CN114993067B - Marine anti-swing water tank and parameter design method thereof - Google Patents
Marine anti-swing water tank and parameter design method thereof Download PDFInfo
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 127
- 238000000034 method Methods 0.000 title claims abstract description 18
- 238000013461 design Methods 0.000 title claims abstract description 12
- 238000009833 condensation Methods 0.000 claims abstract description 37
- 230000005494 condensation Effects 0.000 claims abstract description 37
- 238000003860 storage Methods 0.000 claims abstract description 35
- 239000007788 liquid Substances 0.000 claims description 22
- 238000010438 heat treatment Methods 0.000 claims description 19
- 238000005485 electric heating Methods 0.000 claims description 7
- 230000007246 mechanism Effects 0.000 claims description 7
- 230000008569 process Effects 0.000 claims description 5
- 238000004781 supercooling Methods 0.000 claims description 5
- 238000007789 sealing Methods 0.000 abstract description 10
- 230000005484 gravity Effects 0.000 abstract description 7
- 230000000694 effects Effects 0.000 abstract description 6
- 239000007789 gas Substances 0.000 description 15
- 230000009471 action Effects 0.000 description 8
- 238000004891 communication Methods 0.000 description 7
- 230000001133 acceleration Effects 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000011261 inert gas Substances 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B7/00—Combinations of two or more condensers, e.g. provision of reserve condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient
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Abstract
The invention relates to the technical field of water level control of marine steam power systems, in particular to a marine anti-swing water tank and a parameter design method thereof, wherein the marine anti-swing water tank comprises the following components: the condenser comprises a box body, two condensers and two check cavities. A water outlet cavity, a water condensation cavity and an air storage cavity which are communicated in sequence are arranged in the box body, and the air storage cavity is positioned above the water condensation cavity and used for storing a choked flow working medium; the two condensers are arranged above the box body, each condenser is communicated with a communicating pipeline extending into the water condensation cavity, and an outlet of each communicating pipeline and the condenser correspondingly communicated with the communicating pipeline are respectively positioned at two ends of the water condensation cavity; two non return cavities are respectively arranged at two ends of the water condensation cavity and communicated with the water condensation cavity, the width of the non return cavity is smaller than that of the water condensation cavity, and the outlet of the communicating pipeline extends into the non return cavity. The problem that in the prior art, the check sealing pressure of the stop return valve is insufficient, the required sealing pressure of the check valve is difficult to maintain only by means of gravity pressure drop, and the check effect is not good can be solved.
Description
Technical Field
The invention relates to the technical field of water level control of marine steam power systems, in particular to a marine anti-swing water tank and a parameter design method thereof.
Background
In a steam power system for a ship, a condenser is generally arranged on each of a left side and a right side, and condensed water of the two condensers is collected to a condensed water tank through a hot well and then is pumped away by a condensed water pump.
However, under the condition of swinging/tilting, the condensed water in the condensed water tank and the condenser hot well with a higher position can flow backwards into the condenser with a lower position under the action of gravity to submerge the heat transfer pipe of the condenser, so that the effective heat exchange area is reduced, and the performance of the condenser is influenced, thereby the operation of a steam power system is influenced.
To solve the above problems, a check valve is adopted in the prior art to prevent the reverse flow of the condensed water. The current check valve solution suffers from three problems: the check sealing pressure of the check valve is insufficient, the sealing pressure required by the check valve is difficult to maintain only by means of gravity pressure drop, and the check effect is poor; the resistance of the check valve is too large, which affects the water discharge of a hot well and causes the pressure at the inlet of the condensate pump to be too low, thereby generating cavitation and affecting the safe operation of the condensate pump; due to the limitation of marine space, the check valve can only be arranged in the water tank, and the maintenance is extremely difficult.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a marine anti-swing water tank and a parameter design method thereof, which can solve the problems that in the prior art, the check sealing pressure of a check valve is not enough, the sealing pressure required by the check valve is difficult to maintain only by means of gravity pressure drop, and the check effect is not good.
