The present invention relates to a heat pump according to the preamble of claim 1.
DE 198 18 807 A1 describes a heat pump for air-conditioning vehicle passenger compartments that operates in accordance with the adsorber/desorber principle. In this vehicle air-conditioning system, a number of structured metal sheets are placed one on top of another in the form of a stack, so that they form closed cavities and passage spaces, an adsorber/desorber region and a condensation/evaporation region being formed in the cavities in each case. An air flow for heating and/or cooling down the adsorber region and an air flow for generating cooled air by flowing around the evaporator region are controlled in each case by a pair of distributing cylinders for the passage regions, the distributing cylinders having rotatable distributor inserts. The efficiency of a vehicle air-conditioning system of this type is not yet competitive in its described embodiment. In addition, the cooling power which can be achieved is limited in the case of the given overall size of the device.
The object of the invention is to improve the capacity and the driving heat requirement of a heat pump mentioned at the outset at a given overall space.
According to the invention, for a heat pump mentioned at the outset, this object is achieved by the characterizing features of claim 1.
The formation of in each case at least four separate helical chambers in each of the devices for distributing at least the first fluid allows significantly improved exchange of heat between the first fluid and the first zones of the hollow elements.
The term “a fluid” refers in the sense of the invention to basically any free-flowing substance, in particular a gas, a liquid, a mixture of the gaseous and liquid phase or a mixture of the liquid and solid phase (for example flow ice). The term “interaction of the working medium with the first and the second zone” refers to any type of a thermodynamically relevant exothermic or endothermic reaction of the working medium with or in the zone, in which, in particular, heat is exchanged between the respective zone and the fluid flowing around the zone. By way of a specific example, it should be noted that the first zone can contain an adsorber/desorber material, for example zeolite, wherein the working medium may be water which is, in particular, condensable or vaporable in the second zone in capillary structures. Alternatively, the zones can also contain, for example, differing metals, the working medium being for example hydrogen, so that metal hydrides are formed or dissolved in the zones, heat being absorbed and/or heat being emitted. The interaction of the working medium with the zones can include both physisorption and chemisorption or a different type of interaction. The term “a hollow element” refers in the sense of the invention to any element within which the working medium can be conveyed.
An example of the use of a heat pump according to the invention is building engineering. In building engineering, the heating power generated by a burner can be used also to raise environmental heat to a temperature level which can be used for heating purposes. Furthermore, the heat pump can be used, for example, in conjunction with a cogeneration unit to increase the overall efficiency. In winter the heat pump can, for example, be used for more effective utilization of the waste gas heat flow for heating purposes in that additional heat is pumped from outside-temperature level to a level which can be used for heating. In summer the same system, which may be slightly modified or else just set differently, can be used to cool the building in that the waste gas heat flow of the power generator is likewise used to drive the cooling means. Thermal solar energy can however also be used for cooling by means of the heat pump. Equally, the heat pump according to the invention can in principle also be used, as described in DE 198 18 807 A1, for the air-conditioning of, in particular, utility vehicles. Other conceivable applications include the use of district heat in summer for cooling or air-conditioning or the use of waste heat from industrial furnaces to generate air-conditioning cooling or process cooling. Generally, a heat pump according to the invention is distinguished by requiring very little maintenance and being highly reliable. There is high flexibility in the selection of the first and second fluid, which do not have to be the same and can, for example, differ for summer use and winter use.
In a preferred embodiment of the heat pump, the heat pump is an adsorption heat pump, the working medium being adsorbable and desorbable in the first zone and vaporable and condensable in the second zone. In an alternative preferred embodiment, the working medium is reversibly chemisorbable at least in the first zone. The heat pump may also be a pump based on a mixed principle, for example in the sense that some hollow elements operate in accordance with the adsorber principle (physisorption) and other hollow elements display chemisorption.
