Patent Application
20130133853
The invention refers to mechanical engineering and can be used for more efficient and safer fluid power recuperation, including mobile applications, such as road-building machines, carrying and lifting equipment as well as hydraulic hybrid trucks and motorcars.
There are devices for fluid power recuperation in the form of hydropneumatic accumulators (hereinafter—accumulators), their shells containing a variable volume gas reservoir filled with pressurized gas via a gas port as well as a variable volume fluid reservoir filled with fluid via a fluid port; while these gas and fluid reservoirs are separated by a separator movable relative to the shell.
Fluid power recuperation is performed using accumulators both with a solid separator in the form of a piston and elastic separators, for example, in the form of elastic polymer membranes or bladders [1] as well as in the form of metal bellows [2].
Before operation the gas reservoir of the accumulator is charged via the gas port with pressurized gas, generally, with nitrogen, up to the initial pressure from several to dozens MPa.
During power transfer from the fluid power system to the accumulator (at hydraulic hybrid vehicle braking, for example) the pumping of the working fluid from the fluid power system into the accumulator occurs as well as working gas compression in it, with the gas pressure and temperature increase. During power return from the accumulator into the fluid power system (at acceleration of the hydraulic hybrid vehicle, for example) the pressurized working gas expands and displaces the working fluid into the fluid power system.
As a rule, the accumulator contains one gas reservoir and one fluid reservoir with equal gas and fluid pressures in them. The higher the hydraulic power transferred to the accumulator, the higher the gas compression ratio in it. To maintain the required recuperated power the pressure increase has to be compensated by reduced delivery of the hydraulic machine (a pump or a motor) hydraulically connected with the accumulator. As the delivery reduces, the hydraulic machine efficiency drops; hence, the total recuperation efficiency drops, which is a disadvantage of such devices.
An increased volume of the accumulator or an increased number of accumulators for gas compression ratio reduction raises the cost of the system, as well as makes it heavier, which is critical for mobile applications.
A well-known device [3] is used to reduce gas compression ratio and, at the same time, to increase the maximum possible recuperated power. The device includes a hydropneumatic accumulator, its shell containing a fluid port communicating with the fluid reservoir of the accumulator separated by a movable separator from the gas reservoir of the accumulator that communicates with at least one gas receiver via a gas port.
When the working fluid is pumped from the fluid power system into the fluid reservoir of the accumulator, the separator is displaced and forces the gas out of the accumulator into the receiver compressing the gas in the receiver and in the accumulator. The work of pumping the fluid into the accumulator is transformed into internal energy of the pressurized gas, its pressure and temperature increasing. When the power returns from the device into the fluid power system, the pressurized working gas expands and is partially forced out of the receiver into the gas reservoir of the accumulator. The separator is displaced with the volume of the fluid reservoir of the accumulator decrease and the working fluid is forced out of it into the fluid power system via the fluid port. The internal energy of the pressurized gas is transformed into the work of the fluid displacement, i.e. the device returns the fluid power received from the fluid power system back into the system, with the gas pressure and temperature decreasing.
The addition of the receiver that is lighter and cheaper than the accumulator to the system allows increasing the amount of the recuperated power at the expense of better use of the accumulator volume and reducing gas compression ratio and, accordingly, the range of variation of the delivery of the hydraulic machines operating in the system, which increases the recuperation efficiency.
A shortcoming of the devices used for fluid power recuperation is the high level of heat losses due to the fact that when compressed and expanded the gas in the receiver exchanges its heat only with the internal walls of the receiver, the distance between them for typical receiver volumes (units and dozens of liters) being too large (dozens and hundreds mm) and the gas heat conductivity being too small.
At such distances the gas heat exchange with the receiver walls caused by the gas heat conductivity is insignificant. Therefore, the gas compression and expansion processes are essentially non-isothermal and there emerge considerable temperature gradients of dozens and even hundreds degrees in the receiver. Considerable temperature differentials in a large receiver volume generate convective flows increasing the heat transfer to its walls dozens and hundreds times. Therefore, the gas heated during compression in the receiver and partially in the accumulator cools down, which results in reduced pressure of the gas and accumulated power losses increasing during storage of the accumulated power (for example, when the hydraulic hybrid vehicle stops). The non-equilibrium heat transfer processes in case of high temperature differentials are irreversible, i.e. the greater part of the heat transferred from the pressurized gas to the receiver walls cannot be returned to the gas during expansion. Thus, when the gas expands, the amount of the fluid power returning to the fluid power system is much less than the amount received during gas compression.
