JP2013533041A - User retention system, apparatus, and method - Google Patents

Abstract

This PCT application brings together five separate US applications into a single application consisting of parts AE. Part A relates to a bed structure with a deck section transfer converter. Part B relates to a method and system for controlling the evaporation and heat recovery performance of a user-carrying surface. Part C relates to the bed sensor described above. Part D relates to a user holding device. Part E relates to a side rail whose height can be changed.

Description

Cross-reference to related applications. This application is filed in U.S. Application Nos. 12 / 833,321 (filed July 9, 2010), 12 / 836,606 (filed July 15, 2010), 12 / 847,337. Claiming priority of No. (filed July 30, 2010), 61 / 369,499 (filed July 30, 2010), and 61 / 369,152 (filed July 30, 2010), Which are incorporated herein by reference in their entirety.

Part A
The subject matter described herein is an articulatable retainer such as a hospital bed, in particular a deck frame, a deck panel connected to the frame, and a movement that matches the translational movement of the panel with the rotation and / or longitudinal movement of the frame. The present invention relates to a cage having a converter.

Part B
The subject matter described herein relates to a user holding surface, such as a hospital bed mattress with microclimate management capabilities, and a method and system for controlling the evaporation and heat recovery performance of the holding surface.

Part A
Pending US Patent Application No. 12 / 618,256, filed November 13, 2009, entitled “Anthropometrically Controlled User Retainer” describes an articulatable retainer such as a hospital bed. This articulation is at least partially dependent on anthropometry. The contents of application 12 / 618,256 are incorporated herein by reference. The present application discloses a mode of operation in which the rotation of the upper body section of the bed involves a longitudinal movement of the upper body part and a “translation” of the upper body deck panel. In this application, translation is defined as the movement of the deck panel in a direction parallel to the existing angular direction of the upper body section.

Part B
The hospital bed can include a holding surface with microclimate management (MCM) functionality. The MCM function refers to a function that affects the environment in the immediate vicinity of the bed user, particularly temperature and humidity. The MCM capable holding surface can be a topper installed on the mattress or the mattress itself. Effective microclimate management can benefit bed users by resisting or mitigating the effects of skin tissue destruction.

Part A
The teachings of previous applications are presented in the context of a bed with three actuators for controlling the movement of the upper body section. One of these actuators controls the translation. The other two rotate the upper body section at the same time as moving it vertically, rotating the upper body section without giving it a vertical movement, or moving the upper body section vertically without giving it a rotation. To be operated. Such systems may be desirable with prototype or experimental beds to allow maximum flexibility of articulation during testing or development, but beds produced for commercial sale are included in the upper body section It is envisioned that fewer actuators will be used. Thus, the application also describes a simplified kinematic configuration bed with a single upper body section actuator and dual rack and pinion. In operation, the actuator extends or retracts to move its upper body section longitudinally while changing its angular orientation. At the same time, the double rack and pinion causes the desired translation of the upper body deck panel in response to the movement and orientation of the upper body section.
Despite the benefits of simplified kinematics and double rack and pinion described in previous applications, applicants continue to pursue further innovations that can lead to improved performance, increased reliability and reduced cost. .

Part B
A typical MCM-capable holding surface provides airflow acceptance and release. At least that portion of the holding surface on which the user rests is vapor permeable. In operation, the airflow flows through the interior of the holding surface. Provided that the air is cooler than the user's skin, the internal airflow acts as a heat sink to keep the user's skin cool, thereby reducing the metabolic demands of the skin tissue and, as a result, the user Reduce the chance of developing pressure sores (bed sores). This mode of heat transfer is proportional to the temperature gradient between the user's skin and airflow (dq _DRY / dt = k ₁ ΔT), hereinafter referred to as “dry flux” DF.

In addition, heat transfer from the user's skin gains enough energy for the sweat molecules present at the interface between the holding surface and the user's skin to be free from liquid sweat (ie, evaporate). Yes. The liberated molecules travel through the vapor permeable portion of the user cage and are carried away by the internal airflow. Given that the skin is not excessively dry, reducing the associated humidity at the skin / surface interface is beneficial because dry skin is less susceptible to tissue damage than wet skin. Furthermore, since evaporation is the result of heat transfer from the user, the user experiences an evaporative cooling effect in addition to the dry flux described above. This evaporation mode of heat transfer consists of P _{2 O, SKIN,} which is the partial pressure of water vapor (sweat) in the user's skin (ie, at the user / surface interface) _, and P _, which is the partial pressure of water vapor in the air stream. _It is proportional to the difference between _{H2O and STREAM} (dq _WET / dt = k ₂ ΔP _H2O ) and is referred to herein as “wet flux” WF. The heat transfer wet flux element appears only when the user is sweating and depositing liquid-phase sweat on the skin / surface interface.

  Typically, the airflow through the MCM capable surface is ambient air (eg, air from a hospital room), in addition to the adjustments made by the hospital heating, ventilation and air conditioning (HVAC) system, the temperature and / or air Or it is unregulated in the sense that humidity control is not added. As a result, the effectiveness of the MCM-capable holding surface is limited by the indoor air characteristics. What is needed is to selectively achieve improved microclimatic characteristics and performance and control the degree of improvement.

Part A
The bed structure includes a frame, a deck frame movably connected to the frame, a panel movably connected to the deck frame, and a movement converter. The movement converter moves the panel relative to the deck frame in response to one or both of a) relative translation between the deck frame and frame, and b) relative rotation of the deck frame and frame. In one detailed embodiment, the mobile converter is separated from a rack fixed to the frame, a primary gear meshing with the rack, a panel driven sprocket mounted coaxially with the primary gear and rotated on the deck framework, and the panel driven sprocket. And an idler sprocket rotatably mounted on the deck framework, a slider connected to the panel, and a chain connected to the slider in conjunction with the panel drive sprocket and idler.
The foregoing and other features of the user retainer described herein will become more apparent from the following detailed description and the accompanying drawings.

Part B
A method for controlling the performance of an MCM-capable holding surface with a flow path that guides airflow along at least a portion of the surface identifies a desired evaporation performance that is superior to that achieved with unregulated ambient air Cooling unregulated ambient air to a temperature that is at least as low as that required to achieve 100% relative humidity, thereby dehumidifying the air and supplying the cooled and dehumidified air to the flow path Including doing. The method may also include heating the cooled and dehumidified air before supplying it to the flow path.
The foregoing and other features of various embodiments of the systems and methods for improving and controlling the microclimate performance of a retention surface described herein will become more apparent in the following detailed description and accompanying drawings.