In a preferred development of a heat pump according to the invention, the flow paths include a first group of at least two adjacent flow paths and a second group of at least two adjacent flow paths, the flow paths of the first group all being flowed through in a first direction and the flow paths of the second group all being flowed through in a direction opposite thereto. This allows the individual flow paths of a group to be assigned to differing temperatures of the fluid, thus improving an exchange with the hollow elements at a given overall size or contact surface area of the fluid and hollow element as a result of adaptation to the temperature profile prevailing therein. An improvement is in this case achieved both by the same direction of the flow of fluid within one group and by the opposing directions of the two groups to each other, thus allowing for the inversion of the progression of temperature during emission of heat relative to absorption of heat.
In a preferred configuration, a plate element comprises a number of parallel flat tubes which are closed at their ends, each of the flat tubes forming a hollow element with a first and second zone. This allows a heat pump to be manufactured cost-effectively, the shape of the flat tubes benefiting an exchange of heat at a given overall size. Particularly advantageously, the flat tubes are hermetically separated from one another. This particularly allows differing hollow elements or flat tubes of the same plate element to display differing temperatures and pressures, leading, on appropriate grading of the temperatures in conjunction with a suitable direction of flow of the fluid along the plate elements, to an again improved exchange of heat at a given overall size.
Also preferably, a hollow plate, the cavity of which is associated with one of the passage regions, is arranged between two of the plate elements, the hollow plate being thermally connected in a planar manner to the adjacent plate elements, in particular connected by soldering. This facilitates a modular construction of a stack of plate elements and passage spaces in a simple and cost-effective manner, the number of specially produced complex components being kept low. Particularly preferably, arranged between two plate elements are in this case a hollow plate of a first type, forming a passage region of a first type, and a hollow plate of a second type which is substantially thermally separated from the hollow plate of the first type and forms a passage region of a second type. In this way, the two types of passage region are at the same time thermally separated while continuing to use standardized components. The hollow plates of the first and second type do not necessarily have to have the same thickness; this can be compensated for by appropriate formation of the plate elements or hollow elements; thus, for example, the hollow plate of the first type can be configured so as to be adapted for a liquid fluid and the hollow plate of the second type for a gaseous fluid.
Also preferably, at least two distributing devices which are arranged at the end of the plate elements in each case and associated with a distribution of the second fluid through the passage regions of the second type are each provided with a stationary hollow cylinder and a distributor insert which is able to rotate in the hollow cylinder. This allows distribution, which is optimized with regard to the exchange of heat, of the second fluid to the passage regions in a simple manner. Particularly preferably, the distributor insert of the devices for distributing the second fluid has in this case partitions which separate off at least three separate helical chambers in at least one of the cylinders, a flow path comprising at least one passage region of the second type being defined by each of the chambers. This also allows optimization of the exchange of heat of the second fluid with the second zones at a given overall space.
In a preferred embodiment, the partitions, which are in particular but not necessarily spirally formed, have lugs by means of which at least one flow path can be temporarily closed. Such temporary closure of a flow path with regard to the exchange of fluid can, depending on the formation of the heat pump, further improve the efficiency of an exchange of heat at a given overall size, by preventing bypass flows.
In a preferred formation of a heat pump, the distributor insert has a connection region with radial apertures, a fluid exchange of the chamber being carried out via the aperture which is aligned in each case with a chamber. This allows simple connection of the helical chamber to an outer fluid guide even when there are a large number of separate chambers. In a particularly simple formation, the fluid exchange of a plurality of the helical chambers is in this case carried out via a corresponding number of the apertures with a multipart connection space which at least partly surrounds the cylinder. Also preferably, a space of the first cylinder connected to a connection space of the second cylinder is connected via a number of channels which are separated from one another. Overall, this allows particularly complex guidance of a large number of flow paths using simple and cost-effective means.