Therefore, the above device has low efficiency of the recuperated fluid power due to high heat losses.
The device of fluid power recuperation selected as the closest analog and proposed in [4] includes at least one hydropneumatic accumulator communicating with at least one gas receiver (gas bottle) via its gas port. The gas receiver is made in the form of aggregate of cells communicating with the gas port of the accumulator. For higher safety the cells have strong walls with considerable thermal capacity exceeding the thermal capacity of the gas in the receiver. The receiver cells are made in the form of narrow channels (tubes) so that the ratio between the receiver volume and the area of the internal surfaces of the cells does not exceed 10 mm, which both reduces the kinetic energy of the gas jet in case of cell shell destruction and increases the heat exchange between the gas and walls of the cells considerably. Thus, the walls of the cells in said receiver perform the function of a regenerating heat exchanger taking heat from the gas during compression and returning the heat to the gas during expansion, thus ensuring lower heat losses of the devices. The closer the walls of the cells to one another, i.e. the smaller the cross dimensions of the cells, the more efficient the heat exchange between them and the gas and the higher the recuperation efficiency. However, a shortcoming of the proposed device is the difficulty of manufacturing of the receiver in the form of a strong honeycomb structure, especially with small size cells necessary for higher heat exchange capacity with the growing recuperation rate. In addition, the proposed honeycomb structures are poorly compatible with commercial gas receivers of the most common type, i.e. made with solid cylindrical shells with rounded ends, the holes in them being much smaller than the diameters of internal chambers of the receivers.
The objective of the present invention is creation of a device for fluid power recuperation with reduced heat losses and increased efficiency of fluid power recuperation combined with better manufacturability and possibility of using off-the-shelf gas receivers (bottles) of various types in the device.
The objective is achieved by proposal of a device for fluid power recuperation that comprises at least one hydropneumatic accumulator, containing in its shell a fluid port communicating with the fluid reservoir of the accumulator separated from the gas reservoir of the accumulator by a movable separator. The gas reservoir of the accumulator communicates via a gas port with at least one gas receiver containing a regenerating heat exchanger made in the form of a metal porous structure, while the aggregate volume of the material of the regenerating heat exchanger is in the range from 10 to 50% of the internal receiver volume and the aggregate area of the heat exchange surfaces of the regenerating heat exchanger reduced to the aggregate internal receiver volume exceeds 2000 cm2/liter, preferably exceeds 10 000 cm2/liter.
Thus, at gas compression or expansion in the receiver the heat exchange between the gas and the regenerating heat exchanger occurs at small average distances between the gas and the heat exchange surfaces and on a large heat exchange area and, therefore, with smaller temperature differentials, which increases reversibility of the heat exchange processes and recuperation efficiency. To achieve smallness of the average distance between the gas and the heat exchange surfaces necessary for effective heat exchange the regenerating heat exchanger is preferably made with the average pore size below 5 mm (here and hereafter the pore size in every particular place of a pore means the diameter of a sphere that can be placed in this place of the pore and the average pore size means said value averaged throughout the volume of the porous structure). To reduce the gas-dynamic resistance of the metal porous structure the regenerating heat exchanger should be preferably embodied with the average pore size of at least 0.05 mm. With said share of the receiver volume occupied by the metal of the regenerating heat exchanger the thermal capacity of the latter exceeds the thermal capacity of the gas in the receiver. For example, the specific thermal capacity of the regenerating heat exchanger made from steel will be from 400 to 2000 kJ/K/m3 while the thermal capacity of the gas (nitrogen) at working pressures of 100-300 bar (and the temperature of about 300 K) is from 120 to 360 kJ/K/m3. The higher the gas working pressure, the higher the thermal capacity of the regenerating heat exchanger must be, i.e. the larger the share of the receiver volume occupied by the material of its porous structure uniformly distributed in the receiver volume. Thus smallness of the average temperature variations and low long-storage losses are ensured.