1 is a schematic side view of a bed of the type used in hospitals and other medical facilities. FIG. 1 is a perspective view of a bed structure as described herein having a frame and an upper body deck section, the deck section being shown in a horizontal angular orientation relative to the frame. FIG. FIG. 2B is a view similar to FIG. 2A but with the deck section at an angle of about 65 degrees relative to the frame. In particular, the portion of FIG. 3A showing the gear rack, the split gear housing positioned at one end of the gear rack, and the legs of the deck section, with the deck section rail cut away to show the chain and the chain housing within the rail. FIG. FIG. 4B is an illustration of the gear rack shown in FIG. 4A, with the gear rack slide rail components cut away, with the gear housing at the other end of the gear rack, and one of the elements such as the deck section and the split gear housing. One side has been removed. It is sectional drawing of the 6-6 direction of FIG. 2A. It is an exploded view which shows the component of a bed structure. It is an exploded view which shows the component of a bed structure. FIG. 5 is a perspective view showing components such as sprockets, drive chains, and sliders with selected components removed or cut away. FIG. 5 is a perspective view showing components such as sprockets, drive chains, and sliders with selected components removed or cut away. FIG. 10B is a cross-sectional view in the direction 11--11 of FIG. 10A showing the slider of FIGS. 9A-10A with respect to the rail portion, chain housing, and deck panel drive lug of the upper body deck section. FIG. 10 is a perspective view showing a second slider with respect to the rail portion of the upper body deck section and the deck panel drive lug. It is a side view of a lift chain. It is a schematic side view of the bed structure which has a non-movable joint between a compression link and the bed raiseable frame. FIG. 14B is a view similar to FIG. 14A showing the results of various modes of movement in an embodiment in which the joint between the compression link and the raiseable frame can move vertically. FIG. 14B is a view similar to FIG. 14A showing the results of various modes of movement in an embodiment in which the joint between the compression link and the raiseable frame can move vertically. FIG. 14B is a view similar to FIG. 14A showing the results of various modes of movement in an embodiment in which the joint between the compression link and the raiseable frame can move vertically. FIG. 14B is a view similar to FIG. 14A showing the results of various modes of movement in an embodiment in which the joint between the compression link and the raiseable frame can move vertically. FIG. 3 is a schematic side view of a bed having a MCM capable holding surface. It is a figure in direction 2--2 of Drawing 1B. 1 is a schematic diagram of a microclimate management system including a chiller and a water collection system, as disclosed herein. FIG. 3B is a schematic diagram of a microclimate management system similar to that of FIG. 3B, but also including a heater. It is a block diagram of an algorithm for controlling the evaporation capacity of the holding surface. It is a block diagram of an algorithm for controlling the evaporation capacity of the holding surface. FIG. 6 is a graph showing the vapor pressure of water as a function of temperature and including data symbols corresponding to the example numbers described in the specification. FIG. 8 is a view in the direction 7--7 of FIG. 2B showing a nucleation device comprising a number of vertically oriented fibers. FIG. 4 is a user interface diagram illustrating two ways to allow a caregiver to specify the desired performance of a microclimate management system. FIG. 4 is a user interface diagram illustrating two ways to allow a caregiver to specify the desired performance of a microclimate management system.

Part A:
1A-3A show a hospital bed 10 that extends longitudinally from a head end 12 to a foot end 14 and laterally extends from a left side 16 to a right side 18. 1A-2A also show a centerline 22 extending in the longitudinal direction. The bed structure includes a base frame 26 and a liftable frame 28 connected to the base frame by a folding link 30. The bed also includes four deck sections (upper body section 34, seat section 36, thigh section 38, and calf section 40) all connected to an ascendable frame. The upper body deck section 34 includes a framework 50 comprising left and right hollow rails 52, 54 joined together by an upper beam 56 and a lower beam 58. The first and second rail slots 60, 62 extend through the upper end of each rail and extend partway along it. The lower end of each rail also includes a double-sided mounting bracket 64. The framework 50 is movably connected to the ascendable frame 28 so that the framework moves longitudinally relative to the ascendable frame and can also rotate about the pivot axis 70. The deck section 34 also includes a deck panel 72 (shown in dashed lines) movably connected to the framework 50. In particular, the panel 72 is movable with respect to the frame in directions P1 and P2 parallel to the angular direction α of the frame. This translation is the translation referred to in the application summarized in the “Background” section of this application.

  The bed has a pair of compressions each having a frame end 76 pivotally connected to the ascendable frame at the frame joint 78 and a deck end 82 pivotally connected to the deck framework at the deck joint 84. A link 74 is also included. In the embodiment shown in FIGS. 1A-3A, the frame joint 78 is not movable relative to the frame, but in another embodiment (FIG. 15A), the joint 78 is movable longitudinally relative to the frame. is there.

  The bed also includes a drive system that includes an actuator 90 having a deck end 92 connected to the upper body deck framework 50 and a ground end 94 connected to a suitable mechanical ground such as the liftable frame 28. The drive system may move the panel 72 relative to the deck frame in response to at least one of a) relative translation between the deck frame and frame, and b) relative rotation about the axis 70 of the deck frame and frame. Also included is a movement converter (generally indicated by reference numeral 100) for movement. The illustrated embodiment includes both right and left mobile converter units 100L, 100R. Since the units are mirror images of each other, it will be sufficient to describe only one of the units in more detail.

  4A-8A show in more detail one component and structure of the mobile converter. The movement converter includes a gear rack 102 mounted to the ascendable frame 28. Alternatively, the gear rack can be considered part of the raiseable frame. The rack shown in the figure includes a single slide rail 104 screwed to a frame, and a rack plate 106 screwed to a pedestal 108 at each end of the slide rail. The slot 110 extends along the slide rail between the pedestals. The slide rail has lateral inner and outer surfaces 112, 114 that each have a shoulder 116. The rack plate includes an opening 120 for receiving gear teeth. The opening has a shape that matches the shape of the gear teeth.

  The movement converter also includes a primary gear 124 that meshes with the rack plate. The gear has a stub shaft 126 that extends laterally from the bed centerline 22. A pair of lugs 128 protrude laterally from the shaft. The split gear housing 130 has a rectangular shaped opening 132 extending through its base 134, a cavity 136 inside the base, and a tail 138 protruding from the base. The tail fits snugly into the slide rail slot 110 and the opening 132 surrounds and fits snugly around the rack plate 106. The inner plate 140 is in the cavity. Screws 142 extend through bearing plate 144 and backing plate 146 into inner plate 140 and slidably secure the housing to the slide rail by a bearing plate adjacent to rail shoulder 116. The primary gear is rotatably mounted inside the gear housing 130 by inner and outer gear bushes 154, 156 and a laterally extending pivot 158. The pivot axis also extends through the hole 162 to the rail mounting bracket 64 and connects the primary gear to the deck frame. The bearing 164 fits into the hole 162 and surrounds the pivot axis 158.