Furthermore, provision may preferably be made for each of the distributor inserts to be able to rotate such that it can be driven in synchronization with the other distributor inserts. Phase-matched synchronization of the rotational movement of the distributor inserts is generally required for efficient functioning of the heat pump. Advantageously, the two distributor inserts of the first fluid and the two distributor inserts of the second fluid are each positioned in their phase position in such a way that the flow regions communicating with the chambers correspond to one another. In a preferred embodiment, a device for distributing the second fluid can in this case be altered relative to a device for distributing the first fluid such that it can be adjusted with respect to a phase position of a distribution cycle. This can be carried out, in particular, via a phase position of the distributor inserts. The adjustability of the phase position allows further optimization of the capacity of the heat pump. Generally speaking, optimization of the phase position can improve the mode of operation as a function of the average temperatures of the fluids, the type of mode of operation of the hollow elements and the type of working medium, the type of fluids and further parameters of the heat pump.
In a further advantageous formation, an inclination of a coiled chamber is not constant over the length of the cylinder. As a result, a variable number of passage regions are connected to each chamber over a cycle or a revolution of the distributor insert or the flow path defined by the chamber has a variable width; in individual cases, this can optimize the capacity of the heat pump at a given overall space.
Generally speaking, a plurality of hollow elements which are hermetically separated from one another may be provided, at least two of the hollow elements having differing working media and/or sorbents. In principle, a heat pump according to the invention is not limited to uniform substance systems in each of the hollow elements.
In order generally to improve heat exchange performance, provision is preferably made for the flow paths of the first fluid to be flowed through in the opposite direction compared to the flow paths, which are associated via identical hollow elements, of the second fluid.
In a first expedient design, provision is made for the partitions of the distributor insert to be spirally formed and for the separated-off chambers to be helical.
In an alternative expedient embodiment, the partitions of the distributor insert run substantially straight over the length of the distributor insert. In this way, the distributor inserts can be manufactured simply and cost-effectively, in particular as bodies, at least certain portions of which are substantially prismatic. These bodies can be manufactured, for example, as optionally post-machined extruded profiles. For simple provision of the plurality of flow paths, the hollow cylinder has in this case a plurality of apertures, apertures which succeed one another in the axial direction each being arranged offset from one another by an angle. This provides in a constructionally simple manner a cyclic sequence of flow paths which migrate in the stacking direction of the hollow elements as a result of rotation of the straight distributor insert.
In a particularly suitable constructional detailed solution, the hollow cylinder surrounding the distributor inserts has in this case an inner and an outer wall, a plurality of annular chambers arranged in axial succession being formed between the two walls. This allows, in particular, simple connection of the hollow cylinder to the stack of plate elements or hollow elements. Particularly preferably, the annular chambers are formed as annular chamber modules which can be stacked in the axial direction. This allows manufacture, which is adapted in a cost-effective manner, of hollow cylinders or distributing devices of differing lengths or heat pumps of differing size to be achieved using the same parts.
In a further advantageous embodiment of the heat pump, a means is provided for distributing the second fluid to optimize capacity at a given overall space, the second fluid being guided by means of the distributing device via a plurality of flow paths through the passage regions of the second type. Particularly preferably, one of the flow paths forms in this case a closed loop which is separated from the remaining flow paths of the second fluid. The closed flow path has in this case advantageously a smaller width in the stacking direction than an adjacent flow path, the closed flow path being guided, in particular, for intermediate-temperature evaporation and/or intermediate-temperature condensation. Such guidance of the closed flow path forms inner thermal coupling of an evaporation zone and a condensation zone of the heat pump, thus allowing, in particular, heat sources to be utilized even at a lower temperature range. In an expedient detailed configuration, the closed flow path comprises in this case a pump member for conveying the fluid.
This embodiment utilizes the possibility of producing merely by means of the fluid control a type of cascade connection, either to lower the required desorption temperature and/or to increase the difference in temperature between the minimum adsorption temperature and evaporation temperature (rise in temperature). This is achieved as a result of the fact that the fluid distributing cylinders for fluid-controlling the phase alternation zone contains between the distributing chambers for condensation and for evaporation intermediate chambers through which an additional small circuit circulates. As a result, heat is transferred from the condensation end phase to the evaporation end phase using cold fluid to cool the condenser. This causes a reduction in pressure at the end of the desorption/condensation phase, thus lowering the temperature required for complete desorption. The rise in pressure associated therewith at the end of the adsorption/evaporation phase raises the required adsorption temperature. These effects can also serve to increase the effectively utilized load width of the adsorbent or reactant used.
