CN110986415A - Double-effect Stirling device and operation control method thereof - Google Patents
Double-effect Stirling device and operation control method thereof Download PDFInfo
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- CN110986415A CN110986415A CN201911169611.8A CN201911169611A CN110986415A CN 110986415 A CN110986415 A CN 110986415A CN 201911169611 A CN201911169611 A CN 201911169611A CN 110986415 A CN110986415 A CN 110986415A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
Abstract
The invention discloses a double-effect Stirling device and an operation control method thereof, wherein the device is provided with a piston reciprocating in a piston cylinder, and the method comprises the following steps: braking the piston to move from the piston top dead center position to the piston bottom dead center position; and braking the piston to move from the piston bottom dead center position to the piston top dead center position. The device comprises a Stirling heat engine module 101, a Stirling refrigeration module 102, a piston 7 and piston braking devices 6 and 9, wherein the Stirling heat engine module comprises a first heat exchanger 1, a first regenerator 2, a heat engine discharger 3 and a second heat exchanger 4; the Stirling refrigeration module comprises a refrigerator ejector 10, a third heat exchanger 11, a second heat regenerator 12 and a fourth heat exchanger 13, the heat engine ejector 3 is connected with the refrigerator ejector 10 through an ejector connecting rod 5, and the piston brake device brakes the motion of the piston in the piston cylinder. Compared with the existing double-effect Stirling device, the piston has the advantages of higher performance coefficient and reduced piston mass.
Description
Technical Field
The invention relates to the field of refrigerating machines/heat pumps, in particular to a double-effect Stirling refrigerating machine/heat pump system.
Background
The stirling cycle is an important cycle in the fields of power engineering and refrigeration, and consists of two constant volume processes and two isothermal processes, and theoretically has carnot cycle efficiency or reverse carnot cycle efficiency. The stirling cycle was originally used for a heat engine to obtain work output. Since the stirling cycle was used primarily in the field of refrigeration, the refrigeration effect was produced by the stirling reverse cycle.
Because the Stirling heat engine outputs power and the Stirling refrigerator consumes power, and working media used by the Stirling heat engine and the Stirling refrigerator are the same and have similar structures, the mechanical power output by the Stirling heat engine is used for directly driving the Stirling refrigerator, and the heat-mechanical power-electricity-mechanical process-cold can be reduced into a heat-mechanical power-cold process, so that the overall efficiency is improved.
The efficiency of a double effect stirling cooler is equivalent to the stirling heat engine thermal efficiency multiplied by the stirling cooler refrigeration efficiency. The heat efficiency of the Stirling heat engine depends on the phase difference between the heat engine ejector and the piston, the heat efficiency of the Stirling refrigerating machine depends on the phase difference between the refrigerating machine ejector and the piston, and in order to obtain higher refrigerating efficiency, the heat engine ejector-piston phase difference and the refrigerating machine ejector-piston phase difference are required to simultaneously reach respective phase difference optimal values. However, at present, the heat engine discharger, the piston and the refrigerator discharger of the double-effect stirling cooler all move simultaneously, and the movement and displacement among the three are influenced by the pressure coupling relation, such as: as shown in fig. 1, when the hot end ejector moves downwards, the pressure in the heat engine rises, which causes the pressure of the working medium in the heat engine acting on the piston to increase, and the piston is prevented from moving upwards; similarly, the piston moves downwards, which results in the decrease of the inner volume of the refrigerator, and the compression of the working medium in the refrigerator results in the increase of the pressure of the working medium in the refrigerator acting on the piston, and the obstruction of the downward movement of the piston. Therefore, in the existing double-effect Stirling refrigerator, the movement and displacement among the heat engine ejector, the piston and the refrigerator ejector are difficult to simultaneously meet respective theoretical optimal values of the heat engine ejector-piston phase difference and the refrigerator ejector-piston phase difference due to the coupling relation, so that the efficiency of the double-effect Stirling refrigerator is low. Moreover, the phase of the outlet pressure fluctuation of the heat engine in the double-effect Stirling refrigerator leads the volume flow rate, and the phase of the inlet pressure fluctuation of the refrigerator lags behind the volume flow rate, so that in order to realize the impedance matching between the heat engine and the refrigerator, the piston of the double-effect Stirling refrigerator is heavy, the vibration is large, the reliability is reduced, and meanwhile, the stable operation difference is difficult to realize under the non-rated working condition. In addition, in order to meet the requirement of operation under rated working conditions and partial load working conditions, for example, the rated working condition of the Stirling is 500 ℃/60 ℃/0 ℃, when the device operates at 50 ℃/10 ℃, the heat absorption capacity of a heat source at the end of a heat engine needs to be reduced, so that the output work of the heat engine is reduced, and the refrigerating capacity or the heating capacity of a refrigerating machine is further reduced. However, reducing the heat absorption is generally accomplished by reducing the heating temperature of the heat source at the heat sink end, e.g., from a nominal 500 ℃ to 300 ℃, which is known to reduce system efficiency based on the carnot cycle.
