TWI707121B - An alternating notch configuration for spacing heat transfer sheets - Google Patents

Abstract

A heat transfer sheet for a rotary regenerative heat exchanger includes a plurality of rows of heat transfer surfaces each being aligned with a longitudinal axis extending between first and second ends thereof. The heat transfer surfaces have a height relative to a central plane of the heat transfer sheet. The heat transfer sheet includes one or more notch configurations for spacing the heat transfer sheets apart from one another. Each of the notch configurations are positioned between adjacent rows of heat transfer surfaces. The notch configurations include one or more lobes connected to one another, positioned in a common flow channel and extending away from the central plane and one or more lobes extending away from the central plane in an opposite direction and being coaxial. The lobes have a height relative to the central plane that is greater than the height of the heat transfer surfaces.

Description

Staggered groove configuration for separating heat transfer plates

The present invention relates to heat transfer fins of a rotating regeneration air preheater for transferring heat from a stream of flue gas to a stream of combustion air, and more particularly to the heat transfer fins for making adjacent heat transfer fins mutually A heat transfer sheet with a staggered groove configuration and an improved heat transfer efficiency.

Rotary regeneration air preheaters are generally used to transfer heat from a stream of flue gas discharged from a furnace to a stream of incoming combustion air to improve the efficiency of the furnace. The conventional preheater includes a heat transfer sheet assembly including a plurality of heat transfer sheets stacked on top of each other in a basket. The heat transfer fins absorb heat from the flue gas stream and transfer this heat to the combustion air stream. The preheater further includes a rotor with a radial baffle or diaphragm defining a compartment containing a separate heat transfer fin assembly. The preheater includes a fan-shaped plate extending across the upper and lower surfaces of the preheater to divide the preheater into one or more gas sectors and air sectors. The hot flue gas stream and the combustion air stream are simultaneously guided through each sector. The rotor rotates the flue gas and combustion air sectors in and out of the flue gas stream and the combustion air stream to heat and then cool the heat transfer fins, thereby heating the combustion air stream and cooling the flue gas stream. The conventional heat transfer sheets used in these preheaters are usually made by forming, pressing or rolling a piece of steel. A typical heat transfer sheet includes sheet partition members formed therein to position adjacent sheets spaced apart from each other and provide the structural integrity of the assembly of the plurality of heat transfer sheets in the basket. The adjacent pair of partition members form a channel for flue gas or combustion air to flow through. Some heat transfer sheets include undulating patterns between the sheet partition members to hinder the flow in a portion of the channel and thereby generate turbulence that increases the heat transfer efficiency. However, the typical sheet partitioning member has a feature that allows flue gas or combustion air to flow uninterruptedly at high speeds and with little or no turbulence through the open sides formed by the sheet partitioning members. One of the channels is configured. As a result of the uninterrupted high-speed flow, the heat transfer from the flue gas or combustion air to the partition member is minimal. It is generally known that generating turbulence through a plurality of heat transfer fins, such as through channels defined by and between adjacent fin partition members, increases the pressure drop across the preheater. In addition, it has been found that the sudden change in the flow direction caused by the sudden contour change of the heat transfer sheet increases the pressure drop and forms stagnant flow areas or zones, which often lead to particles (eg, ash) Accumulate in one of the areas of stagnant flow. This further increases the pressure drop across the preheater. This increased pressure drop reduces the overall efficiency of the preheater due to the increased fan power required to push the combustion air through the preheater. The efficiency of the preheater is also reduced due to the increase in the power required to rotate the flue gas and combustion air sector into and out of the flue gas and combustion air stream, as the weight of the heat transfer fin assembly in the basket increases. Therefore, there is a need for improved lightweight heat transfer fins with increased heat transfer efficiency and low pressure drop characteristics.

This article discloses a heat transfer fin for a rotary regenerative heat exchanger. The heat transfer sheet includes a plurality of rows of heat transfer surfaces. Each of the plurality of rows is aligned with a longitudinal axis extending between an inlet end and an outlet end of the heat transfer sheet. The heat transfer surfaces have a first height relative to a center plane of the heat transfer sheet. The heat transfer sheet includes one or more groove configurations for separating the heat transfer sheets from each other. The groove configurations are positioned between adjacent rows of heat transfer surfaces. The groove configurations include: one or more first lobes extending away from the central plane in a first direction; and one or more second lobes extending in a second direction opposite to the first direction Extend away from the central plane. The first lobes and the second lobes each have a second height relative to the center plane. The second height is greater than the first height. The first lobes and the second lobes are connected to each other and are in a common flow channel. In one embodiment, the first lobes and the second lobes are coaxial with each other along an axis parallel to the longitudinal axis. This article also discloses a heat transfer assembly for a rotary regenerative heat exchanger. The heat transfer assembly includes two or more heat transfer fins stacked on top of each other. Each of the heat transfer sheets includes a plurality of rows of heat transfer surfaces. Each of the rows is aligned with a longitudinal axis extending between an inlet end and an outlet end of the heat transfer assembly. The heat transfer surfaces have a first height relative to a center plane of the heat transfer sheet. Each of the heat transfer fins includes one or more groove configurations for separating the heat transfer fins from each other. Each of the groove configurations is positioned between adjacent rows of heat transfer surfaces. Each of the groove configurations includes: one or more first lobes that extend away from the central plane in a first direction; and one or more second lobes that are opposite to the first direction A second direction extends away from the central plane. The first lobes and the second lobes are connected to each other and are in a common flow channel. Each of the first lobes and the second lobes has a second height relative to the center plane. The second height is greater than the first height. The first flap of the first one of the heat transfer fins engages the heat transfer surface of the second one of the heat transfer fins; and the second flap of the second one of the heat transfer fins engages the The heat transfer surface of the first heat transfer sheet defines a flow path between the heat transfer sheets. The flow path extends from the inlet end to the outlet end. In one embodiment, the first lobes and the second lobes are coaxial with each other along an axis parallel to the longitudinal axis. In one embodiment, the groove configuration includes one or more flow diversion configurations defined by a transition zone connecting one of the first lobes and one of the second lobes. The transition zone is formed into an arcuate and/or flat shape. The first petals and/or the second petals are formed to have an S-shaped and/or C-shaped cross section. In one embodiment, the heat transfer surfaces include undulating surfaces that are angularly offset from the longitudinal axis. A stack of heat exchanger fins is also disclosed herein. The stack of heat exchanger fins includes one or more first heat transfer fins. Each of the first heat transfer sheets includes a first undulating surface extending along the first heat transfer sheet and oriented at a first angle with respect to a flow direction through the stack. The first heat transfer fins also include a second undulating surface extending along the first heat transfer fin and oriented at a second angle with respect to the flow direction through the stack, the first angle and the second undulating surface The angles are different, for example, in a herringbone pattern. The stack of heat transfer fins further includes one or more second heat transfer fins. Each of the second heat transfer fins defines a plurality of groove configurations that are parallel to the expected flow direction at a first end and a first end of at least one second heat transfer fin A longitudinal axis extending between the two ends is used to separate the first heat transfer fin from the adjacent one of the second heat transfer fins. One or more of the groove configurations include: one or more first lobes that extend away from a central plane of the second heat transfer sheet in a first direction; and one or more second lobes, It extends away from the central plane in a second direction opposite to the first direction. The first lobes and the second lobes are connected to each other and are in a common flow channel. One or more of the first lobes engage the first undulating surface and/or a portion of the second undulating surface; and/or one or more of the second lobes engage the first undulating surface and/or Or a part of the second undulating surface to define a flow path between the first heat transfer sheet and the second heat transfer sheet. In one embodiment, the first lobes and the second lobes are coaxial with each other along an axis parallel to the longitudinal axis. This article further discloses a spacer for a stack of heat transfer fins. The spacer includes a plurality of groove configurations, and the plurality of groove configurations extend along a longitudinal axis extending between a first end and a second end of the spacer parallel to the expected flow direction for Separate adjacent heat transfer fins from each other. The groove configurations include: one or more first lobes extending away from a central plane of the spacer along a first direction; and/or one or more second lobes extending along the first direction The opposite second direction extends away from the central plane. The first lobes and the second lobes are connected to each other and are in a common flow channel. In one embodiment, the first lobes and the second lobes are coaxial with each other along an axis parallel to the longitudinal axis. In one embodiment, the groove configuration of the spacer includes one or more flows defined by a transition zone connecting one of the first lobes and one of the second lobes Turn to configuration. In one embodiment, successive ones of the transition regions are separated from each other by a distance of one from 2 to 8 inches. In one embodiment, one or more of the transition regions (eg, at least one) defines a longitudinal distance of 0.25 to 2.5 inches. In one embodiment, adjacent groove configurations among the groove configurations are spaced apart from each other by 1.25 to 6 inches measured perpendicular to the longitudinal axis. In one embodiment, the configurations define a ratio of a height of the groove configuration to a longitudinal spacing between the continuous transition areas from 5:1 to 20:1. In one embodiment, the groove configurations define a ratio of a height of the configuration to a height of the heat transfer surface from 1.0:1 to 4.0:1. In one embodiment, the undulating surfaces define a plurality of undulating peaks, adjacent undulating peaks of the undulating peaks are separated by a predetermined distance, and a ratio of the predetermined distance to the first height is 3.0:1 to 15.0 :1.