A metal (steel or aluminum, for instance) porous structure can be made from ready metal items to be disposed, for example, or from metal-working production wastes.
In a preferred embodiment of the device in terms of cost the metal porous structure is formed from turnings or metal cuttings resulting from another process of metal machine work (drilling, milling cut operation, etc.). To increase thermal capacity and vibration resistance these metal turnings or other cuttings inside the receiver can be additionally compacted.
In other embodiments the metal porous structure can be formed from metal wool or metal foam.
To prevent possible penetration of particles or other fragments of the metal porous structure of the regenerating heat exchanger from the gas receiver via its gas port the latter is provided with a blocking element. To reduce the gas-dynamic resistance the axial length of the blocking element exceeds 20% of the axial length of the receiver.
The objective of increasing the manufacturability of the device with the use of various types of the off-the-shelf gas receivers can be fulfilled when the metal porous structure of the regenerating heat exchanger is formed inside the ready shell of the receiver by loading the components forming this structure (chips, wool, metal foam pieces, etc.) through holes in the receiver shell. It is also possible to use receivers made, as in the closest analog, in the form of a set of cells (tubes) with solid walls additionally containing regenerating heat exchangers in the form of the metal porous structures described above.
The invention is described in more detail in the example given below and illustrated by the drawing presenting:
FIG. 1—Schematic representation of the device for fluid power recuperation with one accumulator and one receiver containing a regenerating heat exchanger, axial section of the receiver.
The device for fluid power recuperation in
To ensure high efficiency of the heat exchange between the gas and the regenerating heat exchanger the latter is preferably embodied so that the average distances between the gas and its heat exchange surfaces are small, namely its average pore size should not exceed 5 mm. To reduce gas-dynamic losses during gas flow through the metal porous structure of the regenerating heat exchanger the latter is preferably embodied with small gas-dynamic resistance, namely so that its average pore size is not less than 0.05 mm.
The gas port 8 of the receiver 9 is provided with the blocking element 11 to prevent possible penetration of particles or other fragments of the metal porous structure of the regenerating heat exchanger from the gas receiver via its gas port. The blocking element 11 according to
In an embodiment preferred in terms of simplicity of its introduction the metal porous structure of the regenerating heat exchanger is formed inside the ready shell of the receiver by loading the components making this structure through the hole in the receiver shell. This embodiment allows assembling recuperation devices using off-the-shelf standard receivers (gas bottles) by loading the necessary amount of the components of the metal porous structure into them. An additional advantage of this embodiment is the possibility of increasing efficiency of the already functioning recuperation device containing a receiver.
In addition, it is possible to use honeycomb-structured gas bottles (for example, embodied in the form of a set of cells with solid walls made by extrusion molding or with cells in the form of separate tubes) additionally containing regenerating heat exchangers in the form of the aforesaid metal porous structures improving heat exchange and ensuring additional increase of fluid power recuperation efficiency. In such a variant the technology of manufacturing a honeycomb receiver providing higher safety can be also simplified by reducing the number of the cells and increasing their internal size.
In the device embodiment preferable in terms of cost the metal porous structure is formed from metal turnings. The type of turnings depends on the method of turning of the part (turning of the metal element along the outer or inner cylindrical generatrix, flat or conical face). In terms of heat exchange efficiency it is preferable to use turnings resulting from face or conical turning.
Besides, in manufacturing porous structure of the regenerating heat exchanger it is possible to use cuttings resulting from another process of metal machine work, for example, milling cut operation, press forging wastes as well as metal wool, wires, separate metal elements or metal foam (loaded into the receiver by separate pieces or created inside the receiver by a chemical or another method). In addition it is possible to use metal items of required sizes to be disposed after use (for example, caps, cartridges, washers, springs, etc.).
Metal cuttings or other components of the metal porous structure inside the receiver (for example, metal elements, wool or metal foam pieces) can be additionally compacted as they are loaded into the receiver. The result is a uniform porous regenerating element with high thermal capacity and resistance to receiver vibration and gas circulation both during operation of the device and during its preliminary gas charging or discharging.