Disclosure of Invention
The present invention aims to overcome the above problems with the present double-effect stirling coolers and proposes a double-effect stirling cooler having a non-simple harmonic moving piston and a method, the device having a piston reciprocating in a piston cylinder, the method comprising: braking the piston to move from the piston top dead center position to the piston bottom dead center position; and braking the piston to move from the piston bottom dead center position to the piston top dead center position. The device comprises a Stirling heat engine module, a Stirling refrigeration module, a piston and a piston brake, wherein the Stirling heat engine module comprises a heat engine discharger, a first heat regenerator, a first heat exchanger, a second heat exchanger, a first cylinder and a working medium; the Stirling refrigeration module comprises a refrigerator ejector, a second heat regenerator, a third heat exchanger, a fourth heat exchanger, a second cylinder and a working medium, the heat engine ejector is connected with the refrigerator ejector through a connecting rod, and the piston brake device brakes the movement of the piston in the piston cylinder. The double-effect Stirling device is composed of two double-effect Stirling devices, a coupling mechanism is arranged between pistons of the two double-effect Stirling devices, the coupling mechanism is a connecting rod or a pipeline, and a phase difference of 180 degrees exists between the piston in the first double-effect Stirling device and the piston in the second double-effect Stirling device in the operation process. Compared with the existing double-effect Stirling device, the Stirling device has the advantages that a higher performance coefficient is generated, the piston quality is reduced, the stable operation under the non-rated working condition is realized, the efficiency under the non-rated working condition is improved, and the Stirling device has wide development and application prospects.
The technical scheme of the invention is as follows:
a method of controlling operation of a dual action stirling device having a heat engine displacer reciprocating within a heat engine cylinder, a chiller displacer reciprocating within a chiller cylinder and a piston reciprocating within a piston cylinder, wherein the heat engine displacer has a top dead center position and a bottom dead center position within the heat engine cylinder, the chiller displacer has a top dead center position and a bottom dead center position within the chiller cylinder, the piston has a top dead center position and a bottom dead center position within the piston cylinder, the method of controlling operation comprising:
and braking the piston to move from the piston top dead center position to the piston bottom dead center position and the piston to move from the piston bottom dead center position to the piston top dead center position, and removing the coupling relation between the piston and the heat engine ejector and the refrigerator ejector.
Further, the method comprises the following steps:
a during the time that the heat engine displacer moves from the 1/4 position to the bottom dead center and from the bottom dead center back to the 1/4 position, the braking device acts to move the piston from the top dead center position to the bottom dead center position;
b during the time when the heat engine displacer moves from the 1/4 position to the bottom dead center and from the bottom dead center back to the 1/4 position, the piston reaches near the bottom dead center position, and the braking device acts to cause the piston to stay at the bottom dead center position.
c during the time that the heat engine displacer moves from the 3/4 position to the top dead center and from the top dead center back to the 3/4 position, the braking device acts to move the piston from the bottom dead center position to the top dead center position;
d during the time the heat engine displacer moves from the 3/4 position to top dead center and back from top dead center to the 3/4 position, the piston reaches near top dead center position and the braking device acts to cause the piston to stay at the top dead center position.
A double-effect Stirling device comprises a Stirling heat engine module 101, a Stirling refrigeration module 102 and a piston structure, wherein a piston 7 is installed in a piston cylinder of the piston structure, the piston 7 divides a piston shell into an upper air cavity 81 and a lower air cavity 82, the upper air cavity 81 is communicated with the Stirling heat engine module 101, and the lower air cavity 82 is communicated with the Stirling refrigeration module 102.
Further, an ejector coupling mechanism is arranged between the heat engine ejector 3 in the Stirling heat engine module 101 and the refrigeration ejector 10 in the Stirling cooler 102, and the coupling mechanism is an ejector connecting rod 5.
Further, the ejector is provided with ejector brakes 14 and 15 which brake the ejector in a dead center position for a part of the time when the ejector is in a top dead center or bottom dead center position.
Further, the piston brake device comprises a gas valve or an electromagnet.
Further, when the braking device is an air valve, the upper air cavity 81 is communicated with the stirling heat engine module 101 through the first piston braking device 6; the lower air cavity 82 is communicated with the Stirling refrigeration module 102 through the second piston brake device 9; the first piston brake device 6 comprises a first air valve group and a first closing plate 63 for closing the top end of the piston shell; the second piston brake device 9 includes a second valve set and a second sealing plate 93 for sealing the bottom end of the piston housing.
Further, the first air valve group comprises a first main air valve 62 and a first auxiliary air valve 61; the second air valve group comprises a second main air valve 92 and a second auxiliary air valve 91; wherein, the flow area of the first main air valve 62 is larger than the flow area of the first auxiliary air valve 61; the flow area of the second main air valve 92 > the flow area of the second auxiliary air valve 91.
Further, the first main air valve 62 and the second main air valve 92 are both communicated with the side wall of the piston housing, and the communication and the closing of the flow passage of the main air valves are realized through the change of the movement position of the piston.
Further, the ratio of the diameter of said piston 7 facing the end of the stirling heat engine module to the diameter of the heat engine exhaust is between 0.05 and 1;
the ratio of the diameter of the end of the piston 7 facing the Stirling refrigerator module to the diameter of the refrigerator discharger is 0.05-1;
the mass of the piston is less than or equal to 20 kg;
the ratio of the response frequency of the first air valve bank and the second air valve bank to the operation frequency of the double-effect Stirling device is 0.5-300;
the ratio of the scavenging volume of the heat engine end of the piston to the scavenging volume of the heat engine exhaust is 0.1-3;
the ratio of the scavenging volume of the piston refrigerator end to the scavenging volume of the refrigerator ejector is 0.1-3;
the Stirling heat engine module 101 comprises a first cylinder, a heat engine discharger 3 is installed in the first cylinder, two cavities which are formed by the heat engine discharger 3 in a separating mode are formed in the first cylinder, and the two cavities are communicated with each other through a first heat regenerator 2 and a second heat exchanger 4 of a first heat exchanger 1 in sequence; the Stirling refrigeration module 102 comprises a second cylinder, a refrigerator ejector 10 is installed in the second cylinder, two cavities are formed in the second cylinder through the refrigerator ejector 10 in a separated mode and sequentially pass through the two cavities, and the two cavities are sequentially communicated with a third heat exchanger 11, a second heat regenerator 12 and a fourth heat exchanger 13.