Further advantages and features of the invention will emerge from the exemplary embodiment described hereinafter and also from the dependent claims.
A preferred exemplary embodiment of a heat pump with a plurality of modifications will be described hereinafter and explained in greater detail with reference to the appended drawings, in which:
heat pump from
The flat tubes are integrally connected to one another but hermetically separated from one another. Each of the flat tubes 2 forms a hermetically closed hollow element or a continuous cavity which has a first zone 2a and a second zone 2b. The flat tubes are closed at both end faces.
Provided between the two zones 2a, 2b is an empty interval 2c which causes a certain spacing of the zones 2a, 2b. A respective adsorbent medium, in particular zeolite, which is in optimum thermal contact with the outer wall of the flat tube 2, is provided in the first zone 2a. The second zone 2b is lined on its inside with a suitable capillary structure allowing optimally effective storage of a liquid phase of a working medium, in particular water, provided in the flat tube 2. The zone 2a thus forms an adsorber/desorber zone and the zone 2b forms an evaporator/condenser zone. With regard to the precise configuration of the zones, reference is made, in particular, to the disclosure of document DE 198 18 807 A1. In an alternative preferred embodiment, the adsorbent medium is activated carbon and the working medium water. Irrespective of the aforementioned pairs of adsorbent medium and working medium, in terms of design, all of the exemplary embodiments describe adsorption heat pumps. As mentioned at the outset, the invention is not limited to this operating principle but may rather include all other processes or reactions of a working medium.
A respective layer 3, within which a passage of a first fluid and a second fluid is provided, is located between two plate elements 1. In this case, the first fluid is thermally connected to the first zones 2a and the second fluid to the second zones 2b of the plate elements 1 while passing through the layers 3. The layer 3 comprises a first type of hollow plates 4 and a second type of hollow plates 5. These hollow plates are also closed at their ends and on their upper and lower longitudinal sides. The hollow plates 4, 5 are soldered, bonded or braced in a planar manner to the respectively adjacent plate elements 1 to ensure effective thermal contact. Located between two hollow plates 4, 5 of the same layer is a gap 6 which substantially prevents thermal contact between the hollow plates 4, 5. The sectional view according to
Distributing devices 7, 8, 9, 10, each having substantially the shape of a cylinder, are provided perpendicularly to the planes of the plate elements 1 and the hollow plates 4, 5 in end-side regions of the hollow plates 4, 5. A first cylinder 7 and a second cylinder 8 are in this case provided in opposing end regions of the first hollow plates 4 and a third cylinder 9 and a fourth cylinder 10 are provided in opposing end-side regions of the hollow plates 5. In this case, the first two cylinders 7, 8 serve to distribute a first fluid through passage regions of a first type formed in the hollow plates 4 and the pair of cylinders 9, 10 serves to control or distribute the flow of a second fluid through the hollow plates 5 and the passage regions thereof.
Each of the cylinders 7, 8, 9, 10 has a rotatable distributor insert 7a, 8a, 9a, 10a which is guided in a cylindrical inner circumference of a stationary hollow cylinder. The first distributor insert 7a and the second distributor insert 8a are substantially the same in their design. Each of the distributor inserts 7a, 8a, by means of which a through-flow of the first fluid is controlled, comprises a number of helical chambers 11 which are formed by spirally formed partitions 7b, 8b and the inner circumferential walls 7c and 8c of the cylinders 7, 8. Respective lugs 7d, 8d, which cover part of the cylindrical inner circumferential wall 7c, are attached to the partitions 7b, 8b, radially to the ends thereof.