For fluid power recuperation in the device the accumulator 1 is connected with the fluid power system via its fluid port 2.
When energy is transferred from the fluid power system into the device the fluid from the fluid power system is pumped into fluid reservoir 3 of the accumulator 1 via its fluid port 2, the separator 4 is displaced reducing the volume of the gas reservoir 5 and forcing some part of the gas into the receiver 9, thus increasing the gas pressure and temperature in the gas reservoir 5 of the accumulator 1 and in the receiver 9. Due to the small average distances between the gas and the heat exchange surfaces of the regenerating heat exchanger 10 in the receiver 9 and its high thermal capacity the gas flowing into the receiver from the gas reservoir of the accumulator effectively gives away some heat to the regenerating heat exchanger 10, which reduces the gas heating ratio during compression; while the gas heat exchange with the regenerating heat exchanger 10 is reversible at small temperature differentials between it and the gas.
During storage of the fluid power accumulated in the device the heat losses are small as the decreased gas heating ratio reduces the heat transfer to the walls of the receiver 9 casing due to the gas heat conductivity.
When energy returns from the device into the fluid power system the pressurized gas in the receiver 9 and the gas reservoir 5 of the accumulator 1 expands, the separator 4 of the accumulator 1 is displaced reducing the volume of its fluid reservoir 3 and forcing the fluid from it into the fluid power system via the fluid port 2. Due to maintaining small average distances between the gas and the heat exchange surfaces of the regenerating heat exchanger 10 the latter effectively returns the received part of heat to the gas. Thus, the device returns the fluid power received from the fluid power system back into it with reduced losses.
Due to the fact that the average size of the pores of the metal porous structure is at least 0.05 mm and the blocking element 11 deeply (preferably to the depth of at least 20% of the axial length of the receiver 9) penetrates into the regenerating heat exchanger 10, the gas-dynamic losses during gas flow between the accumulator and the receiver as well as through the metal porous structure of the regenerating heat exchanger 10 are small.
The blocking element 11 provided with a filtering element 12 prevents particles of the material of the regenerating heat exchanger 10 from penetrating into the gas line 7 and the gas reservoir 5 of the accumulator 1. Thus, the sliding seals of the piston separator 4 are protected from abrasive impact while the gas line 7 is protected from deposition of the particles, which increases reliability of the device.
The embodiments described above are examples of implementation of the main idea of the present invention that also contemplates a lot of other embodiments that are not described here in detail for example comprising several accumulators and receivers as well as various embodiments of a regenerating heat exchanger in the receiver.
Thus, the proposed solutions allow creation of a fluid power recuperation device with the following properties:
1—L. S. Stolbov, A. D. Petrova, O. V. Lozhkin. Fundamentals of Hydraulics and Hydraulic Drive of Machines. Moscow, Mashinostroenie, 1988, p. 172
2—U.S. Pat. No. 6,405,760
3—H. Exner, R. Freitag, Dr. H. Gais, R. Lang, Y. Oppoltser, P. Shwab, E. Zumpf, U. Ostendorff, M. Ryke. Hydraulic Drive. Fundamentals and Components. 2nd Russian edition. Bosch Rexport AG Service Automation Didactics Erbach Germany, 2003, p. 156
4—A. Stroganov, L. Sheshin., Honeycomb Receiver as an Accumulator Shell: Significant Reduction of Danger and Thermal Losses, Proceedings of the 11th Scandinavian International Conference on Fluid Power, SICFP'09, Jun. 2-4, 2009, Linköping, Sweden
5—A. Stroganov, L. Sheshin., Efficient, Safe and Reliable Recuperation: Regenerative Accumulator in Honeycomb Receiver, Proceedings of the 7th International Fluid Power Conference, Mar. 22-24, 2010, Aachen, Germany
| Number | Date | Country | Kind |
|---|---|---|---|
| 2010129792 | Jul 2010 | RU | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/RU10/00575 | 10/1/2010 | WO | 00 | 12/21/2012 |