  With further reference to FIGS. 9A-11A, the motion converter also includes a deck panel rotary drive element, such as a panel drive sprocket 170. The sprocket is adjacent to the gear housing 130 and is present inside the chain housing 172 disposed on the outside thereof. The sprocket is rotatably mounted on the pivot shaft 158 by an outer gear bush 156. The sprocket has a stub shaft 174 that extends laterally toward the bed centerline 22. A notch 176 at the inner tip of the stub shaft couples with the lug 128 on the primary gear stub shaft and rotatably connects the sprocket to the primary gear. The sprocket and primary gear are therefore coaxial and can rotate at the same speed relative to each other. In the illustrated embodiment, the pitch circle diameters of the primary gear and sprocket are 37.0 mm and 42.6 mm, respectively. Therefore, the primary gear and the sprocket exhibit a non-single drive ratio, specifically, the drive ratio is about 1.15.

  Chain housing 172 extends into the hollow interior of the framework (ie, into rail 52). The chain housing includes an inner track or protrusion 182, a shoulder 184, and an elongated slot 186 that coincides with the first slot 60 of the frame rail. The idler sprocket 192 is rotatably mounted at its distal end 194 within the chain housing. Since the chain housing is stationary with respect to the deck frame 50, the idler is considered to be mounted on the frame.

  The slider 200 includes a slide link 202 that is movably held on a housing inner track 182 and a slide block 204 that is bolted to the slide link. The slide link has a protrusion 206 adjacent to the chain housing shoulder 184 to confine the slide link within the chain housing 172. The slide block includes a head portion 208 lying on top of the framework rail 50 on either side of the first rail slot 60 and a neck portion 210 that extends through the rail slot and extends to the slide link. The slider also includes a drive lug 218 protruding from the slide block. The drive lug is connected to the deck panel 72, thereby connecting the slider to the panel.

  Referring to FIG. 12A, the second slider 212 includes a second slide block 214 having a head portion 226 and a neck portion 228. The second slider also includes a holding plate 230. The head portion 226 of the slider block 214 lies on top of the frame rail 52 on either side of the second rail slot 62. The neck portion 228 protrudes through the rail slot 62 and extends to the holding plate. The slide block and presser plate are together so that the side of the presser plate is under the interior of the frame rail 52 on either side of the second rail slot 62 and the slider can slide longitudinally along the length of the slot. Bolted to. The drive lug 218 is connected to the deck panel 72, thereby connecting the slider to the panel.

  The roller chain 220 and the loops 170, 192 around each sprocket mesh with the sprocket teeth. The end of the chain is connected to the opposite end of the slide link 202, thereby connecting the chain to the deck panel 72. As long as the portion of the chain that extends linearly between the sprockets moves in the direction of P1 or P2 during operation of the drive system, the chain is a linear or movable drive element. Other kinematic equivalent devices may be used in place of the roller chain 220. For example, an example lift chain as seen in FIG. 13A can serve as a movable drive element.

  The sprockets 170, 192, the chain 220 and the slider 200 operably connect the primary gear to the deck panel 72.

  In operation, the actuator 90 extends and pushes the frame member beam 58 longitudinally toward the head end 12 of the bed. The compression link 74 rotates clockwise to change the angular direction α of the upper body deck frame. As seen in FIGS. 5A, 8A, 9A and 10A, the longitudinal movement of the framework relative to the raiseable frame causes the primary gear 124 to rotate clockwise. The primary gear drives the panel drive sprocket 170 in the same rotational direction. The sprocket drives a chain acting on the slider 200 to move the deck panel 72 in the direction of P1 with respect to the deck frame 50. The retracting of the actuator reverses the above movement and moves the deck panel in the direction of P2.

  In operation, the kinematic interaction between the gear rack 102 and the primary gear 124 is as a means of converting the relative translation and / or rotation between the deck frame and the liftable frame into the rotational motion of the primary gear 124. To play a role. The kinematic interaction between the sprocket 170 and the chain 220 serves as a means to convert rotational motion into translational motion. The slider 200 and lug 218 serve as a means for transmitting the translational movement of the chain to the panel.

  FIG. 14A is a simplified schematic diagram illustrating the kinematic interaction of the actuator 90, liftable frame 28, deck framework 50 and compression link 74 of the bed structure described above. As described above, the joint 78 does not move with respect to the frame 28. As shown in FIG. 14A, the operation of the actuator 90 causes the deck panel 72 to move in the vertical direction by a distance D with respect to the ascending frame and to rotate about the angle β with respect to the ascending frame. In another embodiment seen in FIG. 15A, the joint 78 is movable longitudinally relative to the frame by movement of the second actuator 222. Depending on how the movements of the actuators 90 and 222 are adjusted, with respect to the ascending frame without any movement (FIG. 15AC) or rotation or movement as in the first embodiment (FIG. 15AD) The deck frame 50 can be moved in the vertical direction with respect to the ascendable frame 28 without rotation of the rotating frame (FIG. 15AB). Inclusion of the second actuator 222 increases complexity but also increases flexibility, which may be desirable. Since the motion converter described herein is responsive to relative motion between the frame and the deck framework and is independent of whether the relative motion is translation, rotation, or a combination thereof, FIGS. 14A and 15A The same applies to both embodiments.

  It is understood that the kinematic equivalents of the various components of the movement converter can be used in place of the components shown in the figures. For example, belts and pulleys can be used in place of chain 220 and sprockets 170, 192, notched or toothed belts and meshing gears can be substituted for chains and sprockets, rollers and high coefficient of friction tracks (To prevent roller slippage) can be substituted for gear 124 and rack 102.

Part B
1B-2B, the bed 20 has a retaining surface 22 with microclimate management (MCM) functionality. The MCM capable holding surface is shown as a topper placed on a mattress that is not MCM capable, but may alternatively be the mattress itself. The holding surface holds the user 24. The retaining surface includes a material layer 26 that borders and at least partially defines the internal fluid flow path 30. A portion 32 of the holding surface is the portion on which the user rests and is vapor permeable. The holding surface includes an air intake port 36 and an air exhaust port 38. In operation, the air stream 40 flows through the flow path and acts as a sink for heat and water vapor. The bed also includes a user interface 42 for accepting user instructions regarding the operation of the microclimate management system (FIGS. 3B, 4B). The user interface shown in the figure includes a keypad 44 for accepting user instructions and a display panel 46 for communicating information to the user. The bed also includes a controller 50 that responds to user instructions to control the microclimate management system. With reference to FIGS. 3B-4B, the microclimate management system includes a chiller 60, a water collection system 62, and in one embodiment a heater 64.

  Before further describing methods and systems for improved microclimate management, it may be beneficial to establish specific definitions and concepts.