Further, the piston 7 and the two ends have different diameters, and the two ends of the piston cylinder are matched with the two ends of the piston 7, so that a closed gas cavity 83 is formed between the piston 7 and the piston cylinder.
Further, the double-effect Stirling device comprises a pressure adjusting device 19, the pressure adjusting device comprises a compressor 191 and a valve 192, one end of the compressor 191 is communicated with the Stirling heat engine module 101 or the Stirling refrigerator module 102 through the valve, and the other end of the compressor 191 is communicated with the air storage tank 193 through the valve or communicated with the Stirling heat engine module 101 or the Stirling refrigerator module 102 through the valve.
Further, the double-effect Stirling device comprises an isothermal heat exchange device 20, the isothermal heat exchange device comprises a sliding block 201, a sliding block braking device 202 and a heat exchanger 203, the sliding block 201 is located in a moving volume cavity of the heat engine ejector 3, the refrigerator ejector 10 or the piston 7, the sliding block braking device 202 brakes the sliding block 201 to slide in the volume cavity where the sliding block 201 is located, and the heat exchanger 203 is provided with two air flow ports which are different in height from those of the connecting volume cavity.
Furthermore, the movement frequency of the slide block is 0.5 to 4 times of the movement frequency of the ejector or the piston communicated with the same volume cavity; when the volume of the volume cavity in which the sliding block 201 is located is the maximum and the ejector or the piston in the same volume cavity is static, the sliding block 201 slides under the braking of the sliding block braking device 202.
Further, a load regulation device is included, comprising a closed cavity 16, the closed cavity 16 communicating with the stirling heat engine module 101 through a valve 17.
Further, the double-effect Stirling engine comprises two double-effect Stirling devices, a piston coupling mechanism 18 is arranged between pistons of the two double-effect Stirling devices, and the piston coupling mechanism is a piston connecting rod 181 or a piston closed gas cavity connecting pipe 182 or a combined mechanism of the piston connecting rod 181 and the piston closed gas cavity connecting pipe 182.
Further, during operation, a 180-degree phase difference exists between the piston in the first double-effect Stirling device and the piston in the second double-effect Stirling device.
Furthermore, a refrigeration module in the double-effect Stirling device has multi-stage refrigeration temperature or a heat engine module has multi-stage heat source temperature.
Further, the method also comprises the following steps: the regenerator exchanges heat with a medium-temperature heat source heat exchanger in the Stirling heat engine module, and the temperature of the medium-temperature heat source heat exchanger in the Stirling heat engine module is between 40 and 180 ℃.
The invention has the beneficial effects that:
the double-effect Stirling device and the method solve the problems of control and implementation of a heat engine ejector-piston phase difference and a refrigerator ejector-piston phase difference in the conventional double-effect Stirling device, solve the problems of high piston quality and stable operation, solve the problem of high-efficiency operation of partial load, greatly improve the system efficiency and improve the reliability, and further improve the application value of the double-effect Stirling device.
Drawings
FIG. 1(a) is a diagram of a present dual effect Stirling refrigeration/heat pump system;
FIG. 1(b) is a schematic view of a conventional piston displacement curve;
FIG. 2(a) is a diagram of a dual effect Stirling apparatus according to the present invention;
FIG. 2(b) is a schematic view of the piston displacement curve of the present invention;
FIG. 3 is a schematic view of the top dead center and bottom dead center positions of the dual action Stirling apparatus of the present invention;
FIG. 4 is a schematic representation of the movement of the piston in the dual action Stirling device of the present invention;
FIG. 5 is a schematic view of the ejector brake of the dual action Stirling engine of the present invention;
FIG. 6 is a schematic view of a valve block in the dual action Stirling apparatus of the present invention;
FIG. 7 is a schematic view of a pressure regulating device in the dual action Stirling apparatus of the present invention;
FIG. 8 is a schematic view of the isothermal heat exchange unit of the dual effect Stirling engine of the present invention;
FIG. 9 is a schematic view of a load leveling device in the dual action Stirling engine of the present invention;
FIG. 10 is a schematic view of a coupling system of two double effect Stirling devices according to the second embodiment;
fig. 11 is a schematic diagram of the dual stage cold and hot ends of the dual effect stirling device of the third embodiment, wherein (a) is a schematic diagram of the dual stage cold end configuration and (b) is a schematic diagram of the dual stage hot end configuration;
FIG. 12 is a schematic view of a combined dual effect Stirling device and regenerator system according to a fourth embodiment, wherein (a) is the connection between the dual effect Stirling device and the regenerator and (b) is the connection between the regenerator and the ejector system; (c) the connection mode of the solution regenerator is adopted.