As shown in FIG. 1, a rotary regeneration air preheater (hereinafter referred to as a "preheater") is generally designated by the number 10. The preheater 10 includes a rotor assembly 12 rotatably mounted on a rotor column 16. The rotor assembly 12 is positioned in a housing 14 and rotates relative to the housing 14. For example, the rotor assembly 12 can rotate around an axis A of the rotor column 16 in the direction indicated by the arrow R. The rotor assembly 12 includes a diaphragm 18 (for example, a diaphragm) extending radially from the rotor column 16 to an outer periphery of the rotor assembly 12. The adjacent pair of partitions 18 define respective compartments 20 for receiving a heat transfer assembly 1000. Each of the heat transfer assembly 1000 includes a plurality of heat transfer sheets 100 and/or 200 (for example, see FIGS. 4A and 4B showing one of two heat transfer sheets stacked) stacked on top of each other In other words, see Figure 2A and Figure 3A respectively). As shown in FIG. 1, the housing 14 includes a flue gas inlet tube 22 and a flue gas outlet tube 24 for flowing the heated flue gas through the preheater 10. The housing 14 further includes an air inlet pipe 26 and an air outlet pipe 28 for flowing combustion air through the preheater 10. The preheater 10 includes an upper sector plate 30A adjacent to an upper surface of the rotor assembly 12 and extending across the housing 14. The preheater 10 includes a lower sector plate 30B adjacent to the lower surface of the rotor assembly 12 and extending across the housing 14. The upper sector plate 30A extends between the flue gas inlet pipe 22 and the air outlet pipe 28 and is connected to the flue gas inlet pipe 22 and the air outlet pipe 28. The lower fan-shaped plate 30B extends between the flue gas outlet pipe 24 and the air inlet pipe 26 and is connected to the flue gas outlet pipe 24 and the air inlet pipe 26. The upper sector plate 30A and the lower sector plate 30B are connected to each other by a circumferential plate 30C, respectively. The upper sector plate 30A and the lower sector plate 30B divide the preheater 10 into an air sector 32 and a gas sector 34. As illustrated in FIG. 1, the arrow labeled "A" indicates the direction of a flue gas stream 36 passing through the gas sector 34 of the rotor assembly 12. The arrow labeled "B" indicates the direction of a combustion air stream 38 passing through the air sector 32 of the rotor assembly 12. The flue gas stream 36 enters through the flue gas inlet pipe 22 and transfers heat to the heat transfer assembly 1000 installed in the compartment 20. The heated heat transfer assembly 1000 rotates into the air sector 32 of the preheater 10. Then, the heat stored in the heat transfer assembly 1000 is transferred to the combustion air stream 38 entering through the air inlet pipe 26. Therefore, the heat absorbed from the hot flue gas stream 36 entering the preheater 10 is used to heat the heat transfer assembly 1000, which in turn heats the combustion air stream 38 entering the preheater 10 . As illustrated in FIGS. 2A, 2B, 2C, and 5A, the heat transfer sheet 100 includes a plurality of rows (for example, two rows F and G are illustrated in FIG. 2A) of heat transfer surfaces 310. The rows F and G of the heat transfer surface 310 are parallel to the flow of flue gas and combustion air (as indicated by arrows A and B, respectively) at a first end 100X and a second end of the heat transfer sheet 100 A longitudinal axis L extending between 100Y is aligned. When the heat transfer sheet 100 is in the air sector 32, the first end 100X is used for an inlet of the combustion air stream 38 and the second end 100Y is used for an outlet of the combustion air stream 38. When the heat transfer sheet 100 is in the gas sector 34, the first end 100X is used for an outlet of the flue gas stream 36 and the second end 100Y is used for an inlet of the flue gas stream 36. The heat transfer surface 310 has a first height H1 relative to a center plane CP of the heat transfer sheet 100, as shown in FIG. 2B. In one embodiment, the heat transfer surface 310 is defined by an undulating surface that is angularly offset from the longitudinal axis L, as described further herein. As illustrated in FIGS. 2A, 2B, 2C, and 5A, the heat transfer sheet 100 includes a plurality of groove configurations 110 for separating the heat transfer sheets 100 from each other, as further described herein with reference to FIG. 4B. One of the groove configurations 110 is positioned between row F and row G of the heat transfer surface. The other of the groove configurations 110 is positioned between the row F of the heat transfer surface 310 and another adjacent row (not shown); and the other of the groove configurations 110 is positioned between the row G of the heat transfer surface 310 and Between another adjacent column (not shown). Each of the groove configurations 110 is parallel to the longitudinal axis L and extends longitudinally along the heat transfer sheet 100 between the first end 100X and the second end 100Y of the heat transfer sheet 100. As further described herein with reference to FIG. 4B, the groove configuration engages the heat transfer surface 310 adjacent to the heat transfer fins 100 to separate the heat transfer fins 100 from each other and define a flow path P between the heat transfer fins 100. As shown in FIGS. 2A and 5A, the groove configuration 110 includes four lobes that are collectively referred to as a staggered full groove design. The lobes include adjacent double lobes connected to each other along the longitudinal axes L1 and L2. , As further described herein with reference to FIGS. 2A and 2C. For example, one double lobe is defined by a first lobe 160L and a second lobe 170R; and another longitudinally aligned and inverted double lobe is defined by a second lobe 170L and a first lobe 160R. Therefore, the groove configuration 110 has an S-shaped cross-section. As shown in FIG. 5A, each of the groove configurations 110 is in a common flow channel defined by longitudinal boundary lines L100 and L200 (shown as dashed lines) parallel to the longitudinal axes L1 and L2. The common flow path defines a localized longitudinal flow of the flue gas 36 and the combustion air 38 in the flow path P (for an example of the flow path P, see FIG. 4B). As shown in FIG. 5A, the common flow channel has a width D100 measured between the longitudinal boundary lines L100 and L200. In one embodiment, the width D100 is approximately equal to the width D101 of the groove configuration 110. In one embodiment, the width D100 is between 1.0 and 1.1 times the width D101 of the groove configuration. In one embodiment, the width D100 is between 1.0 and 1.2 times the width of the groove configuration. One of the four lobe configurations is a first lobe configuration. The first lobe configuration is defined by a plurality of first lobes 160L extending away from the central plane CP in a first direction. The first flap 160L is in the common flow channel. In the embodiment illustrated in FIG. 5A, the first lobes 160L are spaced apart from each other along a first longitudinal axis L1 and are coaxially aligned with each other (e.g., one of the first lobes 160L is positioned close to the first end 100X (see FIG. 2A), and the second one of the first petals 160L is positioned close to the second end 100Y (see FIG. 2A)). The first petal 160L and the second petal 170L are longitudinally spaced apart and coaxially aligned, and laterally abut one of the second petals 170R. The other of the four lobe configurations is a second lobe configuration. The second lobe configuration is defined by a plurality of first lobes 160R extending away from the center plane CP in the first direction. The first valve 160R is in the common flow channel. In the embodiment illustrated in FIG. 5A, the first lobes 160R are longitudinally spaced from each other along a second longitudinal axis L2 and are coaxially aligned with each other. The first petal 160R and the second petal 170R are longitudinally spaced apart and coaxially aligned, and laterally abut one of the second petals 170L. The other of the four lobe configurations is a third lobe configuration. The third lobe configuration is defined by a plurality of second lobes 170L extending away from the central plane CP in a second direction. The second lobe 170L is in the common flow channel. In the embodiment illustrated in FIG. 5A, the second lobes 170L are longitudinally spaced apart from each other along the first longitudinal axis L1 and are coaxially aligned with each other (e.g., one of the second lobes 170L is positioned close to the first Between the first petal 160L at one end 100X and the first petal 160L positioned close to the second end 100Y). The second direction is opposite to the first direction. The second petal 170L is longitudinally spaced apart from and coaxially aligned with the first petal 160L, and laterally abuts one of the first petals 160R. The other of the four lobe configurations is a fourth lobe configuration. The fourth lobe configuration is defined by a plurality of second lobes 170R extending away from the center plane CP in the second direction. The second petal 170R is in the common flow channel. In the embodiment illustrated in FIG. 5A, the second lobes 170R are longitudinally spaced apart from each other along the second longitudinal axis L2 and are coaxially aligned with each other (e.g., one of the second lobes 170R is positioned close to the first end 100X, and the other of the second lobes 170R is positioned close to the second end 100Y, where one of the first lobes 160R is positioned between the two). The second petal 170R is longitudinally spaced from the first petal 160R and aligned coaxially, and laterally abuts one of the first petals 160L. Therefore, the first petals 160L and 160R extend away from the first surface 112 of the heat transfer sheet 100 in the first direction; and the second petals 170L and 170R extend away from the second surface 114 of the heat transfer sheet 100 in the second direction. The adjacent groove configuration 110 is separated by one of the rows F or G of the heat transfer surface 310 and crosses the heat transfer sheet 100 transversely (for example, perpendicular to the axis L) between an S-shaped section and an inverted S-shaped section staggered. As shown in FIG. 5A, each of the first lobes 160L is longitudinally adjacent to one of the second lobes 170L aligned along an axis L1 parallel to the longitudinal axis L of the heat transfer sheet 100. Therefore, the first lobe 160L and the second lobe 170L are coaxial and configured in a staggered longitudinal pattern in which the first lobe 160L is away from the central plane CP in the first direction (away from the page in FIG. 5A) and The second petal 170L faces away from the center plane in the second direction (entering the page in FIG. 5A). Likewise, in the embodiment shown in FIG. 5A, the first lobe 160R and the second lobe 170R are coaxial and in a common flow channel. The first lobe 160R and the second lobe 170R are configured to form a staggered longitudinal pattern in which the first lobe 160R is away from the center plane CP in the first direction and the second lobe 170R is away from the center plane CP in the second direction . In addition, the first petal 160L and the second petal 170R are adjacent to each other in a direction transverse to the longitudinal axis; and the first petal 160R and the second petal 170L are adjacent to each other in a direction transverse to the longitudinal axis L. As shown in FIG. 2A, each of the first lobes 160L and 160R and each of the second lobes 170L and 170R extend a length L6 along the sheet in a longitudinal direction parallel to the longitudinal axis L. Although three lobes (ie, two first lobes 160L and one second lobe 170L) are shown along axis L1 and between the first end 100X and the second end 100Y; and three lobes (ie, two The second petal 170R and one first petal 160L) are shown along the axis L2 and between the first end 100X and the second end 100Y, but the present invention is not limited to this, because it depends on the preheater The design parameters can adopt any number of first lobes 160R, 160L and second lobes 170R and 170L between the first