Two main mechanisms of heat transfer affect the microclimate. In one mechanism, dry heat transfer is proportional to the temperature difference and is independent of the presence or absence of liquid-phase sweat at the user / surface interface. The potential that the holding surface affects dry heat transfer at a given temperature difference is called its dry flux capacity DFC. The actual dry heat transfer that is actually realized during operation of the system described herein is the actual dry flux DF. Since dry heat transfer is independent of the presence of liquid-phase sweat at the user / surface interface, the actual dry flux DF is equal to the dry flux capacity DFC:
DF = DFC = (1 / R _DRY ) (T _SKIN -T _STREAM ) (1)

Here, _RDRY is a characteristic of the MCM capable surface 22 (particularly the retaining surface portion 32) combined with the state of the airflow 40 (eg, temperature and flow rate) and the proximity of the airflow to the user's skin. Specifically, _RDRY is a system constant that characterizes the resistance to dry heat flow of the holding surface and airflow. The reciprocal 1 / R _DRY has units of power / unit area / temperature, such as watts / meter ² / ° C., for example. A low value of _RDRY corresponds to high heat transfer, and a high value of _RDRY corresponds to low heat transfer. In the example shown below, R _DRY has a value of 0.300 (m ² ° C) / watt.

T _SKIN is the temperature of the user's skin at the user / surface interface. T _SKIN has a temperature unit such as Celsius (° C),
T _STREAM is the temperature of the airflow 40. In this disclosure and in the accompanying object of numbers example, also many practical _{applications, T STREAM} can be approximated as equal to ambient room temperature _{T AMBIENT} room. Such an estimate ignores the effects of temperature changes because the effects of temperature changes on the ambient air are transmitted through the topper. These temperature changes include the temperature changes associated with pressurizing the ambient air in the room to flow through the topper, heat transfer resulting from heat blockage by nearby electronic components, and heat transferred from the user to the airflow, etc. Can be attributed to many factors. T _STREAM has a temperature unit such as Celsius (° C.).

The dry flux capacity DFC and the dry flux DF have units of power per unit area, such as, for example, watts / meter ² .

The value of _RDRY for a given system can be determined experimentally with a “dry plate test”. A dry test plate heated to a test temperature of 36 ° C. (reasonable “standard” human skin temperature based on extensive measurements) is placed on the surface. A known temperature of air flow below 36 ° C will flow along the opposite side of the surface. Despite the cooling effect of the test airflow, energy is supplied to the plate at a rate sufficient to maintain the plate temperature at 36 ° C. These numbers are used in equation (1) (36 ° is used as the value for T _SKIN , the temperature of the test airflow is used as T _STREAM , and is supplied to keep the test plate at a constant temperature of 36 °. The power per unit area of the test plate is used as the value of the dry flux DF). Equation (1) can then be solved for _RDRY .

Moist heat transfer, the second mechanism of heat transfer, is proportional to the difference between the partial pressure of water vapor (sweat) in the user's skin and the partial pressure of water vapor in the airflow 40. The potential ability of the holding surface to affect wet heat transfer is its wet flux capacity WFC. The wet heat transfer actually realized during operation of the system described herein is the actual wet flux WF. When sweat is available for evaporation at the skin / surface interface, the wet flux capacity WFC is realized as an actual wet flux WF. Potential and actual wet heat transfer rates are referred to as wet flux capacity WFC and wet flux WF, respectively, and can be expressed as:
WFC = (1 / R _WET) (P _{H2O, SKIN} -P _{H2O, STREAM} ) (2A)
WF = (1 / R _WET) (P _{H2O, SKIN} -P _{H2O, STREAM} ) (2B)

Here, R _WET is a characteristic of the MCM capable holding surface 22 (particularly the holding surface portion 32) that combines the state of the airflow 40 (eg, temperature and flow rate) and the proximity of the airflow to the user's skin. . Specifically, R _WET is a system constant that characterizes the resistance to evaporative cooling of the holding surface and airflow. The reciprocal, 1 / R _WET, has units of power / unit area / unit pressure, such as watts / meter ² / pascal, for example. Low R _WET value corresponds to a high evaporation heat transfer, high R _WET value corresponds to a low evaporation heat transfer. In the example shown below, R _WET has a value of 250 (m ² Pa) / watt.

P _{H2O, SKIN} is the partial pressure of water vapor in the user's skin (ie, the user / surface contact surface), P _{H2O, SKIN} has a unit of pressure such as Pascal (Pa),
PH _{2 O, STREAM} is the partial pressure of water vapor in the airflow 40. If T _STREAM is estimated to be equal to T _AMBIENT , it can be estimated that PH _{2 O, STREAM} is equal to the partial pressure of water vapor at room ambient room temperature. PH _{2 O, STREAM} has a unit of pressure such as Pascal (Pa).

  The right side of equations 2A and 2B are identical in form, but equation 2A applies without limitation because it describes the potential or capacity of the system. The applicability of Equation 2B accounts for the actual wet heat transfer that is realized only when liquid sweat is available for evaporation, so it is limited to conditions when liquid sweat is deposited on the user / surface interface Is done.

The wet flux capacity WFC and the wet flux WF have units of power / unit area, such as watts / meter ² , for example.

The value of R _WET for a given system can be determined experimentally with a “wet plate test”. First, the dry plate test is performed as described above. The test is then repeated while supplying water directed to the plate to ensure that the entire test plate remains wet throughout the test. Despite the combined effect of evaporative cooling due to dry heat transfer and test airflow, energy is delivered to the plate at a rate sufficient to maintain the plate temperature at 36 ° C. Next, the appropriate numerical value obtained from the test is substituted into the equation (2A or 2B). The value used for WF (or WFC) is the difference between the power supplied to the test plate during the test wet phase and the power supplied during the test dry phase. Since liquid moisture is present at the plate / surface interface during the test, the value used for PH _{2 O, SKIN} is 5946 Pa, which is the fraction of water vapor at 36 ° C. and 100% relative humidity (ie, saturation pressure). Pressure. PH _{2 O, STREAM} is determined by multiplying the measured relative humidity of the ambient air in the room by the prevailing water vapor saturation pressure at room temperature. Equation (2) can then be solved for R _WET .

  As is apparent from the foregoing, RDRY and RWET are system specific constants, i.e., they are the characteristics of the material used to make the surface, or at least the surface portion 32 of interest, the airflow through the holding surface. 40 state characteristics and closeness of airflow to the user's skin. Factors such as TSTREAM, TSKIN, PH2O, STREAM and PH2O, SKIN are environmentally related factors because their values depend on room air temperature and humidity, and general conditions in the user's skin.

The total heat recovery (heat removal) capacity THWC is the sum of the dry flux capacity DFC and the wet flux capacity WFC. The actual total heat recovery THW is the sum of the dry flux DF and the wet flux WF.
THWC = DFC + WFC (3A)
THW = DF + WF (3B)

In this application, we denote wet flux capacity and wet flux with units of energy / unit time / unit area as evaporation capacity EC and evaporation rate ER with units of (water) mass / unit time / unit area. Is effective. The heat of water evaporation at about 36 ° C. is about 2420 Joules / gram. That is, approximately 2420 joules (2420 watt seconds or 0.672 watt hours) of energy are required to evaporate 1 gram of water. Therefore, wet flux capacity of one watt / ^{m 2} corresponds to the evaporation capacity of 1.489G / time / ^{m 2,} 1 actual moisture flux W / ^{m 2} is 1.489G / Time / ^{m 2} Corresponds to the actual evaporation rate.
EC = 1.489 WFC (4A)
ER = 1.489 WF (4B)
Where EC and ER are the evaporation capacity and evaporation rate expressed in grams / hour / square meter, 1.489 is the reciprocal heat of evaporation of water at 36 ° C. expressed in grams / joule, and WFC and WF are Wet flux capacity expressed in grams / watt hour and actual wet flux.