The three-dimensional views according to
The distributor inserts 7a are expediently formed in such a way that their coiled chambers 11 or spirally formed partitions 7b rotate, over the length of the distributor insert 7a and the height of the stack of plates 1, 4, 5 of the heat pump, fully about the axis of symmetry of the cylinder.
As a result of driven rotation of the distributor inserts 7a, 8a within the stationary hollow cylinders 7c, 8c, the group of the passage regions 13, each of which is connected to the same chamber 11, thus migrates along a stacking direction of the plates 1, 4, 5 of the heat pump. This is illustrated, in particular, by the schematic view in
Connection spaces 19 surrounding the connection regions 16, 17 are provided outside the connection regions 16, 17. The spaces 19 are separated from one another by means of annular partitions 19a which rest on the closed regions of the surfaces of the connection regions 16, 17 so as to produce a sliding seal, in particular in the manner of shaft ring seals. As a result, in each case just one aperture 18 is connected to one of the annular connection spaces 19, the annular spaces 19 being isolated from one another.
A number of connecting channels 20 (shown merely schematically in
Synchronous rotation of the two distributor inserts 7a, 8a then causes displacement of the flow paths in accordance with the varying connections of the helical chambers 11 to the passage regions 13 in the stacking direction of the plate elements 1 or the hollow elements 4. This variation in the contacting of the individual chambers 11 with the individual passage regions 13 is equivalent to migration of the flow paths in the stacking direction, in the present case toward the right. As a result of the displacement of the flow paths toward the right, the sorption tubes 2, which are illustrated by way of example, are gradually cooled down more and more until the coldest zone has reached these elements. A large proportion of the adsorption heat transferred in this process is in this case transferred to the heat-carrier fluid which is heated more and more in the process. The heating power of the subsequent heating element 23 can be reduced as a result. In principle, the flow paths migrate or the distributor inserts rotate very slowly, as these processes are adapted to the sluggishness of the exchange of heat between the first fluid and the respective hollow elements 2 and also of the conveyance of substances within the hollow elements 2.
In the exemplary embodiment according to
The first group of flow paths (flow paths 1-6), which are in addition the first six flow paths after the cooling in the cooling element 24, serve to cool down the first zones or the sorption regions of the cavities 2, whereas the second six flow paths serve to heat up these regions.
To further illustrate the cyclic processes in the sorption region of the heat pump,
A third diagram according to
As shown in
At the starting point in time, a selected sorption plate (cavity 2) is at the highest temperature. In the view according to
As a result of slow further rotation of the distributor inserts 7a, 8a, all twelve flow paths, each of which have a differing temperature, migrate toward the right, as a result of which the cavity first enters into contact with increasingly cool first fluid. As a result of adsorption of working medium, in the present case water vapor, the pressure in the cavities 2 falls (see
After passing through the coldest zone, zone No. 6 according to
In the present example, the fluid temperature jumps rapidly to approximately 160° C., corresponding to the point of transition from flow path No. 6 to flow path No. 7. As a result, the sorbent is heated rapidly. After passing through equilibrium loading, the adsorption changes into desorption, as a result of which the water vapor partial pressure rises rapidly (see
It is in this case advantageous to orient the heat pump in the space in such a way that the axes of the cavities 2 lie substantially horizontally in order to prevent adverse influences of gravity on the distribution of the working medium.
Both the adsorption/evaporation process (useful process) and the desorption/condensation process (regeneration process) are timed, by adapting the rotational speed of the distributor inserts, in such a way that use is made of a loading region of the adsorbent that leads to a good compromise between power density and the ratio of useful heat to drive heat of the device as a whole. In the present simulated example, both partial processes are of equal length. Asymmetrical division in terms of time of the two partial processes is however easily possible in that the chambers 11 of the distributor inserts 7a, 8a are distributed accordingly asymmetrically along the circumference. This can expediently be achieved by adapting the division of the opening angles for the chamber segments.
Likewise, it can be beneficial, to optimize the mode of operation, to set a phase shift between the control of the distributing devices 7, 8 for the adsorption/desorption zone and the distributing devices 9, 10 for the evaporation/condensation zone.