end 100X and the second end 100Y. As shown in FIG. 2B, the first lobes 160L and 160R and the second lobes 170L and 170R have a second height H2 relative to the center plane CP. The second height H2 is greater than the first height H1. Although the first lobes 160L and 160R and the second lobes 170L and 170R are all shown and described as having the second height H2, the present invention is not limited to this, because the first lobes 160L and 160R and the second lobes 170L and 170R are more May have different heights from each other (for example, H2 and/or H3 as shown in FIG. 2F) (for example, either or both of the first lobes 160L and 160R and the second lobes 170L and 170R are relative to the central plane It has a second height H2 or a third height H3, as shown in Figure 2F, where H3 is smaller than H2). As illustrated in FIG. 2C, each of the groove configurations 110 includes a transition region 140L that connects the first lobe 160L and the second lobe 170L longitudinally and one of the first lobe 160R and the second lobe 170R longitudinally. The transition zone 140R defines a flow turning configuration (for example, a flow stagnation mitigation path). The transition region 140L extends a predetermined length L5 along the axis L1 between the first lobe 160L and the second lobe 170L; and the transition region 140R extends a predetermined length L5 along the axis L2 between the first lobe 160R and the second lobe 170R. In one embodiment, the transition regions 140L and 140R are formed by plastically deforming heat transfer fins. The flow turning configuration (for example, a flow stagnation mitigation path) is further defined by a smooth and radical change in the direction of the flow path to reduce or eliminate the localized low-speed flow area (for example, vortex) to prevent accumulation of particles (for example, ash) . The flow turning configuration (for example, a flow stagnation mitigation path) enables a turbulent flow pattern to appear therein. The width D100 of the common flow channel is configured to allow turbulence patterns to not form in the transition zone 140L and/or 140R or otherwise between the first lobes 160L, 160R and the second lobes 170L, 170R Appears in any situation where the flow is stagnant. Therefore, the transition regions 140L and 140R and each of the first lobes 160L, 160R and the second lobes 170L, 170R are in close proximity to each other. Therefore, the width D100 of the common flow channel has a predetermined value that is sufficient to eliminate (ie, narrow enough) the bypass flow into the region of the heat transfer surface 310. In addition, the groove configuration 110 and the common flow channel are configured to eliminate the direct high-speed bypass of the flue gas 36 and the combustion air 38 in the localized pipe or tunnel passing through the flow path P. This direct high-speed bypass of the flue gas 36 and the combustion air 38 in the localized pipe passing through the flow path P or the tunnel reduces the heat transfer efficiency of the heat transfer fin 100. As shown in Figure 5A, the transition regions 140L and 140R are in a common flow channel. In the embodiment shown in FIG. 5A, the transition zone 140L is coaxial with the first and second lobes 160L and 170L; and the transition zone 140R is coaxial with the first and second lobes 160R and 170R. Although in FIGS. 2A and 5A, the first lobe 160L, the first transition region 140L, and the second lobe 170L are shown and described as coaxial, the present invention is not limited to this, because the first lobe 160L, the first transition The regions 140L and/or the second petal 170L may be offset from each other and the longitudinal axis L1; and/or the first petal 160R, the second transition region 140R, and/or the second petal 170R may be offset from each other and the longitudinal axis L2. For example, the heat transfer sheet 100' of FIG. 5B illustrates that the first lobe 160L', the first transition region 140L', and/or the second lobe 170L' are in a common flow channel, and the first lobe 160L' and the second lobe The petals 170L' deviate perpendicular to the longitudinal axis L1, and the transition region 140L' connects the first lobe 160L' and the second lobe 170L' and is angularly offset from the longitudinal axis L1, and a portion of the transition region 140L' crosses the longitudinal axis L1. FIG. 5B also illustrates that the first petal 160R', the second transition region 140R', and/or the second petal 170R' are in the common flow channel, and the first petal 160R' and the second petal 170R' are perpendicular to the longitudinal axis L2. The transition zone 140R' connects the first lobe 160R' and the second lobe 170R' and is angularly offset from the longitudinal axis L2, and a portion of the transition zone 140R' crosses the longitudinal axis L2. As shown in FIG. 5B, the common flow channel has a width D100, and 1) a first lobe 160L, a first transition zone 140L, and/or a second lobe 170L and 2) a first lobe 160R, a second transition zone 140R, and/or The second lobe 170R is within a width D101' which is less than or equal to the width D100. The heat transfer sheet 100" of FIG. 5C illustrates that the first petal 160L", the first transition region 140L" and/or the second petal 170L" are in the common flow channel, and the first petal 160L" and the second petal The two lobes 170L" are angularly offset from the longitudinal axis L1, and a part of the first lobe 160L" and the second lobe 170L" cross the longitudinal axis L1, and the transition zone 140L" connects the first lobe 160L" and the second lobe 160L"170L''. Figure 5C also illustrates that the first valve 160R", the second transition region 140R" and/or the second valve 170R" are in the common flow channel, and the first valve 160R" and the second valve 170R" form Angularly deviate from the longitudinal axis L2, and a portion of the first lobe 160R" and the second lobe 170R" cross the longitudinal axis L2, and the transition region 140R" connects the first lobe 160R" and the second lobe 170R". As shown in FIG. 5C, the common flow channel has a width D100, and 1) a first lobe 160L, a first transition zone 140L, and/or a second lobe 170L and 2) a first lobe 160R, a second transition zone 140R, and/or The second lobe 170R is within a width D101" that is less than or equal to the width D100. Each of the groove configurations 110 extends a total cumulative longitudinal length across the entire heat transfer sheet 100. The total cumulative length of each of the groove configurations 110 is the sum of the length L6 of the first lobe 160L and the second lobe 170L plus the sum of the length L5 of the transition zone 140L. The total cumulative length of each of the groove configurations 110 is also the sum of the length L6 of the first lobe 160R and the second lobe 170R plus the sum of the length L5 of the transition zone 140R. Although the groove configuration is shown and described as extending a total cumulative length across the entire heat transfer sheet 100, the present invention is not limited to this, because any groove configuration 110 can extend less than the entire heat transfer sheet, for example , Between 90% and 100% of the total length of the heat transfer sheet 100, between 80% and 91% of the total length of the heat transfer sheet 100, between 70% of the total length of the heat transfer sheet 100 and Between 81%, between 60% and 71% of the total length of the heat transfer sheet 100, or between 50% and 61% of the total length of the heat transfer sheet 100. As shown in FIG. 2C, the transition zone 140L includes: 1) an arcuate portion 145L extending from a peak 160LP of the first petal 160L; 2) a transition surface 141L (for example, a flat or arcuate surface), which extends from the arcuate portion 145L Transition; and 3) an arcuate portion 143R, which transitions from the transition surface 141L to a valley 170LV of the second petal 170L. Similarly, the transition zone 140R includes: 1) an arcuate portion 143R extending from a peak 160RP of the first petal 160R; 2) a transition surface 141R (for example, a flat or arcuate surface) that transitions from the arcuate portion 143R; and 3 ) An arcuate portion 145R that transitions from the transition surface 141R to a valley 170RV of the second petal 170R. In one embodiment, the transition regions 140L and 140R are longitudinally aligned with each other (ie, in a side-by-side configuration). In one embodiment, the transition regions 140L and 140R are longitudinally offset from each other (eg, staggered along the longitudinal axes L1 and L2, respectively). In one embodiment, one or both of the transition regions 140L and 140R has a straight portion coaxial with the central plane CP and positioned between the respective arcuate portions 143R and 145R or 143L and 145L, as described herein with respect to The staggered half-groove configuration is shown and described in Figure 3E, Figure 3F and Figure 3G. The inventors have surprisingly found that, compared with the prior art sheet partitioning member extending from only one side of the heat transfer sheet, the transition regions 140L and 140R provide the flow direction of the flue gas 36 and the combustion air 38 in the flow path P Smooth turns, which generate turbulence and the increased heat transfer efficiency of the heat transfer fins 100 described herein. The heat transfer fins 100 also provide sufficient structural support and maintain the spacing between adjacent heat transfer fins 100 without significantly increasing the pressure loss across the heat transfer fins 100. As illustrated in FIGS. 3A, 3B, and 6A, another embodiment of a heat transfer sheet is designated by the number 200. The heat transfer sheet 200 includes a plurality of rows (for example, two rows F and G are illustrated in FIG. 3A) of heat transfer surfaces 310. The rows F and G of the heat transfer surface 310 are parallel to the flow of flue gas and combustion air (as indicated by arrows A and B, respectively) at a first end 200X and a second end 200Y of a heat transfer sheet 200 A longitudinal axis L extending between is aligned. When the heat transfer fin 200 is in the air sector 32, the first end 200X is used for an inlet of the combustion air stream 38 and the second end 200Y is used for an outlet of the combustion air stream 38. When the heat transfer sheet 200 is in the gas sector 34, the first end 200X is used for an outlet of the flue gas stream 36 and the second end 200Y is used for an inlet of the flue gas stream 36. The heat transfer surface 310 has a first height H1 relative to a center plane CP of the heat transfer sheet 200, as shown in FIG. 3C. In one embodiment, the heat transfer surface 310 is defined by an undulating surface that is angularly offset from the longitudinal axis L, as described further herein. As illustrated in FIGS. 3A, 3B, and 6A, similar to the groove configuration 110 shown in FIG. 4B, the heat transfer sheet 200 includes a plurality of groove configurations for separating the heat transfer sheet 200 from each other 210. One of the groove configurations 210 is positioned between the row F and the row G of the heat transfer surface 310. The other of the groove configurations 210 is positioned between the row F of the heat transfer surface 310 and another adjacent row (not shown); and the other of the groove configurations 210 is positioned between the row G and the row G of the heat transfer surface 310 Between another adjacent column (not shown). Each of the groove configurations 210 is parallel to the longitudinal axis L and extends longitudinally along the heat transfer sheet 200 between the first end 200X and the second end 200Y of the heat transfer sheet 200. Similar to the groove configuration 110 shown in FIG. 4B, the groove configuration 210 engages the heat transfer surface 310 adjacent to the heat transfer fins 200 to separate the heat transfer fins 200 from each other and define a flow between the heat transfer fins 200 Access P. As shown in FIG. 3A, the groove configuration 210 includes a lobe configuration called a staggered half groove configuration, which includes a plurality of first lobes 260 and a plurality of second lobes 270. The adjacent ones of the first petal 260 and the second petal 270 are connected to each other along