In order to achieve the above purposes, the technical scheme adopted by the invention is as follows:
the invention provides a marine anti-swing water tank, comprising:
the tank body is internally provided with a water outlet cavity, a water condensation cavity and an air storage cavity which are sequentially communicated, wherein the air storage cavity is positioned above the water condensation cavity and is used for storing a flow-resisting working medium;
the two condensers are arranged above the box body, each condenser is communicated with a communicating pipeline extending into the water condensation cavity, and an outlet of each communicating pipeline and the corresponding communicated condenser are respectively positioned at two ends of the water condensation cavity;
two non return cavities are respectively arranged at two ends of the condensed water cavity and communicated with the condensed water cavity, the width of the non return cavity is smaller than that of the condensed water cavity, and the outlet of the communicating pipeline extends into the non return cavities.
In some optional schemes, the outermost side end face of the check cavity forms an inclined surface inclined towards the outer side from the bottom face to the top face, and the outlet of the communication pipeline is positioned on the side close to the top face.
In some optional schemes, an electric heating mechanism is arranged in the check cavity and comprises two electric heaters which are respectively positioned at the upper sides of the two check cavities.
In some optional schemes, the check cavity is also communicated with a delivery pipeline for delivering steam to the check cavity, or a steam heating pipeline extending into the check cavity.
In some optional schemes, the communication pipeline includes a hot well and a non-return pipe which are communicated with each other, a connecting end of the hot well and the non-return pipe extends into the water condensation cavity, the other end of the hot well is communicated with the condenser, and an outlet of the non-return pipe and the condenser are respectively located at two ends of the water condensation cavity.
In some alternatives, the air reservoir has a semi-circular cross-section.
In some optional schemes, the top of the air storage cavity is provided with an air charging and exhausting valve.
On the other hand, the invention also provides a parameter design method of the marine anti-sway water tank, which is used for designing the marine anti-sway water tank and comprises the following steps:
determining the length of a communicating pipeline in the water condensation cavity in the horizontal direction according to the maximum inclination angle of the ship body and the maximum liquid level height difference of the two condensers, or the swing amplitude, the swing period and the maximum swing liquid level height difference of the two condensers;
and determining the volume of the gas storage cavity according to the length of the horizontal direction of the communication pipeline positioned in the condensed water cavity and the section shape of the non-return cavity.
In some alternatives, during a lean condition,according to the formula
Determining the length of the communicating pipe in the condensed water cavity in the horizontal directionLWherein, in the process,
is the maximum inclination angle of the ship body,
is the maximum liquid level head of the two condensers.
In some optional schemes, when steam is used as a flow-resisting working medium, the working temperature of the electric heaters in the two check cavities is determined according to the maximum inclination angle of the ship body, the maximum liquid level height difference of the two condensers, the section shapes of the check cavities, the condensate supercooling degree and the operating pressure of the condensers.
Compared with the prior art, the invention has the advantages that: when the ship body inclines/swings left and right, the flow-resisting working medium in the gas storage cavity is gathered to the non-return cavity under the action of buoyancy, the liquid level is controlled below the outlets of the communicating pipelines, and because the outlet of each communicating pipeline and the condenser corresponding to and communicated with the outlet of each communicating pipeline are respectively positioned at the two ends of the condensate cavity, condensate in the condensate cavity is blocked and flows back to the condenser through the non-return cavity, so that the non-return function of the condensate is realized. The problems that the check valve used in the prior art has insufficient check sealing pressure, the sealing pressure required by the check valve is difficult to maintain only by means of gravity pressure drop, and the check effect is poor can be solved; the problem that the resistance of the check valve is too large, the drainage quantity of a hot well is influenced, and the pressure at the inlet of the condensate pump is too low, so that cavitation is generated and the safe operation of the condensate pump is influenced is solved; and the check valve is limited by the space for the ship and can only be arranged in the water tank, so that the maintenance is extremely difficult.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic structural diagram of a marine anti-sway water tank in an embodiment of the invention;
FIG. 2 is a schematic diagram of a tilted anti-sway water tank for a ship according to an embodiment of the present invention;
fig. 3 is a schematic top view of a marine anti-sway water tank in an embodiment of the invention.