Using equations (1), (2A) and (2B), equations (3A) and (3B) can be rewritten as follows:
THWC = (1 / RDRY) (TSKIN-TSTREAM) + (1 / RWET) (PH2O, SKIN-PH2O, STREAM) (5A)
THW = (1 / RDRY) (TSKIN-TSTREAM) + (1 / RWET) (PH2O, SKIN-PH2O, STREAM) (5B)
Or alternatively,
THWC = (1 / RDRY) (TSKIN-TSTREAM) + EC / 1.489 (6A)
THW = (1 / RDRY) (TSKIN-TSTREAM) + ER / 1.489 (6B)
here
EC = 1.489 WFC = (1.489 / RWET) (PH2O, SKIN-PH2O, STREAM) (7A)
ER = 1.489 WF = (1.489 / RWET) (PH2O, SKIN-PH2O, STREAM) (7B)

  Equations describing the potential or capacity of the system (Equations 5A, 6A, 7A) are applied regardless of whether liquid sweat is deposited on the user / surface interface, and show equations for actual performance (Equation 5B). 6B, 7B) is given the condition that it only applies when liquid sweat is being deposited on the user / surface interface.

If the values of the system constants R _DRY and R _{WET and} the values of the environmental parameters T _SKIN , T _STREAM , P _{H2O, SKIN} , P _{H2O, STREAM} are known, equations (5A), (6A) and (7A) are used. Thus, the potential total heat recovery THWC and the evaporation capacity EC available to cool the bed user can be determined. Similarly, equations (5B), (6B) and (7B) can be used to determine the actual total heat recovery THW and the evaporation rate applied to the bed user, which uses these equations The condition (the presence of sweat available for evaporation at the user / surface contact surface) is satisfied. T _SKIN can be determined from actual skin temperature measurements or expressed as a standard value such as 36 ° C. PH _{2 O, SKIN} can be expressed as the partial pressure of water vapor at T _SKIN at the relative humidity prevailing at the user / surface interface. The relative humidity is 100% when there is liquid phase sweat available at the user / surface interface for evaporation. When a standard value of 36 ° C. is used as the value for T _SKIN , PH _{2 O, SKIN} at a relative humidity of 100% can be expressed as 5946 Pa.

Or, if the desired evaporation rate ERDESIRED is specified, using the parameters RWET, RDRY, TSKIN, PH20, SKIN, room ambient air temperature TAMBIENT, and room relative humidity RHAMBIENT, the specified evaporation rate and result The flow conditions necessary to achieve the total heat recovery obtained, TSTREAM, REQUIRED and PH2O, STREAM, REQUIRED can be calculated. To reflect that evaporation rate is a user-specified parameter, while TSTREAM, PH2O, STREAM, and THW are dependent parameters, equations 5, 6 and 7 are expressed as equations 5C, 6C and 7C below: Has been rewritten. Equations 5C-7C assume the presence of sweat to evaporate at the skin / holding surface interface.
WFREQUIRED = ERDESIRED / 1.489 =
(1 / RWET) (PH2O, SKIN-PH2O, STREAM, REQUIRED) (7C)
THW = (1 / RDRY) (TSKIN-TSTREAM, REQUIRED) +
(1 / RWET) (PH2O, SKIN-PH2O, STREAM, REQUIRED) (5C)
Or as an alternative
THW = (1 / RDRY) (TSKIN-TSTREAM, REQUIRED) + ERDESIRED / 1.489 (6C)

Another alternative is to specify the desired total heat recovery THWDESIRED and, if it exceeds the existing total heat recovery, simply increasing the dry flux will provide the desired total heat recovery, or increasing the wet flux and drying. Although a combination of flux increases may be necessary, the distribution of dry and wet flux cannot be specified independently for a given THWDESIRED. In fact, some designations of total heat recovery may require a greater wet flux (evaporative cooling) than desired. To reflect that THW is a user-specified parameter, whereas flow conditions TSTREAM, PH2O, STREAM, and EC are dependent parameters, Equations 5, 6 and 7 are replaced by Equations 5D, 6D and 7D. Has been rewritten as: Equations 5D-7D assume the presence of sweat to evaporate at the skin / holding surface interface.
THW _DESIRED = (1 / R _DRY ) (T _SKIN -T _{STREAM, REQUIRED} ) +
(1 / R _WET ) (P _{H2O, SKIN} -P _{H2O, STREAM, REQUIRED} ) (5D)
Or as an alternative
THW _DESIRED = (1 / R _DRY ) (T _SKIN -T _{STREAM, REQUIRED} ) +
ER _REQUIRED /1.489 (6D)
here
ER _REQUIRED = 1.489 WF _REQUIRED =
(1.489 / R _WET ) (P _{H2O, SKIN} -P _{H2O, STREAM, REQUIRED} ) (7D)

As described above, the determination of the required flow conditions according to equations 5C-7C and 5D-7D uses 36 ° C. as the value for T _SKIN and 36 ° C. and 100% RH as the values for PH _{2 O, SKIN} . Some simplification can be achieved by using a water vapor pressure of 5946 Pa.

The operation of the MCM-capable holding surface and the microclimate management system of FIG. 3B is understood by referring to the graph of FIG. 6B showing the pressure expressed in Pascals (Pa) as a function of the temperature expressed in degrees Celsius. . Line VP represents the vapor pressure of water and is also referred to as the saturation line or the 100% relative humidity (RH) line. The circle indicates a sweating bed user with a skin temperature T _SKIN of 36 ° C. Due to sweat at the contact surface of the user / holding surface, the relative humidity at the contact surface is 100%, which corresponds to a vapor pressure of 5946 Pa at 36 ° C.