the longitudinal axis L3. Another set of adjacent lobes of the first petal 260 and the second petal 270 are connected to each other along a longitudinal axis L4 that is laterally spaced from the longitudinal axis L3. The first petal 260 and the second petal 270 of the groove configuration 210 are single petals with a C-shaped cross-section. As shown in FIG. 3A, a set of first lobes 260 extend away from the central plane CP along a first direction (in FIG. 6A, the first direction is away from the page). As shown in FIG. 6A, the first petal 260 is in a first common flow channel defined between the boundary line (shown as a dashed line in FIG. 6A) L100 and L200. The common flow channel has a width D100. In the embodiment shown in Figure 6A, the first lobes 260 are coaxially aligned with each other along the longitudinal axis L3. Another set of first lobes 260 extend away from the center plane CP in the first direction. As shown in FIG. 6A, another set of petals 260 is in a second common flow channel defined between boundary lines L100 and L200. The other common flow channel has a width D100. In the embodiment shown in Figure 6A, another set of petals 260 are coaxially aligned with each other along the longitudinal axis L4. In one embodiment, the width D100 is approximately equal to the width D101 of the groove configuration 210. In one embodiment, the width D100 is between 1.0 and 1.1 times the width D101 of the groove configuration 210. In one embodiment, the width D100 is between 1.0 and 1.2 times the width of the groove configuration 210. As shown in FIG. 3A, a set of second lobes 270 extend away from the center plane CP in a second direction (in FIG. 6A, the second direction is the entry page). As shown in FIG. 6A, the second petal 270 is in a first common flow channel defined by the boundary lines L100 and L200. In the embodiment shown in Figure 6A, the second lobes 270 are coaxially aligned with each other along the longitudinal axis L3. Another set of second lobes 270 extend away from the center plane CP in the second direction. As shown in Figure 6A, another set of petals 270 is in the second common flow channel. In the embodiment shown in FIG. 6A, another set of second lobes 270 are coaxially aligned with each other along the longitudinal axis L4. The second direction is opposite to the first direction. Therefore, the first petal 260 extends away from the first surface 212 of the heat transfer sheet 200 in the first direction; and the second petal 270 extends away from the second surface 214 of the heat transfer sheet 200 in the second direction. As shown in FIGS. 3A and 6A, the groove configuration 210 and therefore the first petal 260 and the second petal 270 are in the first common flow channel. The first petal 260 and the second petal 270 in the first common flow channel are connected to each other, are coaxial with each other, and are configured to form a staggered longitudinal pattern. In the staggered longitudinal pattern, the first petal 260 is away from the central plane CP in the first direction And the second petal 270 is away from the center plane in the second direction and aligned coaxially along the longitudinal axis L3. In addition, another set of the first petal 260 and the second petal 270 (ie, another groove configuration 210) is in the second common flow channel. The other set of first petals 260 and second petals 270 in the second common flow channel are coaxial with each other and are configured in a staggered longitudinal pattern. In the staggered longitudinal pattern, the first petal 260 is away from the central plane CP in the first direction And the second petal 270 is away from the center plane in the second direction and aligned coaxially along the longitudinal axis L4. The first petal 260 aligned with the longitudinal axis L3 is longitudinally offset from the first petal 260 aligned with the longitudinal axis L4. The first petal 260 aligned with the longitudinal axis L4 is longitudinally offset from the first petal 260 aligned with the longitudinal axis L3. Similarly, the second petal 270 aligned with the longitudinal axis L3 is longitudinally offset from the second petal 270 aligned with the longitudinal axis L4; and the second petal 270 aligned with the longitudinal axis L4 is longitudinally offset from the first petal aligned with the longitudinal axis L3 Two petals 270. Therefore, in a direction transverse to the longitudinal axis L3 and L4, one of the first petal 260 and the second petal 270 are aligned. In a direction transverse to the longitudinal axes L3 and L4, the first petal 260 and the second petal 270 are separated from each other by the heat transfer surface 310. Similar to the groove configuration 110 shown in FIG. 2B, the first lobe 260 and the second lobe 270 have a second height H2 relative to the center plane CP. The second height H2 is greater than the first height H1 of the heat transfer surface 310. Although the first petal 260 and the second petal 270 are all shown and described as having the second height H2, the present invention is not limited to this, because the first petal 260 and the second petal 270 may have different heights than each other. As illustrated in FIG. 3B, each of the groove configurations 210 includes a flow diversion group defined by a transition region 240 of the first petal 260 and the second petal 270 aligned longitudinally with the longitudinal axis L3 state. Similarly, the groove configuration 210 includes a flow diversion configuration defined by a transition region 240 of the first petal 260 and the second petal 270 that are longitudinally connected and aligned with the longitudinal axis L4. The transition area 240 extends a predetermined length L5 between the first petal 260 and the second petal 270 along the axis L3. The first petal 260 and the second petal 270 aligned along the longitudinal axis L4 have a transition region 240 similar to the transition region 240 aligned along the longitudinal axis L3. In one embodiment, the transition regions 240 of the groove configuration 210 along the longitudinal axis L3 and the longitudinal axis L4 are longitudinally offset from each other. In one embodiment, the transition regions 240 of the groove configuration 210 along the longitudinal axis L3 and the longitudinal axis L4 are longitudinally aligned with each other (ie, in a side-by-side configuration). In one embodiment, the transition zone 240 is formed by plastically deforming the heat transfer sheet 200. The flow turning configuration (ie, the transition zone 240) is, for example, a flow stagnation mitigation path and is further defined by a smooth and radical change in the direction of the flow path to reduce or eliminate localized low-velocity flow areas (e.g., vortices) To prevent the accumulation of particles (for example, ash). The flow turning configuration (for example, a flow stagnation mitigation path) enables a turbulent flow pattern to appear therein. The width D100 of the flow channel is configured to allow turbulent flow patterns to occur in the transition zone 240 or otherwise between any of the first petal 260 and the second petal 270 without any flow stagnation area. Therefore, the transition region 240 and each of the first petal 260 and the second petal 270 are close to each other. Therefore, the width D100 of the common flow channel has a predetermined value that is sufficient to eliminate (ie, narrow enough) the bypass flow into the region of the heat transfer surface 310. In addition, the groove configuration 210 and the common flow channel are configured to eliminate the direct high-speed bypass of the flue gas 36 and the combustion air 38 in the localized pipe or tunnel passing through the flow path P. The direct high-speed bypass of the flue gas 36 and the combustion air 38 in the localized pipe passing through the flow path P or the tunnel reduces the heat transfer efficiency of the heat transfer fin 200. As shown in FIG. 3B, the transition region 240 includes: 1) an arcuate portion 245 extending from a peak 260P of the first petal 260; 2) a transition surface 241 (for example, the flat surface shown in FIG. 3G or the flat surface shown in FIG. 3C The arcuate surface shown in)), which transitions from the arcuate portion 245; and 3) an arcuate portion 243, which transitions from the transition surface 241 to the valley 270V of the second petal 270. In one embodiment shown in Figure 3D, the arcuate portions 243 and 245 are replaced with flat or straight portions 243' and 245', and the transition surface 241 is replaced with a transition point 241'. In one embodiment shown in FIGS. 3E, 3F, and 3G, the transition region 240 includes an extended straight section 241T that is coaxial with the center plane CP. As shown in FIGS. 3E and 3F, the straight section 241T extends between adjacent arcuate portions 243 and 245. As shown in Figure 3G, straight section 241T extends between straight sections 243' and 245'. In one embodiment, the straight section 241T is about 5% of the longitudinal distance L7. In one embodiment, the straight section 241T is greater than 0% of the longitudinal distance L7. In one embodiment, the straight section 241T is about 5% to 25% of the longitudinal distance L7. In one embodiment, the straight section 241T is about 5% to 100% of the longitudinal distance L7. In one embodiment, the straight section 241T is greater than 100% of the longitudinal distance L7. The inventors have surprisingly found that, compared with the prior art sheet partition member extending from only one side of the heat transfer sheet, the transition zone 240 provides a smooth flow of the flue gas 36 and the combustion air 38 in the flow path P Turning, these smooth flow turns generate turbulence and the increased heat transfer efficiency of the heat transfer fins 200 described herein. The heat transfer fins 200 also provide sufficient structural support and maintain the spacing between adjacent heat transfer fins 200 without significantly increasing the pressure loss across the heat transfer fins 200. As shown in FIG. 6A, a first set of transition zones 240 are in the first common flow channel; and another set of transition zones 240 are in the second common flow channel. In the embodiment shown in FIG. 6A, for the first common flow channel, the first set of transition regions 240 are coaxial with the first 260 and second 270 lobes. The second set of transition regions 240 are coaxial with the first petal 260 and the second petal 270. Although in FIGS. 3A and 6A, the first valve 260, the first set of transition regions 240, and the second valve 270 in the first flow channel are shown and described as coaxial, the present invention is not limited to this. The first lobes 260, the first set of transition regions 240, and/or the second lobes 270 in a common flow channel may deviate from each other and the longitudinal axis L3. Although in FIGS. 3A and 6A, the first petal 260, the second set of transition regions 240, and the second petal 270 in the second flow channel are shown and described as coaxial, the present invention is not limited to this, because the first The first lobes 260, the second set of transition regions 240, and/or the second lobes 270 in the two common flow channels may be offset from each other and the longitudinal axis L4. For example, the heat transfer sheet 200' of FIG. 6B illustrates that the first petal 260' and the second petal 270' in the first common flow channel deviate perpendicularly to the longitudinal axis L3, and the transition region 240' connects the first petal 260' is angularly offset from the longitudinal axis L3 with the second petal 270', and a portion of the transition region 240' crosses the longitudinal axis L3. FIG. 6B also illustrates that the first petal 260 and the second petal 270' in the second common flow channel deviate perpendicular to the longitudinal axis L4, and the transition region 240' connects the first petal 260' and the second petal 270' and forms It is angularly offset from the longitudinal axis L4, and a portion of the transition zone 240' crosses the longitudinal axis L4. As shown in FIG. 6B, the first common flow channel has a width D100, and the first petal 260', the first set of transition regions 240', and the second petal 270' are within a width D101' that