between the substrates 1202 and 1203.
In the embodiment described in FIG. 9, the heat transfer fluid is liquid TE material while in the other embodiments, the heat transfer fluid is some other fluid such as air or water, or a slurry of TE materials and suitable media. Furthermore, a solid heat transfer material can also be employed. FIGS. 16A and 16B show one embodiment using a solid heat transfer material. FIG. 16A shows a plan view of the apparatus. FIG. 16B is sectional view from 16B—16B of FIG. 16A. A TE array 1601 is constructed with TE elements 1605 that are connected in series with circuitry 1606. Voltage, V is applied between the ends of the series circuit. A plurality of TE elements 1605 are arrayed with spaces between them. Filling each space is a heat transfer ring 1604 that has a plurality of circumferential ridges 1608 (like teeth) that fit within the space between the TE elements 1605. The remaining space between the TE elements 1605 and the heat transfer ring's ridges 1608 is filled with a thermally conducting lubricant 1607. The heat transfer ring 1604 is made from a material such as a metal-epoxy composite that has high thermal conductivity axially and radially, and low thermal conductivity circumferentially. As viewed in FIG. 16A, the ring 1604 rotates about its center in a counter-clockwise direction. A duct 1609 with inlet 1602 and outlet 1603 for the fluid to be heated 1610 surrounds that portion of the heat transfer ring 1604 that is not in thermal contact with the TE array 1601. It thereby creates a barrier so that the fluid 1610 is prevented from passing through the TE array region 1611. The fluid 1610 at temperature TA enters the duct 1609 at inlet 1602 and flows clockwise in FIG. 16A around the heat transfer ring exiting at the outlet 1603 at temperature TH. Thus the ring 1604 and duct 1609 form a reverse flow heat exchanger. As the heat transfer ring 1604 rotates counter-clockwise, it is heated in the region of the TE array 1601. The flow rate of the fluid 1610 and the rotational rate of the heat transfer ring 1604 are such that as the fluid 1610 flows clockwise, heat is transferred from the heat transfer ring 1604 to the fluid 1610 thereby cooling back to a temperature near TH, that portion of the heat transfer ring 1604 that is about to re-enter the TE array 1601. A heat pipe 1612 convects heat from an external heat sink to the cold side of the TE elements 1605.
Based on theoretical analysis that parallels that of Goldsmid, the optimum theoretical COP, φcm(δ) can be written as; ϕ c m ( δ ) = ( T c Δ T ) ( 1 + Z ( δ ) T ( δ ) - 1 - ξ ( δ ) Δ T T c 1 + Z ( δ ) T ( δ ) + 1 ) ( 26 ) I ( δ ) opt = α T c R ( 1 + Z ( δ ) T ξ - 1 1 + Z ( δ ) T ξ + 1 ) where ; ( 27 ) Z ( δ ) = α 2 R K ( δ ) ( 28 ) T ξ = T c + ξ ( δ ) 2 Δ T ( 29 ) Similarly, the COP, φcc(δ) for maximum cooling qc(δ) can be written as; ϕ cc = Z ( δ ) T C 2 - Δ T Z ( δ ) T C T H ( 30 ) If, in Equations 26 and 30, δ goes to zero the results become Equations 9 and 10, so the difference is due to δ, as expected.
The efficiency and ΔT of the TE system 1700 depicted in FIG. 17 increases by using convective heat transport in accordance with the present invention for example as shown by TE system 1800 in FIG. 18. In FIG. 18, a TE assembly 1801 is constructed with a main side substrate 1802 and a waste side substrate 1803 sandwiching a plurality of elongated TE elements 1804. TE elements may be porous, or have other configurations described above which permits fluid to flow through the TE element. Other configurations shown above may also be applicable with slight variations. The TE elements 1804 are connected by circuitry 1805. Voltage V 1812 is applied to the TE assembly 1801. The polarity of the voltage 1812 determines whether the main side is cooled or heated. A fan 1806 forces air 1813 at ambient temperature TA into the inlet 1807. The air from the inlet 1807 is introduced circumferentially to the TE array 1801 near the centers 1808 of the porous TE elements 1804, a point on the TE elements 1804 that is near ambient temperature TH. A portion of the air 1814 is ducted by a manifold and air passage 1809 through space between the TE elements 1804 and is collected and exits at the main side outlet 1810 and the remaining portion of the air 1815 is ducted to the waste side outlet 1811. COP and mass flow fraction on the main side can be 30-70% larger than with the traditional design.
It should be noted that the N- and P-type TE elements are made up of TE materials that have been drawn equal in size and shape. However, they need not be equal in size and shape to achieve optimum efficiency. The preferred requirement for efficient functionality is that; L n A p L p A n = ( ρ p λ n ρ n λ p ) ( 31 ) where;
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F25B21/02, F02G1/043Cooperative ClassificationF25B21/02, F02G2254/11, H01L35/32, F25B33/00, F02G1/043, F25B2321/021, H01L35/30, H01L35/00European ClassificationH01L35/32, F25B21/02, H01L35/00, F02G1/043, H01L35/30Legal EventsDateCodeEventDescriptionMay 23, 2006CCCertificate of correctionFeb 11, 2009FPAYFee paymentYear of fee payment: 4May 11, 2012ASAssignmentOwner name: BANK OF AMERICA, N.A., TEXASFree format text: SECURITY AGREEMENT;ASSIGNORS:AMERIGON INCORPORATED;BSST LLC;ZT PLUS, LLC;REEL/FRAME:028192/0016Effective date: 20110330Mar 14, 2013FPAYFee paymentYear of fee payment: 8Feb 9, 2015ASAssignmentOwner name: GENTHERM INCORPORATED, MICHIGANFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BSST LLC;REEL/FRAME:034925/0240Effective date: 20141112RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services