In the figure: 1. a box body; 11. a water outlet cavity; 12. a water condensation cavity; 13. a gas storage cavity; 14. an inflation and exhaust valve; 2. a condenser; 3. a communicating pipe; 31. a hot well; 32. a non-return pipe; 4. a check cavity; 5. a delivery conduit; 6. an electrical heating mechanism.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
Embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.
As shown in fig. 1, the present invention provides a tank for preventing rolling of a ship, comprising: the condenser comprises a box body 1, two condensers 2 and two check cavities 4. A water outlet cavity 11, a water condensation cavity 12 and an air storage cavity 13 which are sequentially communicated are arranged in the box body 1, wherein the air storage cavity 13 is positioned above the water condensation cavity 12 and is used for storing a flow-resisting working medium; the two condensers 2 are arranged above the box body 1, each condenser 2 is communicated with a communicating pipeline 3 extending into the water condensation cavity 12, and an outlet of each communicating pipeline 3 and the corresponding communicated condenser 2 are respectively positioned at two ends of the water condensation cavity 12; two non return chamber 4 establish respectively at the both ends of water chamber 12 to with water chamber 12 intercommunication congeals, the width in non return chamber 4 is less than the width in water chamber 12, and the export of intercommunication pipeline 3 stretches into in the non return chamber 4.
Referring to fig. 1-3, during normal operation of the system, condensed water of two condensers 2 flows into the non-return cavity through the communication pipeline 3 extending into the water condensation cavity 12, converges into the water condensation cavity 12, and is discharged through the water outlet cavity 11, when the ship body inclines/swings, a right inclination is taken as an example, the state of the box body 1 in the right inclination is shown in fig. 2, a flow-resisting working medium in the gas storage cavity 13 is converged to the non-return cavity 4 on the right side under the action of buoyancy, and the condensed water in the water condensation cavity 12 is blocked to flow back to the condenser 2 on the left side through the non-return cavity 4 on the right side, so that the non-return function of the condensed water is realized.
In this example, go out water cavity 11, congeal water cavity 12 and gas storage cavity 13 and set gradually from last to down, and gas storage cavity 13 is located the middle part of congealing water cavity 12, and when the hull left and right sides slope swayd, the choked flow working medium in the gas storage cavity 13 assembles the non return chamber 4 to both sides under the buoyancy, with the liquid level control below the export of intercommunication pipeline 3, blocks the water that congeals in the congeals water cavity 12 and passes through non return chamber 4 and flow backwards to condenser 2 to realize congealing water non return function. In addition, the gas storage cavity 13 is located in the middle of the water condensation cavity 12, and therefore the flow resisting working medium in the gas storage cavity 13 can be favorably converged to the check cavities 4 on the two sides under the action of buoyancy. Because the width of non return chamber 4 is less than the width of condensate chamber 12, the export of intercommunication pipeline 3 stretches into in non return chamber 4, is favorable to the choked flow working medium in the gas storage chamber 13 to assemble under the buoyancy to form the choked flow behind non return chamber 4, reducible gas storage chamber 13 stores the demand of choked flow working medium. The flow-resisting working medium can adopt inert gas or water vapor.
In this example, the outlet of the communication pipe 3 connected to the left condenser 2 as shown in fig. 1 extends into the right check chamber 4 as shown in fig. 1. The length of the water condensation cavity 12 is larger than that of the water outlet cavity 11.
In some optional implementations, the outermost side end face of the check cavity 4 forms an inclined surface inclined outward from the bottom face to the top face, and the outlet of the communication duct 3 is located on the side close to the top face.
In this implementation, the inclined plane that inclines to the outside is formed from the bottom surface to the top surface with the outermost side terminal surface of non return chamber 4, reducible storage to gas storage chamber 13 chokes the flow demand of working medium, and less chokes the flow working medium just can fill non return chamber 4, plays chokes the flow effect. In addition, the outlet of the communicating pipeline 3 is arranged on one side close to the top surface, so that the requirement for storing the choked flow working medium in the gas storage cavity 13 can be further reduced.