is less than or equal to the width D100. As shown in FIG. 6B, the second common flow channel has a width D100, and the first petal 260', the second set of transition regions 240', and the second petal 270' are within a width D101' that is less than or equal to the width D100. The heat transfer sheet 200" of FIG. 6C illustrates that the first petal 260", the first set of transition regions 240" and the second petal 270" in the first common flow channel are angularly offset from the longitudinal axis L3, and A part of them crosses the longitudinal axis L3; and the first petal 260", the second set of transition regions 240" and the second petal 270" in the second common flow channel are angularly offset from the longitudinal axis L4, and they are equal One part crosses the longitudinal axis L4. FIG. 6C also illustrates: each of the first set of transition regions 240" connects adjacent first petals 260" and second petals 270" to each other in the first flow channel; and the second set of transition regions 240 Each of'' connects the first petal 260'' and the second petal 270'' to each other in the second flow channel. As shown in FIG. 6C, the first common flow channel has a width D100, and the first valve 260", the first set of transition regions 240" and the second valve 270" in the first common flow channel are smaller than or Within the width D101" which is equal to the width D100. As shown in FIG. 6C, the second common flow channel has a width D100, and the first valve 260", the second set of transition regions 240" and the second valve 270" in the second common flow channel are smaller than or Within the width D101" which is equal to the width D100. The heat transfer sheets 100 and 200 can be made of metal sheets or plates of predetermined sizes such as the length, width, and thickness of the preheater 10 used and suitable for making the preheater 10 that meets the required requirements of the factory in which it will be installed. In one embodiment, the heat transfer sheet is manufactured in a single-roll manufacturing process using a single set of crimping rolls having the necessary profile to provide the configuration disclosed herein. In one embodiment, the heat transfer fins 100 and 200 are coated with a suitable coating (such as enamel), which makes the heat transfer fins 100 and 200 slightly thicker and also prevents direct contact between the metal sheet substrate and the flue gas. contact. These coatings prevent or reduce corrosion caused by soot, ash, or condensable vapor that the heat transfer fins 100 and 200 are exposed to during operation in the preheater 10. 2A and 3A, the heat transfer surface 310 is defined by an undulating surface that is angularly offset from the longitudinal axis L. For example, the undulating surface of row F deviates from the vertical axis by an angle θ; and the undulating surface of row G deviates from the longitudinal axis by an angle δ. In one embodiment, the angle θ is equal to the angle δ and extends in the opposite direction from the longitudinal axis L. In one embodiment, the angle θ and the angle δ are between 45 degrees and minus 45 degrees measured relative to the longitudinal axis and/or groove configuration 110 or 210. In one embodiment, the heat transfer surface 310 includes a flat portion. In one embodiment, the undulating surface has undulating peaks 310P spaced apart from each other by a distance 310D in the range of 0.35 to 0.85 inches. In one embodiment, the height H1 is 0.050 to 0.40 inches, where the height H1 does not include the thickness of the heat transfer sheet 100 or 200. In one embodiment, the undulating surface 310 has a ratio of the pitch distance 310D between the undulating peaks 310P of 3.0:1 to 15.0:1 and the height H1 (not including the thickness of the heat transfer sheet). In one embodiment, the heat transfer sheets 100 and 200 have a groove height H2 (excluding the thickness of the heat transfer sheet) and a height H1 (excluding the thickness of the heat transfer sheet) of the groove from 1.0:1.0 to 4.0:1.0 One ratio. In one embodiment, the height H2 is 0.15 to 0.50 inches, which does not include the thickness of the heat transfer sheet. As shown in FIGS. 4A and 4B, two heat transfer sheets 100 are stacked on top of each other to form a part of the heat transfer assembly 1000. The peak 160LP of one of the first petals 160L of the heat transfer sheet 100' engages a part of the heat transfer surface 310 of the heat transfer sheet 100; and the valley 170RV of one of the second petals 170R of the heat transfer sheet 100 engages heat The heat transfer surface 310 of the transfer sheet 100'. Although two heat transfer fins 100 are shown and described, any number of heat transfer fins 100 and/or 200 may be stacked on top of each other to form a heat transfer assembly 1000. The heat transfer fins 100 and 200 and the assembly 1000 are generally described herein as a bisecting air preheater. However, the present invention includes configurations and stacks of various heat transfer fins 100 and 200 for other air preheater configurations (such as but not limited to a three-part or four-part air preheater). As shown in FIG. 2D, another embodiment of the heat transfer sheet is generally designated by the number 400. The heat transfer sheet 400 is similar to the heat transfer sheet 100 of FIG. 2A. Therefore, similar components are designated with similar component symbols, but the first digit "1" is replaced by the number "4". The difference between the heat transfer sheet 400 and the heat transfer sheet 100 is that the heat transfer sheet 400 does not have a groove configuration 110. Therefore, the heat transfer sheet 400 includes a plurality of rows (for example, two rows F and G are illustrated in FIG. 2D) of heat transfer surfaces 410. The rows F and G of the heat transfer surface 410 are parallel to the flow of flue gas and combustion air (as indicated by arrows A and B, respectively) at a first end 400X and a second end of the heat transfer sheet 400 A longitudinal axis L extending between 400Y is aligned. The heat transfer surface 410 has a first height H1 relative to a center plane CP of the heat transfer sheet 100, as shown in FIG. 2D. In one embodiment, the heat transfer surface 410 is defined by an undulating surface that is angularly offset from the longitudinal axis L. The undulating surface 410 is configured similar to the undulating surface 310 described herein. For example, the undulating surface 410 of the row F deviates from the longitudinal axis at an angle θ; and the undulating surface 410 of the row G deviates from the longitudinal axis at an angle δ. In one embodiment, the angle θ and the angle δ are equal and extend in the opposite direction from the longitudinal axis L. In one embodiment, the angle θ and the angle δ are between 45 degrees and minus 45 degrees measured with respect to the vertical axis. As shown in FIG. 2D, the undulating surface 410 of row F and the undulating surface 410 of row G merge with each other along a longitudinal axis M. As shown in FIGS. 2E and 7A, another embodiment of the heat transfer sheet is generally designated by the number 500. The heat transfer sheet 500 is similar to the heat transfer sheet 100 of FIG. 2A. Therefore, similar components are designated with similar component symbols, but the first number "1" is replaced by the number "5". The heat transfer sheet 500 is different from the heat transfer sheet 100 in that the heat transfer sheet 400 does not have an oblique undulating surface similar to the undulating surface 310 illustrated in FIG. 2A and is a separate heat transfer sheet. Therefore, the heat transfer sheet 500 includes a groove configuration 110 similar to the groove configuration 110 described above with reference to FIG. 2A (staggered full groove configuration) and/or the groove configuration 210 described herein with reference to FIG. 3A (e.g. Half groove configuration) a plurality of groove configurations 510 positioned in a side-by-side configuration. Therefore, the groove configurations 510 merge with each other in a direction transverse to (for example, perpendicular to) the longitudinal axis L. The transition regions 540L and 540R are shown longitudinally aligned with each other (ie, in a side-by-side configuration), however, in another embodiment, the transition regions 540L and 540R are longitudinally offset from each other (eg, staggered along the longitudinal axes L1 and L2, respectively ). In one embodiment, the heat transfer sheet 500' of FIG. 7B is configured similarly to the heat transfer sheet 100' of FIG. 5B. In one embodiment, the heat transfer sheet 500" of FIG. 7C is configured similarly to the heat transfer sheet 100" of FIG. 5C. As shown in FIGS. 4C and 4D, a heat transfer assembly 1000' is shown, in which one of the heat transfer fins 400 is positioned between the two of the heat transfer fins 500 and 500' and engages the heat transfer fins 500 and Two of 500'. One or more portions of the groove configuration 510 engage the undulating surface 410 in the row F (FIG. 2D) and/or a portion of the undulating surface 410 in the row G (FIG. 2D) to separate the heat transfer sheets 400 from each other and define Flow path P'. For example, as shown in FIG. 4D: 1) the valley 570RV of the petal 570R engages the part of the undulating surface 410 (for example, the undulating peak 410P); 2) the valley 570LV of the petal 570L engages the part of the undulating surface 410 (for example, the undulating peak 410P); 3) the peak 560LP of the petal 560L engages a portion of the undulating surface 410 (eg, undulating peak 410P); and 4) the undulating peak 560RP of the petal 560R engages a portion of the undulating surface 410 (eg, the undulating peak 410P). The following examples quantify the characteristics of exemplary embodiments of heat transfer fins 100 and 200 that the inventors have surprisingly found to provide the desired and improved heat transfer efficiency compared to prior art heat transfer fins. Example 1 As shown in Figure 2A, the continuous transition regions 140L aligned along the longitudinal axis L1 are spaced apart from each other by a longitudinal distance L6 of 2 to 8 inches; and/or the continuous transition regions 140R aligned along the longitudinal axis L2 They are separated by a longitudinal distance L6 of 2 to 8 inches. Similarly, as shown in FIG. 3A, continuous transition regions 240 aligned along the longitudinal axis L3 are spaced apart from each other by a longitudinal distance L7 of 2 to 8 inches; and/or continuous transition regions aligned along the longitudinal axis L4 The 240 are separated from each other by a longitudinal distance L7 of 2 to 8 inches. Example 2 As shown in FIG. 2C, the transition zone 140L and/or 140R of the heat transfer sheet 100 has a longitudinal distance L5 of 0.25 to 2.5 inches. As shown in FIG. 3B, the transition area 240 of the heat transfer sheet 200 has a longitudinal distance L5 of 0.25 to 2.5 inches. Example 3 is shown in FIG. 2A, the adjacent groove configurations 110 are spaced apart from each other by a distance L8 of 1.25 to 6 inches measured in a direction perpendicular to the longitudinal axis L of the heat transfer sheet 100. As shown in FIG. 3A, the adjacent groove configurations 210 are spaced apart from each other by a distance L8 measured in a direction perpendicular to the longitudinal axis L of the heat transfer sheet 200 from 1.25 to 6 inches. Example 4 is shown in FIG. 2A, the groove configuration 110 defines the longitudinal distance L6 between the continuous transition zone 140L or 140R from 5:1 to 20:1 and the height H2 of the groove configuration 110 (excluding the heat transfer sheet The thickness) is a ratio. The groove configuration 210 defines a ratio of the longitudinal distance L7 between the continuous transition regions 240 of 5:1 to 20:1 and the height H2 of the groove configuration 210 (not including the thickness of the heat transfer sheet). Although the present invention has been disclosed and described with reference to the specific embodiments of the present invention, it should be noted that other changes and modifications can be made, and it is expected that the following patent applications cover such changes and modifications within the true scope of the present invention.