Wherein, the first heat exchanger 1; a first heat regenerator 2; a heat engine ejector 3; a second heat exchanger 4; an ejector link 5; a first piston brake device 6; a piston 7; a closed gas chamber 8; an upper air chamber 81, a lower air chamber 82; a closed gas chamber 83; a second piston brake device 9; a refrigerator ejector 10; a third heat exchanger 11; a second regenerator 12; a fourth heat exchanger 13; a stirling heat engine 101, a stirling cooler 102; a first ejector brake 14; a second ejector brake device 15; a closed cavity 16; through the valve 17; a piston coupling mechanism 18; a pressure adjusting device 19; isothermal heat exchange means 20.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clearly apparent, a double-effect stirling device and a method of the present invention are described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Example one
Fig. 2 is a graph of the double effect stirling device and piston displacement of the present invention comprising a stirling heat engine module 101, a stirling refrigeration module 102, a piston 7 and piston braking devices 6 and 9, wherein the stirling heat engine module 101 comprises a first heat exchanger 1, a first recuperator 2, a heat engine exhaust 3, a second heat exchanger 4, a first cylinder and a working fluid; the stirling refrigeration module 102 comprises a refrigerator ejector 10, a third heat exchanger 11, a second regenerator 12, a fourth heat exchanger 13, a second cylinder and a working medium. Further, the heat engine discharger 3, the refrigerator discharger 10 and the piston 7 in the double-effect Stirling device are coaxial, and the piston 7 is located between the heat engine discharger 3 and the refrigerator discharger 10. The movement of the piston 7 is controlled by the piston brakes 6 and 9 to be non-simple harmonic movement or not continuous sinusoidal movement, and the displacement curve is shown in fig. 2(b), which is different from the continuous sinusoidal movement of the piston in the prior double-effect stirling device. Fig. 3 shows the top dead center, 1/4 position, 1/2 position, 3/4 position and bottom dead center of the ejector as follows:
(a) at a point in time within the time of the heat engine displacer 3 moving from the 1/4 position to the bottom dead center and from the bottom dead center back to the 1/4 position, the braking device is actuated 1, the piston 7 moving from the top dead center position toward the bottom dead center position;
(b) at a point in time within the time of movement of the heat engine displacer 3 from the 1/4 position to the bottom dead center and from the bottom dead center back to the 1/4 position, the piston reaches near the bottom dead center position, the braking device is actuated 2, and the piston 7 stays at the bottom dead center position;
(c) at a point in time within the time of movement of the heat engine displacer 3 from the 3/4 position to the top dead center and from the top dead center back to the 3/4 position, the braking device is actuated 3, the piston 7 moving from the bottom dead center position to the top dead center position;
(d) at some point in time during which the heat engine ejector 3 moves from the 3/4 position to top dead center and back from top dead center to the 3/4 position, the piston reaches near top dead center position, the braking device acts 4, and the piston 7 stays at top dead center position.
Fig. 4 is an exemplary illustration: during the movement of the heat engine displacer 3 from the top dead center position towards the bottom dead center position (a-b), the piston 7 remains almost stationary under the action of the piston brake 6; when the heat engine ejector 3 reaches the bottom dead center position, the braking device 6 acts 1, the piston 7 moves from the top dead center position to the bottom dead center position (b-c), when the piston 7 reaches the bottom dead center position, the braking device 9 acts 2, and the piston 7 stays at the bottom dead center position; during the movement of the heat engine displacer 3 from the bottom dead center position to the top dead center position (c-d), the piston 7 remains almost stationary under the action of the piston brake 9; when the heat engine ejector 3 reaches the top dead center position, the braking device 9 acts 3, the piston 7 moves from the bottom dead center position to the top dead center position (d-e), and when the piston 7 reaches the top dead center position, the braking device 6 acts 4, and the piston 7 stays at the top dead center position.
The heat engine exhaust in current double-effect stirling cryocoolers is coupled to the piston by means of a gas spring and a mechanical spring, the piston is coupled to the cryocooler exhaust by means of a gas spring and a mechanical spring, see figure 1, this can cause a phase difference between the heat engine displacer and the refrigerator displacer, although the piston brake device can control the movement and rest of the piston, but the phase difference between the heat engine displacer and the refrigerator displacer can cause the heat engine displacer-piston phase difference and the refrigerator displacer-piston phase difference to be difficult to achieve better values, the heat engine ejector and refrigerator ejector of the present invention, therefore, is equipped with an ejector coupling mechanism, which may be a gas spring or a link, preferably, the coupling mechanism is the ejector link 5, that is, the heat engine displacer 3 and the refrigerator displacer 10 are directly connected by the displacer connecting rod 5, ensuring the same phase of the heat engine displacer and the refrigerator displacer.
Further, in order to achieve a precise control of the heat engine ejector-piston phase difference and the refrigerator ejector-piston phase difference and a high efficiency at partial load, the ejector is provided with ejector brakes 14 and 15 (see fig. 5), which are constituted by electromagnets, the brake ejector being in a state of rest by ejector brake 14 acting 1 when the ejector moves to the bottom dead center; when the ejector moves to top dead center, ejector brake 15 is actuated 2, braking the ejector to a rest condition. Further, during the actuation of the piston brake and the ejector brake, both of which depend on the moving position of the ejector and the piston, the moving part is provided with displacement monitoring means for accurate actuation of the piston brake.
The piston braking means may be: 1) an electromagnet based on electromagnetic force, wherein a piston or a cylinder is provided with an electromagnetic device, and the piston is braked at a dead point position by the electromagnetic force generated by electrifying the electromagnet; the electromagnet is powered off to eliminate electromagnetic force, so that the piston is converted from a static state into motion; 2) based on a temperature control method of a closed gas cavity, the closed gas cavity between the piston and the cylinder is heated or cooled, and the braking of the piston can be realized by adjusting the acting force of working media in the closed gas cavity acting on the piston; 3) based on a volume control method of a closed gas cavity, the magnitude of acting force of working media in the closed gas cavity acting on the piston can be adjusted by compressing or expanding the closed gas cavity between the piston and the cylinder, so that the braking of the piston is realized; 4) based on a hydraulic device, acting force is generated on the piston through liquid, the piston is braked at a dead point position, and the piston is converted from a static state into motion by eliminating the hydraulic acting force; 5) piston brake device based on pneumatic valve. Furthermore, a combination of the above methods is also possible. The piston brake device can be arranged on the piston cylinder or outside the piston cylinder, for example: the piston brake device can be arranged outside the piston cylinder and can couple the piston with the piston brake device through a connecting rod.