The square marks indicate the ambient air in the room with a temperature of 25.6 ° C. and a relative humidity of 75%, which corresponds to 2451 Pa PH _{2 O, AMBIENT} . The ambient air in the room is unregulated in the sense that no temperature or humidity adjustments are applied other than that applied at the facility's HVAC equipment. If the airflow 40 flowing through the holding surface channel 30 includes this unregulated ambient air, equations (1)-(4) and R _DRY = 0.300 (m ² ° C) / watt and R _WET = 250 (m According to ² Pa) / Watt, the user will experience:
ER = 20.8g / hour / m ² , corresponding to 3495 Pa partial pressure difference
WF = 14.0 Watts / m ²
DF = 34.7 Watts / m ² , corresponding to temperature difference of 10.4 ° C
THW = 48.7 Watts / m ²

If it is desirable to increase evaporative cooling, a user, such as a nurse or other caregiver, may use the keypad 44, for example 24.0 g / hr / m ² (this can be achieved with unregulated ambient air. Would specify a desired evaporation rate ER, such as greater than .8 g / hr / m ² . In response to the user's instructions, the controller 50 commands the operation of the chiller 60 to cool the ambient temperature to 16.8 ° C. (triangle mark), which is the ambient air is 100% relative humidity. It is lower than 20.8 ° C., which is the temperature necessary to reach the state of (oval mark). As can be seen in the graph, cooling from 25.6 ° C. to 20.8 ° C. reduces the temperature of the air at a constant water vapor partial pressure until the relative humidity increases to 100%. This segment of the cooling process increases the dry flux capacity of air (and also increases the actual dry flux), but because there is no change in partial pressure, its wet flux capacity or actual wet flux is Do not increase. Cooling from 20.8 ° C. to 16.8 ° C. proceeds along the saturation line VP, condensing the water vapor and thereby dehumidifying the air (ie, from a mixture of gas phase H ₂ O molecules and gaseous air). Remove water molecules). This segment of the cooling process has the intended effect of increasing the evaporative capacity EC and the evaporative rate ER (due to a decrease in the wet flux capacity WFC and the actual wet flux WF and thus the partial pressure from 2451 Pa to 1916 Pa). And further increase dry flux capacity and dry flux (due to further temperature reduction from 20.8 ° C. to 16.8 ° C.).

  The water removal system 62 drains or otherwise removes liquid water. The illustrated water removal system includes a nucleation device 66 for promoting and enhancing the efficiency of the transition from the gas phase to the liquid phase. Referring to FIG. 7B, an example nucleation device is a device with a number of vertically oriented fibers 68 protruding into the air stream 40. The fibers converge in the funnel 70. Water drops collect on the fibers. The weight of the water drop moves the fibers where it drops into the funnel downwards, drawing water from the system. The cooled and dehumidified air is then supplied to the holding surface internal channel 30 where its enhanced dry flux capacity and wet flux capacity appear as actual heat transfer.

Table 1 below compares the performance parameters of the microclimate management system using unregulated ambient air (25.6 ° C., 75% RH) and air cooled as described above. Increase of 31.4 g / Time / ^{m 2} of the total heat recovery should be noted that including the dry flux 2.1 g / time / ^{m 2} of wet flux and 29.3 g / Time / ^{m 2} . Of the 29.3 g / hr / m ² dry flux, 13.3 g / hr / m ² is the dry flux produced by the cooling required to achieve a wet flux of 2.1 g / hr / m ^2. It is.

上述の方法およびシステムは、蒸発率を増加させた結果として、望まれるより大きな合計熱回収（本明細書で「過冷却」と呼ばれる状態）を生じる。例えば、蒸発率を２０．８から２４．０ｇ／時間／ｍ^２に増加させるという蒸発効果が望ましい場合があるが、合計熱回収の少なくとも一部は望ましくない場合がある。ヒーター６４を利用して、冷却・除湿された空気を流路３０に供給するステップの前に空気を加熱することによって、このような状態を緩和することができる。実際問題として、ヒーターは、冷却空気の温度が不十分に低い、または低いであろうと判断された場合のみ作動する。再び図６Ｂを参照すると、加熱により、冷却・除湿された空気の温度が１６．８℃から、例えば１９．０℃（六角形の印）などのより高い値に上昇する。加熱ステップは、気流４０中の水蒸気の分圧には影響を与えないため、蒸発率にも影響しない。しかし、温度の上昇は乾流束を（１６．８℃での乾流束と比較して）減少させる。表２は、１９．０℃に再加熱された空気と比較した、１６．８℃に冷却された空気を使用した微気候管理システムの性能パラメータの変化を要約している。表３は、２５．６℃および７５％ ＲＨの無調節の周囲空気を使用した場合の類似の比較を示している。

The methods and systems described above result in greater total heat recovery (a condition referred to herein as “supercooling”) as a result of increasing the evaporation rate. For example, the evaporation effect of increasing the evaporation rate from 20.8 to 24.0 g / hour / m ² may be desirable, but at least a portion of the total heat recovery may be undesirable. By heating the air before the step of supplying the cooled and dehumidified air to the flow path 30 using the heater 64, such a state can be alleviated. In practice, the heater will only operate if it is determined that the temperature of the cooling air will be insufficiently low or low. Referring again to FIG. 6B, heating increases the temperature of the cooled and dehumidified air from 16.8 ° C. to a higher value, such as 19.0 ° C. (hexagonal mark). Since the heating step does not affect the partial pressure of water vapor in the airflow 40, it does not affect the evaporation rate. However, increasing the temperature decreases the dry flux (compared to the dry flux at 16.8 ° C.). Table 2 summarizes the changes in the performance parameters of the microclimate management system using air cooled to 16.8 ° C compared to air reheated to 19.0 ° C. Table 3 shows a similar comparison when using unadjusted ambient air at 25.6 ° C. and 75% RH.

図６Ｂも、使用者／表面の接触面に液相汗がない一例を示している。本実施例は、接触面において９０％の相対湿度および３６℃の温度を仮定している（四半円の印）。従って、Ｐ_{Ｈ２Ｏ，ＳＫＩＮ}は約５３５１Ｐａである。湿流束容量ＷＦＣの計算は、９．２ワット／ｍ^２の熱伝達の潜在能力を示すことになる。対応する蒸発容量の計算は、使用者／表面の接触面から約１３．７ｇ／時間／ｍ^２の水分（汗）を除去する潜在能力を示すことになる。しかし、熱伝達および蒸発のこれらの値は、まず乾熱伝達が温度を約３４．１℃まで低下させた場合のみ、実現される（温度は５３５１Ｐａで相対湿度１００％に対応している）。

FIG. 6B also shows an example where there is no liquid-phase sweat at the user / surface contact surface. This example assumes a 90% relative humidity and a temperature of 36 ° C. at the contact surface (marked by a quarter circle). Therefore, _{PH2O, SKIN} is about 5351 Pa. The calculation of the wet flux capacity WFC will indicate a heat transfer potential of 9.2 watts / m ² . The corresponding evaporation capacity calculation will show the potential to remove about 13.7 g / hr / m ² of moisture (sweat) from the user / surface interface. However, these values of heat transfer and evaporation are only realized if dry heat transfer first reduces the temperature to about 34.1 ° C. (temperature corresponds to 5351 Pa and relative humidity of 100%).