3F/3G-3F/3G‧‧‧line 10‧‧‧rotating regeneration air preheater/preheater 12‧‧‧rotor assembly 14‧‧‧housing 16‧‧‧rotor column 18‧‧‧partition 20 ‧‧‧Compartment 22‧‧‧flue gas inlet pipe 24‧‧‧flue gas outlet pipe 26‧‧‧air inlet pipe 28‧‧‧air outlet pipe 30A‧‧‧upper sector plate 30B‧‧‧lower sector Plate 30C‧‧‧Circumferential plate 32‧‧‧Air sector 34‧‧‧Gas sector 36‧‧‧flue gas stream/flue gas 38‧‧‧combustion air stream/combustion air 100‧‧‧heat Transfer piece 100'‧‧‧Heat transfer piece 100``‧‧‧Heat transfer piece 100X‧‧‧First end 100Y‧‧‧Second end 110‧‧‧Groove configuration 112‧‧‧First side 114‧ ‧‧Second side 140L‧‧‧First transition zone/Transition zone/Continuous transition zone 140L'‧‧‧First transition zone/Transition zone 140L''‧‧‧First transition zone/Transition zone 140R‧‧‧第Second transition zone / transition zone / continuous transition zone 140R'‧‧‧ second transition zone / transition zone 140R''‧‧‧ second transition zone / transition zone 141L‧‧‧ transition surface 141R‧‧‧ transition surface 143R‧‧ ‧Bow-shaped part 145L‧‧‧Bow-shaped part 145R‧‧‧Bow-shaped part 160L‧‧‧First part 160L'‧‧First part 160L''‧‧‧First part 160LP‧‧‧Peak 160R‧‧‧First part 160R'‧‧‧First 160R''‧‧‧First 160RP‧‧‧Peak 170L‧‧‧Second 170L'‧‧Second 170L''‧‧‧Second 170LV‧‧ ‧Valley 170R‧‧‧Second segment 170R'‧‧‧Second segment 170R``‧‧‧Second segment 170RV‧‧‧ Valley 200‧‧‧Heat transfer sheet 200'‧‧‧Heat transfer sheet 200''‧ ‧‧Heat transfer sheet 200Y‧‧‧Second end 210‧‧‧Groove configuration 212‧‧‧First side 214‧‧‧Second side 240‧‧‧Transition zone/continuous transition zone 240'‧‧‧Transition Zone 240''‧‧‧Transition zone 241‧‧‧Transition surface 241'‧‧‧Transition point 241T‧‧‧Straight section/Extended straight section 243‧‧‧Bow-shaped part 243'‧‧‧Flat or straight part /Straight section 245‧‧‧Bow section 245'‧‧‧Flat or straight section/Straight section 260‧‧‧The first petal/the first petal 260'‧‧ The first petal 260``‧‧‧The first petal 260P ‧‧‧Peak 270‧‧‧Second lobe/lobe 270'‧‧‧Second lobe 270``‧‧‧Second lobe 270V‧‧‧Valley 310‧‧‧Heat transfer surface / undulating surface 310D‧‧‧Distance 310P‧‧‧Ramp peak 400‧‧‧Heat transfer sheet 400X‧‧‧First end 400Y‧‧‧Second end 410‧‧‧Heat transfer surface/Rave surface 410P‧‧‧Ramp peak 500‧‧‧Heat transfer sheet 500'‧‧‧Heat Transfer Film 5 00``‧‧‧Heat transfer film 510‧‧‧Groove configuration 540L‧‧‧Transition zone 540R‧‧‧Transition zone 560RP‧‧‧Rolling peak 570L‧‧‧Petal 570LV‧‧‧Valley 570R‧‧‧Val 570RV‧‧‧Valley 1000‧‧‧Heat transfer assembly/heated heat transfer assembly/Assembly 1000'‧‧‧Heat transfer assembly A‧‧‧Shaft/arrow B‧‧‧arrow F‧‧‧column G ‧‧‧Row R‧‧‧Arrow θ‧‧‧Angle δ‧‧‧Angle P‧‧‧Flow Path P'‧‧‧Flow Path CP‧‧‧Center Plane L‧‧‧Vertical Axis/Axis L1‧‧‧ First vertical axis/longitudinal axis/axis L2‧‧‧second vertical axis/longitudinal axis/axis L3‧‧‧longitudinal axis/axis L4‧‧‧longitudinal axis L5‧‧‧length/predetermined length/longitudinal distance L6‧‧ ‧Length/Longitudinal distance L7‧‧‧Longitudinal distance L8‧‧‧Distance L100‧‧‧Longitudinal boundary line/boundary line L200‧‧‧Longitudinal boundary line/boundary line D100‧‧‧Width D101‧‧‧Width D101'‧‧ ‧Width D101``‧‧‧Width H1‧‧‧First height/height H2‧‧‧Second height/height H3‧‧‧Third height