When the braking device is an air valve, a piston 7 is arranged in a piston cylinder of a piston structure, the piston 7 divides a piston shell into an upper air cavity 81 and a lower air cavity 82, and a closed air cavity 83 is formed between the piston 7 and the piston cylinder; the upper air chamber 81 is in communication with the stirling heat engine module 101 via the first piston brake device 6; the lower air cavity 82 is communicated with the Stirling refrigeration module 102 through the second piston brake device 9; the first piston brake device 6 comprises a first air valve group and a first closing plate 63 for closing the top end of the piston shell; the second piston brake device 9 includes a second valve set and a second sealing plate 93 for sealing the bottom end of the piston housing. The air valve can be an electromagnetic valve, an electric ball valve, a one-way valve or a thermal valve and the like. The working principle of the piston brake device based on the air valve (see figures 4 and 6) is as follows:
(a) in the process that the hot end ejector 3 moves from the upper dead point to the lower dead point, the first air valve group 6 is closed, the upper air cavity 81 is not communicated with the working medium at the hot end 101, and the piston 7 is kept almost static;
(b) when the hot end ejector 3 reaches the position near the lower dead point, the first air valve set 6 and the second air valve set 9 are opened, the upper air cavity 81 at the upper end of the piston 7 is communicated with the heat engine end 101, the piston 7 moves towards the refrigerating machine end 102 under the action of the pressure difference at the two ends, and the working medium at the refrigerating machine end 102 is compressed;
(c) in the process that the hot end ejector 3 moves from the lower dead point to the upper dead point, when the piston 7 reaches the lower dead point, the first air valve group 6 is opened, the second air valve group 9 is closed, the lower air cavity 82 is not communicated with the working medium at the end 102 of the refrigerator, and the piston 7 is kept almost still;
(d) when the hot end ejector 3 reaches the position near the top dead center, the first air valve group 6 and the second air valve group 9 are opened, the lower air cavity 82 at the lower end of the piston 7 is communicated with the end 102 of the refrigerator, and the piston 7 moves to the hot end 101 under the action of the pressure difference at the two ends to compress a working medium at the hot end 101;
(e) in the process that the hot end ejector 3 moves from the upper dead point to the lower dead point, when the piston 7 reaches the upper dead point, the first air valve set 6 is closed, the second air valve set 9 is opened, the upper air cavity 81 is not communicated with the working medium at the hot end 101, and the piston keeps almost static.
On the moving space of the piston 7 facing the heat engine end 101 and the heat engine communication space, more than or equal to 1 group of air valve groups can be arranged, for example: and 2 groups can be arranged and are respectively arranged at different positions of a flow passage where the piston bottom dead center is communicated with the heat engine end. On the communication space between the piston and the refrigerator, there can be more than or equal to 1 group of gas valve sets, for example: the two groups of the cooling device can be arranged at different positions of a flow passage communicated with the end of the refrigerator at the top dead center of the piston.
Because the pressure difference between the two ends of the air valve is large, the requirement on the area of the air valve flow passage is small in order to avoid the requirement of huge acting force when the air valve is opened, and meanwhile, the requirement on the area of the air passage is large in order to avoid overlarge flow resistance loss caused by the small flow passage, therefore, each group of air valves in the invention is composed of two air valves (see figure 6) and is divided into a main air valve and an auxiliary air valve. Further, the first air valve group comprises a first main air valve 62 and a first auxiliary air valve 61; the second air valve group comprises a second main air valve 92 and a second auxiliary air valve 91; wherein, the flow area of the first main air valve 62 is larger than the flow area of the first auxiliary air valve 61; the flow area of the second main air valve 92 > the flow area of the second auxiliary air valve 91. Further, the first main air valve 62 and the second main air valve 92 are both communicated with the side wall of the piston housing, and the communication and the closing of the flow passage of the main air valves are realized through the change of the movement position of the piston. Therefore, when the piston brake is applied, the auxiliary air valve is opened, the piston moves under the pressure difference between the two ends, and when the piston moves to the communication port of the main air valve on the cylinder wall, the main air valve is opened. Since the gas valve response speed affects the frequency of the dual effect stirling device, the ratio of the response frequency of the valves 61 and 91 to the operating frequency of the dual effect stirling device is between 0.5 and 300. Further, the piston is provided with a displacement monitoring device for accurately controlling the opening and closing of the air valve group.
The work output during expansion of the working medium in the heat engine is generally not matched with the work required during compression of the working medium in the refrigerator. For the purpose of matching work, the piston ends have different diameters, and a closed gas chamber 83 is provided between the piston cylinders. Further, the closed gas chamber 83 is not in communication with the working fluid in the heat engine and the refrigerant engine except for leakage when the piston moves to the top dead center or the bottom dead center position (see fig. 4(b), (d)).
The pressure differential between the hot side 101 and the cold side 102 will create a force on the piston. During the time when the piston 7 is held stationary by the piston brake 6 during the movement of the heat engine displacer 3 from the top dead centre to the bottom dead centre, the force on the piston 7 will gradually increase, because the pressure difference between the two ends of the heat engine 101 and the refrigerating machine 102 is large (up to 3-5MPa) in the operation process of the double-effect Stirling device, in order to solve the problems of failure of the braking device under large pressure difference and small space and avoid overhigh acceleration of the piston caused by large pressure difference, the diameter of the piston 7 facing to a heat engine end 101 is smaller than that of a heat engine ejector 3, the diameter of the piston 7 facing to a refrigerating machine end 102 is smaller than that of a refrigerating machine ejector 10, furthermore, the ratio of the diameter of the piston 7 facing to the Stirling heat engine module end 101 to that of the heat engine ejector 3 is between 0.05 and 1, and the ratio of the diameter of the piston 7 facing to the Stirling refrigerating machine module end 102 to that of the refrigerating machine ejector 10 is between 0.05 and 1. Furthermore, in order to reduce the influence of the excessive inertia force of the piston 7 on the acting force of the piston brake, the piston mass is less than or equal to 20 kg.