In a first modification of the above-described heat pump, what are known as adiabatic phases can be introduced. This is provided in the view according to
As mentioned hereinbefore, the focus of the development of a heat pump according to the invention is on the control of the adsorption/desorption process or the processes of the first zones and the corresponding control of the second fluid in the second zone. However, owing to the slight differences in temperature, with the exception of adiabatic zones, usually fewer chambers of the distributor inserts, and thus fewer differing flow paths, are required in the second zone controlling the evaporation/condensation process. In the simulated example described hereinbefore, there is therefore only one group of flow paths for evaporation and one for condensation, such as is in principle known from DE 198 18 807 A1. However, to improve the heat pump, provision may be made also in this region for multiple through-flow which takes place in accordance with the division of the chambers 11 of the distributor inserts 9a, 10a. In this case, individual chamber segments can be used as deflecting segments, distributing and collecting segments.
By way of example,
The view according to
The first distributor insert 109a has, viewed in cross section, a chamber having an opening angle of 180°, two chambers which symmetrically adjoin said chamber and have an opening angle of 45°, and a chamber which is arranged therebetween and has an opening angle of 90°. The other distributor insert 110a has a chamber having an opening angle of 180° and two chambers having an opening angle of 90°. Directions of flow of the fluid are in each case indicated by means of an arrow tip as coming out of the plane of the drawing and by means of an arrow shaft (cross) as going into the plane of the drawing.
The second fluid to be cooled is guided into the two 45° chambers of the left-hand distributor insert and enters the first and the last of the partial blocks shown from the left-hand side in each case. On the opposing side, they are received by the two 90° chambers of the distributor insert 110a and distributed to the two central partial blocks which are then flowed through in the opposing direction. In a further configuration, the partition between the two 90° chambers may be dispensed with to allow mixing of the two partial flows out of the end-side partial blocks. The two 180° chambers are provided for the condensation zones.
The diagram according to
Alternatively, the flow path, provided for evaporation, of the second zone can also be flowed through twice with only two partial blocks. An exemplary division of chambers to implement such a modification is shown in
A further embodiment of a heat pump, which is optimized in particular with regard to the flow paths of the second fluid, is illustrated schematically in
In the illustrated case, according to
Partial block A shows in a schematic view the position of the distributor inserts at the start of the low-temperature evaporation stage which serves to cool down the fluid flow used.
The associated flow paths are defined in their width in the stacking direction (see the view of
A further embodiment of the heat pump, which is in particular a design variation, is shown in
As, in particular, the construction of a cylinder 407 according to the view of
A further exemplary embodiment is shown in
To achieve a corresponding distribution of the fluid to the flow paths which migrate in the stacking direction on rotation of the distributor inserts, the cylindrical wall 507c surrounding the distributor inserts 507a has a plurality of apertures 512 which succeed one another in the axial direction and are each arranged offset from one another by a small angle and thus lie on a spiral line along the cylinder wall. Over the entire axial length of the cylinder wall 507c, the spiral line describes one or more, expediently complete revolutions.
The cylindrical wall 507c is surrounded by an outer cylinder wall 507e, radial partitions 507f between the inner wall 507c and outer wall 507e separating off an annular chamber 507g at each of the apertures 512.
In the outer wall 507e, connection openings 507h, which provide a connection to the passage regions of the heat pump, are respectively provided in alignment on a straight line, for each of the annular chambers, without an angular offset.
Specifically, the individual constructionally identical annular chamber modules 530 are each composed of an outer ring 531 and an inner ring 532, the outer ring 532 having a radial chamfer to form the partition 507f between adjacent annular chamber modules 530. In the present case, the inner rings 532 and the outer rings 531 have corresponding teeth 531a, 532a which engage with one another during assembly to set a defined angular offset of the apertures 512. In particular in the case of automated production, such teeth may be dispensed with. The annular chamber modules 530 can be made of one or more suitable materials such as, for example, plastics material or else aluminum.