Fig. 1 is a schematic perspective view of a rotary regenerative preheater; Fig. 2A is a perspective view of a heat transfer sheet according to an embodiment of the present invention; Fig. 2B is an enlarged view of a part of the heat transfer sheet of Fig. 2A Figures; Figure 2C is an enlarged view of part C of a detail of the heat transfer sheet of Figure 2A; Figure 2D is a perspective view of another embodiment of the heat transfer sheet according to the present invention; Figure 2E is the heat transfer spacer of the present invention A perspective view of another embodiment of the sheet; Fig. 2F is an enlarged view of a part of the heat transfer sheet of Fig. 2A illustrating another embodiment; Fig. 3A is a heat transfer according to another embodiment of the present invention A perspective view of a sheet; Fig. 3B is an enlarged view of part B of a detail of the heat transfer sheet of Fig. 3A; Fig. 3C is a cross section of a part of the heat transfer sheet of Fig. 3B taken across the line 3C/3D-3C/3D Fig. 3D is a cross-sectional view of another embodiment of a part of the heat transfer sheet of Fig. 3B taken across 3C/3D-3C/3D; Fig. 3E is a schematic view of another embodiment of the heat transfer sheet of Fig. 3A A detail of an enlarged view of part B; Figure 3F is a schematic diagram of a section of a part of the heat transfer sheet of Figure 3B taken across the line 3F/3G-3F/3G; Figure 3G is a cross-sectional view of a part of the heat transfer sheet taken across the line 3F/3G-3F/3G A schematic cross-sectional view of another embodiment of a part of the heat transfer sheet in FIG. 3B; FIG. 4A is a photo of one of the two heat transfer sheets stacked on top of each other in FIG. 2A; FIG. 4B is the heat transfer assembly in FIG. 4A Fig. 4C is an end view of a stack of heat transfer fins of Figs. 2D and 2E; Fig. 4D is a side sectional view of a stack of heat transfer fins of Figs. 2D and 2E; 5A is a schematic top view of one of the heat transfer fins of FIG. 2A; FIG. 5B is a schematic top view of another embodiment of the heat transfer fins of FIG. 2A; FIG. 5C is one of another embodiment of the heat transfer fins of FIG. 2A Schematic plan view; Fig. 6A is a schematic plan view of one of the heat transfer fins of Fig. 3A; Fig. 6B is a schematic plan view of another embodiment of the heat transfer fins of Fig. 3A; Fig. 6C is another schematic plan view of the heat transfer fins of Fig. 3A A schematic top view of one embodiment; FIG. 7A is a schematic top view of the heat transfer sheet of FIG. 2E; FIG. 7B is a schematic top view of another embodiment of the heat transfer sheet of FIG. 2E; and FIG. 7C is FIG. 2E A schematic top view of another embodiment of the heat transfer sheet.