Further, the double effect stirling device further comprises:
the ratio of the scavenging volume of the heat engine end of the piston to the scavenging volume of the heat engine exhaust is 0.1-3;
the ratio of the scavenging volume at the end of the piston refrigerator to the scavenging volume of the ejector of the refrigerator is 0.1-3.
Further, in order to realize load matching and work matching, the double-effect Stirling device comprises a pressure adjusting device 19, see FIG. 7, wherein the pressure adjusting device 19 comprises a compressor 191 and a valve 192, one end of the compressor 191 is communicated with the Stirling heat engine module 101 or the Stirling cooler module 102 through the valve, and the other end of the compressor 191 is communicated with the air storage tank 193 through the valve or is communicated with the Stirling heat engine module 101 or the Stirling cooler module 102 through the valve. Fig. 7 is an example only, and one end of the compressor 191 communicates with the stirling heat engine module 101 through the valve 192, and the other end communicates with the air reservoir 193, and the air reservoir 193 communicates with the stirling cooler module 102 through the valve 192.
Further, in order to balance the pressure in the system in the operation process, the double-effect Stirling device further comprises a communication valve for communicating working media in the Sterling heat engine module 101 and the Stirling refrigeration module 102 in at least one part of the operation process.
Further, the double-effect Stirling device comprises an isothermal heat exchange device 20, the isothermal heat exchange device comprises a sliding block 201, a sliding block braking device 202 and a heat exchanger 203, the sliding block 201 is located in a moving volume cavity of the heat engine ejector 3, the refrigerator ejector 10 or the piston 7, the sliding block braking device 202 brakes the sliding block 201 to slide in a connecting volume cavity of the heat exchanger 203, the heat exchanger 203 is provided with two air flow ports with different heights from the connecting volume cavity, one air flow port is located at the bottom of a sliding block stroke, and the other air flow port is located at the upper part of the sliding block stroke. The slider stopper 202 is composed of an electromagnetic device and a spring. The working process of the isothermal heat exchange device 20 is described below by taking fig. 8 as an example:
the fourth heat exchanger 13 adopts the isothermal heat exchange device 20, the sliding block 201 is located in the moving volume cavity of the refrigerator ejector 10, and the sliding block braking device 202 can be installed on the refrigerator ejector 10 or at the bottom of the moving volume cavity of the refrigerator ejector 10, in this case, the sliding block braking device 202 is installed at the bottom of the moving volume cavity of the refrigerator ejector 10. When the ejector 10 of the refrigerator moves upwards, the sliding block 201 and the sliding block braking device 202 are kept tightly attached and still; when the refrigerator ejector 10 reaches the top dead center (fig. 8 (a)), that is, when the volume of the volume chamber in which the slider 201 is located is the maximum, the refrigerator ejector 10 is in a stationary state under the action of the ejector braking device 15, the slider 201 moves upward under the braking of the slider braking device 202, and pushes the working medium in the volume chamber to exchange heat in the heat exchanger 203; when the sliding block 201 is near the top dead center, the ejector 10 of the refrigerator moves downwards to push the sliding block 201 to move downwards together, and meanwhile, the working medium in the volume cavity is pushed to exchange heat again in the heat exchanger 203; when the slide 201 reaches the lower dead point, the slide 201 is kept still under the brake of the slide brake 202. Compared with a heat exchanger without the isothermal heat exchange device 20, the heat exchange times of the working medium in the isothermal heat exchange device 20 are increased, and the working medium approaches to an isothermal process.
It should be noted that fig. 8 is only a schematic illustration, and the first recuperator 1, the second heat exchanger 4, and the third heat exchanger 11 may also partially or completely employ the isothermal heat exchange device 20.
The movement speed of the slide block can be the same as or different from that of the ejector or the piston communicated with the same volume cavity, and furthermore, the movement frequency of the slide block is 0.5-4 times that of the ejector or the piston communicated with the same volume cavity.
Further, in order to realize the matching between the output work of the heat engine and the output work of the refrigerating machine, the refrigerating machine further comprises a load adjusting device, and the load adjusting device is composed of a closed cavity 16 and a valve 17 (see fig. 9). The closed cavity (see 16 in figure 9) is communicated with the Stirling heat engine through a valve (see 17 in figure 9), and the communication between the closed cavity and the end of the Stirling heat engine is opened or closed according to the output load requirement. Preferably, the load adjusting means comprises a plurality of sets of closed chambers and valves, as shown in fig. 9, consisting of two sets of closed chambers and valves.
Further, the piston and the ejector act as a mass spring system, and the piston and the ejector are provided with springs for the reciprocating movement.
Example two
The two double-effect Stirling device coupling systems are composed of two double-effect Stirling devices, and each double-effect Stirling device comprises a Stirling heat engine module 101, a Stirling refrigeration module 102 and a piston structure. A piston coupling mechanism 18 is arranged between the pistons of the two double-effect Stirling devices, and the piston coupling mechanism can be a piston connecting rod 181 or a piston closed gas cavity connecting pipe 182 or a combined mechanism of an ejector connecting rod and the piston closed gas cavity connecting pipe. Fig. 10 shows a combination mechanism of a piston connecting rod 181 fixed on a piston or a piston closed gas cavity connecting pipe 182, the two pistons are directly coupled through the piston connecting rod, and the piston closed gas cavity connecting pipe 182 is communicated with a closed gas cavity between the piston and a cylinder to realize the movement of a working medium in the two closed cavities.