FIG. 5B is a block diagram of an algorithm for increasing the evaporation capacity of the MCM-capable holding surface beyond what can be achieved with unregulated ambient air. The numbers on the right of the diagram block are from the above example, using 36 ° C. as the value for T _SKIN and the vapor pressure of 5946 Pa for water at 36 ° C. and 100% RH as the values for PH _{2 O, SKIN} . At block 100, the algorithm calculates the partial pressure of water vapor P _{H2O, AMBIENT} at dominant ambient conditions as a function of relative humidity and water vapor pressure P _VAPOR (which is a function of ambient temperature T _AMB ). To:
P _{H2O, AMBIENT} = (RH) (PVAPOR) (8)
P _VAPOR is arbitrary, such as by using a _look-up table that matches the saturation line VP of FIG. 6B, or by an equation that gives the vapor pressure in Pascal as a function of temperature in ° C, such as the cubic equation (9) Can be determined in a convenient way. Equation (9) agrees satisfactorily with the saturation line between about 10 ° C. and 40 ° C .:
P _VAPOR = .0776 (T _AMB ³ )-.757 (T _AMB ² ) + 80.364 (T _AMB ) + 413.15 (9)
Block 102 uses equations (2) and (4) to calculate the evaporation rate ER _AMBIENT achievable with ambient air, subject to the presence of sweat to evaporate at the skin / holding surface interface. .

Block 104 evaluates whether the desired evaporation rate value input by the user on keypad 44 exceeds the evaporation rate achievable with unregulated ambient air. Otherwise, a message prompting the user for another desired value, a message providing guidance on which evaporation rate values are acceptable, or confirming that the evaporation rate achievable in ambient air meets the condition The control device takes a “corrective action” at block 106, such as instructing the display panel 46 to display one or more messages, such as a message to ask for. If the user provides an acceptable desirable evaporation rate, such as 24 g / hr / m ² , the algorithm proceeds to block 108.

At block 108, the algorithm uses equation (7B) to calculate the partial pressures of water vapor PH _{2 O, STREAM, REQUIRED} required to achieve the desired evaporation rate.

At block 110, the algorithm again uses the relationship between the vapor pressure and the temperature T _{STREAM, REQUIRED} to determine the temperature required to achieve the PH _{2 O, STREAM, REQUIRED} determined at block 108. .

At blocks 112 and 114, the algorithm determines the difference ΔT between the ambient temperature and the required temperature determined at block 110 and evaluates whether ΔT is within the chiller's known performance ΔT _MAX . Otherwise, instruct the display panel 46 to display one or more messages, such as a message asking the user for another desired evaporation rate value or a message providing guidance on which evaporation rate value is achievable. The control device takes “corrective action” 116. If the user provides an acceptable evaporation rate acceptable to the user, the algorithm repeats the appropriate steps starting at block 104 and proceeds to block 118.

At block 118, the controller activates chiller 60 to cool the ambient air to the required temperature T _{STREAM, REQUIRED} determined at block 110.

  At block 120, the controller determines whether the overcooling condition occurs by cooling the ambient air to the required temperature determined at block 110. The subcooling test may take various forms, for example, a proactive or corrective order from the user, or a predetermined limit for a specific user, a specific class of user, or a limit established by a facility protocol. If there is a problem with the subcooling test, the algorithm proceeds to block 122. If the test is successful, the algorithm proceeds to block 124 where the controller activates the heater 64 to heat the cooled and dehumidified air. The algorithm then proceeds to block 122.

  At block 122, the algorithm determines one or more microclimate performance parameters and displays the parameters on the display panel 46. Table 4 shows examples of parameters that may be of interest along with the numerical values from the above examples.

再び図６Ｂを参照すると、蒸発率を指定するのではなく、目標の合計熱回収を指定することにより、ユーザーがＭＣＭ可能な保持器を管理できるようにするために、本明細書に開示された原理を使用することができる。目標の合計熱回収を達成するために乾流束だけで十分な場合、チラーが作動して、望ましい目標熱回収（例えば、ひし形の印）を達成するために十分低い温度まで周囲空気（正方形の印）を冷却する。この温度は、当然ながら、相対湿度１００％に対応する温度よりも高い。

Referring again to FIG. 6B, disclosed herein to allow a user to manage a MCM capable retainer by specifying a target total heat recovery rather than specifying an evaporation rate. The principle can be used. If only a dry flux is sufficient to achieve the target total heat recovery, the chiller will operate and ambient air (square-shaped) to a temperature low enough to achieve the desired target heat recovery (eg, diamond markings). Cool mark). This temperature is naturally higher than the temperature corresponding to 100% relative humidity.

If dry flux alone is not sufficient to achieve the target total heat recovery, the chiller will operate and be at least as low as necessary to achieve a relative humidity of 100% (20.8 ° C), and the target total heat recovery The air is cooled to a sufficiently low temperature to achieve (eg, a dome-shaped mark). In order to achieve the target total heat recovery, in addition to the dry flux element, the wet flux element is also involved, so that the air flow 40 exerts a drying effect on the bed user by heat recovery. If this leads to excessive drying, it may be desirable or necessary to sacrifice some of the wet flux. In the graph, the evaporative cooling limit is indicated by a limit 52, which is proportional to the predetermined wet flux limit. By observing the limits, chiller operation is limited to achieve total heat recovery at the wedge-shaped mark. Table 5 shows ambient air (column 1), air cooled to achieve a total heat recovery of 58 watts / m ² (column 2), cooled to achieve a total heat recovery of 77 watts / m ^2. Example system performance parameters are shown using fresh air (column 3) and air cooled to the limit line 52 (column 4) to achieve a total heat recovery of 67 watts / m ² .

前述を考慮すると、本方法およびシステムの特定の付加的態様が理解される。例えば、アルゴリズムの特定のステップの順序を変更しうる。例えば、過冷却のテストは、チラーが周囲空気を冷却した後に実行でき、または冷却前に実行しうるが、これはどの程度の冷却を過冷却として特定するかについてある程度の予見があることを条件とする。

In view of the foregoing, certain additional aspects of the present method and system are understood. For example, the order of certain steps of the algorithm may be changed. For example, the supercooling test can be performed after the chiller cools the ambient air, or it can be performed before cooling, provided that there is some foreseeing how much cooling is identified as supercooling. And

  The previous numerical examples suggest that the caregiver will specify the desired value of evaporation rate (mass / unit time / unit area) or total heat recovery (power / unit area). Alternatively, as seen in FIG. 8B, the user interface may be a discrete scale from “0” to “10”, a continuous scale from minimum evaporation rate or total heat recovery to maximum evaporation rate or total heat recovery, or system desirable. Other less technical ways to specify performance can be shown to the user.

  While this disclosure describes specific embodiments, those skilled in the art can make various changes in form and detail without departing from the subject matter defined in the appended claims. Will be understood.