In order further to simplify manufacture, the outer rings 531 of the two opposing distributing devices 507, 508 can be manufactured at the same time with at least a portion of the passage regions 504 connecting them, in particular by cold extrusion. The flat tube-like passage regions 504 between the rings 531 can also be completed by suitable surface area-enlarging turbulence metal sheets or by metal cover sheets to be soldered on.
Number | Date | Country | Kind |
---|---|---|---|
10 2005 060 183 | Dec 2005 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
---|---|---|---|---|
PCT/EP2006/012058 | 12/14/2006 | WO | 00 | 6/12/2008 |
Publishing Document | Publishing Date | Country | Kind |
---|---|---|---|
WO2007/068481 | 6/21/2007 | WO | A |
Number | Name | Date | Kind |
---|---|---|---|
4398483 | Wood et al. | Aug 1983 | A |
4708672 | Bentz et al. | Nov 1987 | A |
5009085 | Ramshaw et al. | Apr 1991 | A |
5020411 | Rowan | Jun 1991 | A |
5085603 | Haluzak | Feb 1992 | A |
5263432 | Davis | Nov 1993 | A |
5275014 | Solomon | Jan 1994 | A |
5421173 | Lee et al. | Jun 1995 | A |
5507672 | Imaeda | Apr 1996 | A |
5540174 | Kishi et al. | Jul 1996 | A |
5683275 | Nanami | Nov 1997 | A |
5685253 | Alexander, Jr. | Nov 1997 | A |
5743111 | Sasaki et al. | Apr 1998 | A |
6058873 | Koyanagi | May 2000 | A |
6148631 | Watanabe et al. | Nov 2000 | A |
6230642 | McKenney et al. | May 2001 | B1 |
6332422 | Laroche | Dec 2001 | B1 |
6524146 | Spade et al. | Feb 2003 | B2 |
6604479 | McKenney et al. | Aug 2003 | B2 |
6945217 | Makler | Sep 2005 | B2 |
7174726 | Grau et al. | Feb 2007 | B2 |
7305928 | Bradley et al. | Dec 2007 | B2 |
20030066638 | Qu et al. | Apr 2003 | A1 |
20030221438 | Rane et al. | Dec 2003 | A1 |
Number | Date | Country |
---|---|---|
195 15 527 | Oct 1996 | DE |
195 39 103 | Apr 1997 | DE |
198 18 807 | Oct 1999 | DE |
198 18 807 | Oct 1999 | DE |
100 38 637 | Feb 2001 | DE |
11-118286 | Apr 1999 | JP |
11-294888 | Oct 1999 | JP |
2004-340468 | Dec 2004 | JP |
Entry |
---|
Smart Tabs raise your performance expectations, http://www.nauticusinc.com, 2 pages, website visited Aug. 24, 2010. |
Trim Tab Installation by James W. Hebert, http://continuouswave.com/whaler/reference, 17 pages, website visited Aug. 24, 2010. |
Using an Accelerometer for Inclination Sensing, Analog Devices, http://search.analog.com/search/ProductSearch, 9 pages, website visited Aug. 24, 2010. |
How Insta-Trim Boat Levelers Work, http://insta-trim.com, 9 pages, website visited Aug. 24, 2010. |
Fiberglassing the Bottom Trailing Edge of a Power Boat, Boat Builder Newsletter #54, 1 page, http://www.glen-1.com/weblettr, website visited Aug. 24, 2010. |
The Science of Levers, Tommy Boone, Ph.D., Mph et al., Chapter 51, faculty.css.edu/tboone2/asep/Lever.doc, 16 pages, website visited Aug. 24, 2010. |
Porpoising oscillations of very-high-speed marine craft, Y. Ikeda and T. Katayama, The Royal Society, Phil. Trans. R. Soc. Lond. A (2000) 358, pp. 1905-1915. |
Number | Date | Country | |
---|---|---|---|
20090000327 A1 | Jan 2009 | US |