In the operation process of the two double-effect Stirling device coupling systems, a 180-degree phase difference exists between a piston in the first double-effect Stirling device and a piston in the second double-effect Stirling device, namely in the process that the piston in the first double-effect Stirling device moves from a heat engine end to a refrigerating machine end, the piston in the second double-effect Stirling device moves from the refrigerating machine end to the heat engine end. Similarly, the phase difference of 180 degrees also exists between the ejector in the first double-effect Stirling device and the ejector in the second double-effect Stirling device, namely when the volume of the hot end volume cavity of the heat engine in the first double-effect Stirling device is at the minimum, the volume of the hot end volume cavity of the heat engine in the second double-effect Stirling device is at the maximum. Therefore, the two double-effect Stirling devices have a phase difference of 180 degrees in the operation process of the two double-effect Stirling device coupling systems.
When the refrigerating machine ends of the two double-effect Stirling device coupling systems are oppositely arranged, as shown in a figure 10(a), the refrigerating machine cold end volume cavities of the two devices are separated by a partition plate; when the heat engine ends of the two double-effect Stirling device coupling systems are oppositely arranged, as shown in a figure 10(b), the heat engine hot end volume cavities of the two devices are separated by a partition plate. The ejectors of the two double effect stirling devices may be directly connected or disconnected by a linkage.
EXAMPLE III
The stirling heat engine module 101 or the stirling cooler module 102 of the double effect stirling device may be multi-stage.
Fig. 11(a) shows that the dual-effect stirling device includes a second-stage stirling refrigeration module including an ejector, a regenerator, and a heat exchanger for the second-stage stirling refrigeration module, the ejector of the second-stage stirling refrigeration module being coaxial with the ejector of the first-stage stirling refrigeration module. Further, the second Stirling refrigeration module and the first stage Stirling refrigeration module have different refrigeration temperatures. Further, the double-effect Stirling device further comprises an N-stage Stirling refrigeration module.
As shown in fig. 11(b), the dual-effect stirling device comprises a second-stage stirling heat engine module, the second-stage stirling heat engine module comprises an ejector, a regenerator and a heat exchanger for the second-stage stirling heat engine module, and the ejector of the second-stage stirling heat engine module is coaxial with the ejector of the first-stage stirling heat engine module. Further, the second-stage stirling heat engine module has a different heat source temperature than the first-stage stirling heat engine module. Further, the double effect stirling device further comprises an nth stage stirling heat engine module.
Example four
The double-effect stirling device further comprises a regenerator and exchanges heat with the medium-temperature heat source heat exchanger in the stirling heat engine module, and as shown in fig. 12(a), the temperature of the medium-temperature heat source heat exchanger in the stirling heat engine module is 40-180 ℃. Further, the regenerator is a solution regenerator, a rotary wheel adsorption regenerator, or a regenerator of an ejector system. Fig. 12(b) illustrates an injection system as an example, in which a regenerator exchanges heat with a medium-temperature heat source heat exchanger in a heat engine module, liquid flowing from a pump is heated in the regenerator to become high-temperature high-pressure steam, and then the high-temperature high-pressure steam is sequentially connected with an ejector and a condenser, a part of the liquid coming out of the condenser is input to the regenerator through the pump, and a part of the liquid passes through a throttle valve and flows to the ejector through an evaporator. Fig. 12(c) illustrates the solution regeneration as an example, the dilute solution flows into the regenerator and is then heated in the regenerator to become the concentrated solution. In the process, the regeneration working medium of the regenerator can directly exchange heat with the medium-temperature heat source heat exchanger in the heat engine module, and can also indirectly exchange heat through a heat exchange medium.
The double-effect Stirling device and the method achieve braking of the piston, solve the problems of phase difference matching, expansion work-compression work matching and the like caused by piston braking, improve system efficiency and reduce piston quality requirements.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the present invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (19)
1. A method of controlling operation of a dual action stirling device, the device having a heat engine displacer reciprocating within a heat engine cylinder, a refrigerator displacer reciprocating within a refrigerator cylinder and a piston reciprocating within a piston cylinder, wherein the heat engine displacer has a top dead center position and a bottom dead center position within the heat engine cylinder, the refrigerator displacer has a top dead center position and a bottom dead center position within the refrigerator cylinder, the piston has a top dead center position and a bottom dead center position within the piston cylinder, the method of controlling operation comprising:
and braking the piston to move from the piston top dead center position to the piston bottom dead center position and the piston to move from the piston bottom dead center position to the piston top dead center position, and removing the coupling relation between the piston and the heat engine ejector and the refrigerator ejector.
2. The method of controlling operation of a dual action stirling device of claim 1 comprising the steps of:
a) during the time that the heat engine displacer moves from the 1/4 position to the bottom dead center and from the bottom dead center back to the 1/4 position, the braking device acts to move the piston from the top dead center position to the bottom dead center position;
b) during the time when the heat engine ejector moves from the 1/4 position to the bottom dead center and returns from the bottom dead center to the 1/4 position, the piston reaches the position near the bottom dead center, and the braking device acts to enable the piston to stay at the bottom dead center;
c) during the time that the heat engine displacer moves from the 3/4 position to the top dead center and from the top dead center back to the 3/4 position, the braking device acts to move the piston from the bottom dead center position to the top dead center position;
d) during the time that the heat engine displacer moves from the 3/4 position to top dead center and back from top dead center to the 3/4 position, the piston reaches near top dead center position and the braking device acts to cause the piston to stay at the top dead center position.
3. The utility model provides a double-effect Stirling device, includes Stirling heat engine module (101), Stirling refrigeration module (102) and piston structure, installs piston (7) in piston structure's the piston cylinder, and piston (7) are divided piston housing for last air cavity (81) and lower air cavity (82), goes up air cavity (81) and Stirling heat engine module (101) intercommunication, and lower air cavity (82) and Stirling refrigeration module (102) intercommunication, its characterized in that, the piston has piston arresting gear (6 and 9), the braking the motion of piston in piston cylinder.