100‧‧‧Heat Transfer Film

100X‧‧‧First end

100Y‧‧‧Second end

110‧‧‧Groove configuration

112‧‧‧The first side

114‧‧‧Second Side

140L‧‧‧Transition zone/First transition zone/Continuous transition zone

140R‧‧‧Transition zone/Second transition zone/Continuous transition zone

160L‧‧‧First petal

160R‧‧‧First petal

170L‧‧‧Second petal

170R‧‧‧Second petal

310‧‧‧Heat transfer surface / undulating surface

310P‧‧‧Heave Peak

A‧‧‧Axis/Arrow

B‧‧‧Arrow

F‧‧‧Column

G‧‧‧ column

θ‧‧‧angle

δ‧‧‧angle

CP‧‧‧Center Plan

L‧‧‧Vertical axis/axis

L1‧‧‧Vertical axis/first longitudinal axis/axis

L2‧‧‧Vertical axis/second longitudinal axis/axis

L6‧‧‧Length/Longitudinal distance

L8‧‧‧Distance

Claims (14)

A heat transfer fin (100) for a rotary regenerative heat exchanger (10). The heat transfer fin (100) includes a plurality of rows (F, G) and heat transfer surfaces (310), the plurality of rows (F, G) ) Are aligned with a longitudinal axis (L) that extends parallel to the expected flow direction (A, B) between a first end (100X) and a second end (100Y) of the heat transfer sheet , The heat transfer surfaces (310) have a first height (H1) relative to a center plane (CP) of the heat transfer sheet (100); and at least one groove configuration (110, 210), which is used to make the The heat transfer sheets (100) are separated from each other, the at least one groove configuration (110, 210) is positioned between the heat transfer surfaces of the plurality of rows (F, G) of the heat transfer surfaces (310), the groove The configuration (110, 210) includes: at least one first lobe (160L, 160R, 260) extending away from the central plane (CP) in a first direction; at least one second lobe (170R, 170L, 270) A second direction opposite to the first direction extends away from the center plane (CP); and one of the at least one first lobe (160L, 160R, 260) and the at least one second lobe (170R, 170L, 270) Either or both have a second height (H2) relative to the central plane (CP), the second height is greater than the first height, wherein the at least one first petal (160L, 160R, 260) and the at least A second petal (170R, 170L, 270) is connected to each other in a longitudinally staggered pattern and is in a common flow channel such that the at least one first petal (160L, 160R, 260) is longitudinally adjacent to the at least one second petal ( 170R, 170L, 270). The heat transfer sheet of claim 1, wherein the heat transfer surfaces include undulating surfaces angularly deviated from the longitudinal axis. Such as the heat transfer sheet of claim 1, which further includes a flow diversion configuration defined by a transition region that longitudinally connects the at least one first lobe and the at least one second lobe. Such as the heat transfer sheet of claim 3, wherein the transition area includes an arcuate shape. Such as the heat transfer sheet of claim 3, wherein the transition zone includes a flat section. Such as the heat transfer sheet of claim 3, wherein the transition area includes a flat section parallel to the central plane. Such as the heat transfer sheet of claim 3, wherein the transition zone includes a flow stagnation mitigation path. The heat transfer sheet of claim 1, wherein the at least one first lobe and the at least one second lobe are coaxial with each other along an axis parallel to the longitudinal axis. The heat transfer sheet of claim 1, wherein the at least one first lobe and the at least one second lobe are adjacent to each other in a direction transverse to the longitudinal axis. The heat transfer sheet of claim 1, wherein at least one of the at least one first lobe and the at least one second lobe is angularly offset from each other. A heat transfer assembly (1000) for a rotary regenerative heat exchanger (10), the heat transfer assembly comprising: at least two heat transfer fins (100) stacked on top of each other; the at least two heat transfer fins Each of (100) includes: a plurality of rows (F, G) heat transfer surface (310), each of the plurality of rows (F, G) is parallel to passing through the heat transfer assembly (1000) The expected flow direction (A, B) is aligned with a longitudinal axis (L) extending between a first end and a second end of the heat transfer assembly (1000), and the heat transfer surfaces (310) are opposite A central plane (CP) of the heat transfer sheet (100) has a first height (H1); at least one groove configuration (110, 210) is used to separate the heat transfer sheets (100) from each other, The at least one groove configuration (110, 210) is positioned between adjacent rows of heat transfer surfaces in the plurality of rows (F, G) of heat transfer surfaces, and the groove configuration (110, 210) includes: at least one first lobe (160L) ,160R,260), which extends away from the central plane (CP) in a first direction; at least one second petal (170R, 170L, 270), which extends away from the first direction in a second direction opposite to the first direction Central plane (CP); the at least one first petal (160L, 160R, 260) and the at least one second petal (170R, 170L, 270) either or both have relative to the central plane (CP) A second height (H2), the second height (H2) is greater than the first height (H1); and the at least one first lobe (160L) of the first one of the at least two heat transfer fins (100) ,160R,260) engage the heat transfer surface (310) of the second one of the at least two heat transfer sheets (100), and the second one of the at least two heat transfer sheets (100) At least one second flap (170R, 170L, 270) engages the first of the at least two heat transfer plates (100) A heat transfer surface (310) to define a flow path between the at least two heat transfer fins (100), the flow path extending between the first end (100X) and the second end (100Y); and It is characterized in that the at least one first petal (160L, 160R, 260) and the at least one second petal (170R, 170L, 270) are connected to each other in a longitudinal staggered pattern and are in a common flow channel, so that the at least one The first petal (160L, 160R, 260) is longitudinally adjacent to the at least one second petal (170R, 170L, 270). For example, the heat transfer assembly of claim 11, which further includes a flow turning configuration defined by a transition region that longitudinally connects the at least one first lobe and the at least one second lobe. A stack of heat exchanger fins, the stack comprising: at least one first heat transfer fin (100), including: a first undulating surface extending along the first heat transfer fin (100) and opposite to passing through the A flow direction of the stack is oriented at a first angle, and a second undulating surface extending along the first heat transfer sheet (100) and oriented at a second angle with respect to the flow direction through the stack, The first angle is different from the second angle; and at least one second heat transfer sheet (100), which defines a plurality of groove configurations (110, 210), the plurality of groove configurations are parallel to the expected flow The direction (A, B) extends between a first end (100X) and a second end (100Y) of the at least one second heat transfer sheet (100), and a longitudinal axis (L) extends for making The at least one first heat transfer sheet (100) is separated from an adjacent one of the at least one second heat transfer sheet (100), and the at least one groove configuration (110, 210) includes: at least one first petal (160L) ,160R,260), which extends along a first direction away from the One less second heat transfer sheet has a central plane (CP); at least one second petal (170R, 170L, 270) extends away from the central plane (CP) in a second direction opposite to the first direction; The at least one first petal (160L, 160R, 260) engages a portion of at least one of the first undulating surface and the second undulating surface; the at least one second petal (170R, 170L, 270) engages the first A portion of at least one of the undulating surface and the second undulating surface to define a flow path between the at least one first heat transfer sheet (100) and the at least one second heat transfer sheet (100); and It is characterized in that the at least one first petal (160L, 160R, 260) and the at least one second petal (170R, 170L, 270) are connected to each other in a longitudinal staggered pattern and are in a common flow channel, so that the at least one first petal One petal (160L, 160R, 260) is longitudinally adjacent to the at least one second petal (170R, 170L, 270). A spacer for stacking a heat transfer sheet (100), the spacer includes: a plurality of groove configurations (110, 210), which are parallel to the expected flow direction (A, B) on one of the spacers A longitudinal axis (L) extends between one end and a second end to separate the adjacent heat transfer plates (100) from each other. The groove configurations (110, 210) include: at least one first lobe (160L) ,160R,260), which extends along a first direction away from a central plane (CP) of the at least one second heat transfer sheet (100); at least one second petal (170R, 170L, 270), which extends along with the A second direction opposite to the first direction extends away from the central plane (CP); and is characterized in that the at least one first lobe (160L, 160R, 260) and the at least one second lobe (170R, 170L, 270) are Connected to each other in a longitudinal staggered pattern and in a common flow In the channel, the at least one first lobe (160L, 160R, 260) is longitudinally adjacent to the at least one second lobe (170R, 170L, 270).

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