Claims (29)

A bed structure,
Frame,
A deck framework movably connected to the frame;
A panel movably connected to the deck framework;
A mobile converter,
a) for moving the panel relative to the deck frame in response to at least one of a relative translation between the deck frame and the frame; and b) a relative rotation of the deck frame and the frame. A mobile converter,
Bed structure with. The mobile converter is
A rack attached to the frame;
The bed structure of claim 1, comprising a primary gear meshing with the rack and operably connected to the panel. The mobile converter is
A panel rotation drive element driven by the primary gear;
The bed structure according to claim 3, further comprising a panel-movable drive element connected to the panel and interlocking with the panel rotation drive element.   The bed structure according to claim 3, wherein the panel rotation driving element is a panel driving sprocket and the panel movable driving element is a chain. The bed structure is
An idler rotatably attached to the deck framework, and a chain interlocking with the idler and the panel drive sprocket;
The bed structure according to claim 4, comprising the panel and a slider connected to the chain.   The bed structure of claim 1, comprising an actuator extending between the deck framework and mechanical ground.   The bed structure of claim 6, wherein the frame serves as a mechanical ground.   The bed structure according to claim 1, comprising a compression link pivotally connected to the frame and the deck framework.   The bed structure according to claim 8, wherein the compression link is connected to the frame so as not to be movable. The mobile converter is
a) a rack fixed to the frame;
b) a primary gear rotatably mounted on the deck frame and meshing with the rack;
c) a panel drive sprocket mounted coaxially with the primary gear for rotation on the deck framework;
d) an idler sprocket mounted rotatably on the deck framework away from the panel drive sprocket;
e) a slider connected to the panel;
The bed structure according to claim 1, further comprising: a chain connected to the slider in conjunction with the panel drive sprocket and the idler. The bed structure is
Means for converting said relative translation and / or rotation into rotational motion;
Means for converting said rotational motion into parallel motion;
The bed structure according to claim 1, further comprising means for transmitting the translation movement to the panel. A bed structure,
A frame including a gear rack;
A deck framework connected to the frame so as to be pivotable and movable;
A deck panel,
A drive system,
An actuator extending between the framework and mechanical ground;
A primary gear rotatably mounted on the deck frame and meshing with the rack;
A panel rotation drive element rotatable at the same speed as the primary gear;
A bed structure comprising: a drive system comprising a linear drive element connected to the panel in conjunction with the panel rotation drive element.   The bed structure of claim 12, wherein the panel rotation drive element is a sprocket and the linear drive element is a chain. In a bed having a frame, a deck frame that is rotatably and movable relative to the frame, and a panel that is movable relative to the frame, a method for controlling the translational movement of the panel, Said method comprises
Converting the relative motion between the deck frame and the frame into a rotational motion of a primary drive element;
Converting the rotational movement of the primary drive element into a translational movement;
Transmitting the translation movement to the panel.   The method of claim 14, wherein the relative motion is only a relative translation.   15. The method of claim 14, wherein the relative motion is only relative rotation. A method for controlling the performance of a MCM capable holding surface having a flow path for guiding an air flow along at least a portion of the holding surface, comprising:
Specify a desired evaporation rate that is greater than the achievable evaporation rate with unadjusted ambient air;
Cooling the unregulated ambient air to at least as low a temperature as necessary to achieve 100% relative humidity, thereby dehumidifying the air;
Supplying the cooled and dehumidified air to the flow path.   18. The method of claim 17, comprising determining microclimate performance parameters. The microclimate performance parameter is
a) the difference between the evaporation rate due to cooled and dehumidified air and the evaporation rate achievable with unregulated ambient air,
b) the ratio between the evaporation rate due to cooled and dehumidified air and the evaporation rate achievable with unregulated ambient air;
c) the difference between the wet flux resulting from the cooled and dehumidified air and the wet flux achievable with unregulated ambient air;
d) the ratio of the wet flux due to cooled and dehumidified air to the wet flux achievable with unregulated ambient air;
e) the difference between the dry flux resulting from cooled and dehumidified air and the dry flux achievable with unregulated ambient air;
f) the ratio of the dry flux resulting from the cooled and dehumidified air to the dry flux achievable with unregulated ambient air;
g) difference between total heat recovery due to cooled and dehumidified air and total heat recovery achievable with unregulated ambient air,
19. The method of claim 18, selected from the group consisting of: h) a ratio of total heat recovery due to cooled and dehumidified air to total heat recovery achievable with unregulated ambient air.   19. The method of claim 18, comprising heating the cooled and dehumidified air prior to the supplying step. The method comprises
Determining whether the total heat recovery of the cooled and dehumidified air is not high enough;
21. The method of claim 20, comprising performing the heating step only if the total heat recovery of the cooled and dehumidified air is not high enough. A method for managing the performance of an MCM capable holding surface having a flow path for guiding an air flow along at least a portion of the surface, comprising:
Specify a target total heat recovery that is greater than the total heat recovery achievable with unregulated ambient air;
Evaluate whether dry flux alone is sufficient to achieve the target total heat recovery;
If only dry flux is sufficient to achieve the target total heat recovery,
Cooling unregulated ambient air to a temperature low enough to achieve the target total heat recovery;
If dry flux alone is not sufficient to achieve the target total heat recovery,
Cooling the unregulated ambient air to a temperature at least as low as necessary to achieve 100% relative humidity and sufficiently low to achieve the target total heat recovery.   23. The method of claim 22, wherein the specified target total heat recovery is limited by an evaporative cooling limit.   23. The method of claim 22, comprising determining microclimate performance parameters. The microclimate performance parameter is
a) the difference between the evaporation rate due to cooled and dehumidified air and the evaporation rate achievable with unregulated ambient air,
b) the ratio between the evaporation rate due to cooled and dehumidified air and the evaporation rate achievable with unregulated ambient air;
c) the difference between the wet flux resulting from the cooled and dehumidified air and the wet flux achievable with unregulated ambient air;
d) the ratio of the wet flux due to cooled and dehumidified air to the wet flux achievable with unregulated ambient air;
e) the difference between the dry flux resulting from cooled and dehumidified air and the dry flux achievable with unregulated ambient air;
f) the ratio of the dry flux resulting from the cooled and dehumidified air to the dry flux achievable with unregulated ambient air;
g) difference between total heat recovery due to cooled and dehumidified air and total heat recovery achievable with unregulated ambient air,
25. The method of claim 24, selected from the group consisting of: h) the ratio of total heat recovery due to cooled and dehumidified air to total heat recovery achievable with unregulated ambient air. A microclimate management system,
A microclimate-controllable surface,
A chiller for cooling air delivered to the MCM capable surface;
A user interface for receiving instructions on desirable microclimate management performance;
A microclimate management system comprising: a controller responsive to the instructions for operating the chiller. The microclimate management system,
27. The MCM system of claim 26, comprising a heater that heats the cooling air prior to delivery to the MCM capable surface, wherein the controller activates the chiller and heater.   27. The MCM system of claim 26, comprising a water collection system for collecting liquid water. 30. The MCM system of claim 28, wherein the water collection system includes a nucleation device.

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