4. The dual effect stirling device of claim 3, wherein an ejector coupling mechanism is mounted between the heat engine ejector (3) within the stirling heat engine module (101) and the cold ejector (10) within the stirling cooler (102), the coupling mechanism being an ejector link (5).
5. The dual action stirling device of claim 3, wherein the ejector is provided with an ejector brake (14 and 15) which brakes the ejector in a dead centre position for a portion of the time when the ejector is in a top dead centre or bottom dead centre position.
6. The dual effect stirling device of claim 3, wherein the piston braking device comprises a gas valve or an electromagnet.
7. The dual effect stirling device of claim 6, wherein the upper air chamber (81) communicates with the stirling heat engine module (101) through the first piston brake device (6) when the brake device is an air valve; the lower air cavity (82) is communicated with the Stirling refrigeration module (102) through a second piston brake device (9); the first piston brake device (6) comprises a first air valve group and a first closing plate (63) for closing the top end of the piston shell; the second piston braking device (9) comprises a second air valve group and a second closing plate (93) closing the bottom end of the piston shell.
8. The dual effect stirling device of claim 7, wherein the first gas valve set comprises a first main gas valve (62) and a first auxiliary gas valve (61); the second air valve group comprises a second main air valve (92) and a second auxiliary air valve (91); wherein the flow area of the first main air valve (62) is larger than the flow area of the first auxiliary air valve (61); the flow area of the second main air valve (92) is larger than the flow area of the second auxiliary air valve (91).
9. The dual effect stirling device of claim 8, wherein the first and second main gas valves (62, 92) are each in communication with a side wall of the piston housing, the communication and closing of the main gas valve flow passages being achieved by a change in the position of movement of the piston.
10. The double-effect stirling device of claim 3, wherein the ratio between the diameter of the piston (7) facing the stirling heat engine module end and the heat engine displacer diameter is between 0.05 and 2;
the ratio of the diameter of the end of the piston (7) facing the Stirling refrigerator module to the diameter of the refrigerator discharger is 0.05-2;
the mass of the piston is less than or equal to 20 kg;
the ratio of the response frequency of the first air valve bank and the second air valve bank to the operation frequency of the double-effect Stirling device is 0.5-300;
the ratio of the scavenging volume of the heat engine end of the piston to the scavenging volume of the heat engine exhaust is 0.1-3;
the ratio of the scavenging volume of the piston refrigerator end to the scavenging volume of the refrigerator ejector is 0.1-3;
the Stirling heat engine module (101) comprises a first cylinder, a heat engine discharger (3) is installed in the first cylinder, two cavities which are formed by the heat engine discharger (3) in a separated mode are arranged in the first cylinder, and the two cavities are communicated with a first heat exchanger (1), a first heat regenerator (2) and a second heat exchanger (4) in sequence; the Stirling refrigeration module (102) comprises a second cylinder, a refrigerator ejector (10) is installed in the second cylinder, the second cylinder is internally divided by the refrigerator ejector (10) to form two cavities which are communicated in sequence, and the two cavities are communicated in sequence through a third heat exchanger (11), a second heat regenerator (12) and a fourth heat exchanger (13).
11. The dual effect stirling device of claim 3, wherein the piston (7) and the two ends are of different diameters, the two ends of the piston cylinder matching the two ends of the piston (7) such that a closed gas cavity (83) is formed between the piston (7) and the piston cylinder.
12. The dual effect stirling device of claim 3, comprising a pressure regulating device (19) comprising a compressor (191) and a valve (192), one end of the compressor (191) being in valve communication with the stirling heat engine module (101) or the stirling cooler module (102) and the other end being in valve communication with the air reservoir (193) or with the stirling heat engine module (101) or the stirling cooler module (102).
13. The double-effect Stirling device according to claim 3, comprising an isothermal heat exchange device (20) comprising a slider (201), a slider braking device (202) and a heat exchanger (203), wherein the slider (201) is located in a volume chamber in which the heat engine ejector (3) or the refrigerator ejector (10) or the piston (7) moves, the slider braking device (202) brakes the slider (201) to slide in the volume chamber in which the slider (201) is located, and the heat exchanger (203) has two air flow ports with different heights from those of the connecting volume chamber.
14. The dual effect stirling device of claim 13, wherein the slider motion frequency is 0.5 to 4 times the frequency of the ejector or piston motion in the communicating same volume chamber; when the volume of the volume cavity in which the sliding block (201) is located is maximum and the ejector or the piston in the same volume cavity is static, the sliding block (201) slides under the braking of the sliding block braking device (202).
15. The dual-effect stirling device of claim 3, comprising a load regulation device comprising a closed cavity (16), the closed cavity (16) communicating with the stirling heat engine module (101) through a valve (17).
16. The dual effect stirling device of any one of claims 3 to 15 comprising two dual effect stirling devices, a piston coupling mechanism (18) being provided between the pistons of the two dual effect stirling devices, the piston coupling mechanism being a piston connecting rod 181 or a piston enclosed gas chamber connecting tube 182 or a combination of a piston connecting rod 181 and a piston enclosed gas chamber connecting tube 182.
17. The dual effect stirling device of claim 16 comprising the piston of the first dual effect stirling device being 180 ° out of phase with the piston of the second dual effect stirling device during operation.
18. The dual effect stirling device of any one of claims 3 to 15 wherein the refrigeration module is at a multi-stage refrigeration temperature or the heat engine module is at a multi-stage heat source temperature.
19. The dual action stirling device of any one of claims 3 to 15, further comprising: the regenerator exchanges heat with a medium-temperature heat source heat exchanger in the Stirling heat engine module, and the temperature of the medium-temperature heat source heat exchanger in the Stirling heat engine module is between 40 and 180 ℃.
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