In some alternative implementations, an electrical heating mechanism 6 is provided within check cavity 4, which is disposed within check cavity 4. The electric heating mechanism 6 comprises two electric heaters which are respectively positioned at the upper sides of the two check cavities 4.
In this embodiment, when steam is used as the flow-resistant working medium, the water in the non-return cavity 4 can be heated to generate steam, and the steam is used as the flow-resistant working medium to form a cavity in the non-return cavity 4 for blocking the condensed water in the condensed water cavity 12 from flowing back to the condenser 2 through the non-return cavity 4. In this example, the electric heating mechanism 6 comprises two electric heaters respectively located at the upper sides of the two check cavities 4, and the electric heaters heat condensed water in the check cavities 4 to form steam, so that an air cavity is formed conveniently and quickly.
In some optional implementations, the check cavity 4 is further communicated with a delivery pipe 5 for delivering steam to the check cavity 4, or a steam heating pipe extending into the check cavity 4.
When steam is used as a flow-resisting working medium, hot steam can be conveyed into the non-return cavity 4 through the conveying pipeline 5 communicated with the non-return cavity 4 to form a cavity for blocking condensed water in the condensed water cavity 12 from flowing back to the condenser 2 through the non-return cavity 4, in the embodiment, a control valve is further arranged on the conveying pipeline 5 to control the time and the volume of the conveying pipeline 5 for filling the non-return cavity 4 with the hot steam.
In addition, a circulating steam heating pipeline is arranged in the non-return cavity 4 and used for heating water in the non-return cavity 4 to generate steam, the steam is used as a flow-resisting working medium, and a cavity for blocking condensate in the condensate cavity 12 from flowing back to the condenser 2 through the non-return cavity 4 is formed in the non-return cavity 4.
In some optional implementations, the communication pipeline 3 includes a thermal well 31 and a check pipe 32 which are communicated with each other, a connecting end of the thermal well 31 and the check pipe 32 extends into the water condensation chamber 12, the other end of the thermal well 31 is communicated with the condenser 2, and an outlet of the check pipe 32 and the condenser 2 are respectively located at two ends of the water condensation chamber 12.
In the embodiment in which the condenser 2 projects into the condensation chamber 12 through the hot well 31, the non-return tube 32 is arranged horizontally in this case, and the outlet of the non-return tube 32 is located in the non-return chamber 4 on the side close to the top face.
In some alternative implementations, the air reservoir 13 is semi-circular in cross-section.
In the present embodiment, the air storage chamber 13 with a semicircular cross section is opened downwards for accommodating more flow-resisting working medium. And when the ship body runs stably, the choked flow working medium can be concentrated in the air storage cavity 13.
In some alternative implementations, the top of the air storage chamber 13 is provided with an air charging and discharging valve 14.
In this embodiment, the top of the air storage cavity 13 is provided with the inflation/exhaust valve 14, so that a choked flow working medium can be conveniently filled into the air storage cavity 13, and a part of the choked flow working medium is discharged when the pressure of the choked flow working medium is too high.
On the other hand, the invention also provides a parameter design method of the marine anti-sway water tank, which is used for designing the marine anti-sway water tank and comprises the following steps:
s1: and determining the length of the horizontal direction of the communicating pipeline 3 in the water condensation cavity 12 according to the maximum inclination angle of the ship body and the maximum liquid level height difference of the two condensers 2, or the swing amplitude, the swing period and the maximum swing liquid level height difference of the two condensers 2.
Under the inclined working condition, the length of the horizontal direction of the communicating pipeline 3 in the water condensation cavity 12 is determined according to the maximum inclined angle of the ship body and the maximum liquid level height difference of the two condensers 2.
In particular, according to the formula
Determining the horizontal length of the connecting pipe 3 in the condensation chamber 12LWherein
is the maximum inclination angle of the ship body,
is the maximum liquid level head of the two condensers 2.
The solving principle is as follows:
under the inclined working condition, the maximum liquid level difference of the two condensers 2
Generated driving force
Comprises the following steps:
check pressure drop of horizontal direction communicating pipe 3 in condensed water cavity 12 filled with flow-resisting working medium
Comprises the following steps:
when the check pressure drop is greater than the driving force, the check is achieved, namely:
to obtain
To ensure that the above relation holds, the design length of L should be longer than the horizontal distance between the two condensers 2
Wherein
is the maximum liquid level head of the two condensers 2,
is the density of the condensed water, g is the acceleration of gravity,
is the maximum inclination angle of the ship body,
is the horizontal distance between the two condensers 2.
Under the working condition of swinging, the length of the horizontal direction of the communicating pipeline 3 in the water condensation cavity 12 is determined according to the swinging amplitude, the swinging period and the maximum swinging liquid level height difference of the two condensers 2.
S2: the volume of the gas storage cavity 13 is determined according to the length of the horizontal direction of the communicating pipe 3 positioned in the water condensation cavity 12 and the sectional shape of the check cavity 4.
Under the inclined working condition, the volume of the air storage cavity 13 is as follows:
wherein
the cross-sectional area of the return tube 32,
in order to be an ineffective air volume,Lnamely the length of the check pipe,
h is the inclination angle of the ship body
At the angle, the height of the outlet of the check tube 32 from the top of the check cavity 4,
the angle of inclination of the hull is
Angle, cross-sectional area of the space above the outlet of the check tube 32.
Under the working condition of swinging, the non-return conditions are as follows:
wherein,
additional pressure drop due to the inertial forces of the attachment created for the rocking motion.
lThe length of the flow path from the liquid level in the hot well 31 to the outlet of the check pipe 32;
wherein,
in the form of an angular acceleration, the acceleration,
，yandzrespectively establishing longitudinal (Y) and vertical (Z) coordinates in a coordinate system by using the central axis of the water tank, taking j and k as vector units of corresponding directions, according to a non-return condition and a calculation method under an inclined condition, and under a swing working condition, the expression of the gas storage cavity 13 is
Wherein
in order to be able to set the amplitude of the oscillation,
in order to have a period of the swing,
is the maximum swing level head of the two condensers 2,
is the inertial acceleration of the ship, t is the time,
is the velocity of the water in the connecting channel 3 relative to the tube wall.
In some optional embodiments, when steam is used as the flow-resisting working medium, the working temperature of the electric heater arranged in the two check cavities 4 is determined according to the maximum inclination angle of the ship body, the maximum liquid level height difference of the two condensers 2, the cross-sectional shape of the check cavities 4, the supercooling degree of condensed water and the operating pressure of the condensers.
In this embodiment, there is a device with extremely strict requirements for water quality in the steam-water circulation loop, and when inert gas is not allowed to be used, the device can be heated by an electric heater and steam is heated to generate steam, or steam is directly injected to form a steam cavity to block a backflow channel, so that non-return is realized. The designed working temperature of the electric heater or steam heating can meet the requirement of normal steam production at the moment of backflow, and the designed temperature T and the inclined angle
Maximum difference in liquid level height between left and right side condensers
Cross sectional area of water tank
Super cooling degree of condensed water
Operating pressure of condenser
In connection with, i.e. with
Steam condensation power in check pipe
Comprises the following steps:
wherein,R 1 the total thermal resistance of the condensing portion of the return pipe 32;
heating power of constant temperature heater
Comprises the following steps:
wherein the heating surface of the electric heater isA 2 Surface thermal resistance ofR 2 Saturation temperature
As a function of saturation temperature with respect to condenser operating pressure.
When the temperature is higher than the set temperature
And then, the requirement of maintaining the air cavity is met, then:
wherein,Das to the outer diameter of the return tube 32,
dissipating power for heat.
To sum up:
similarly, under the rocking condition, the design temperature is
If electric heater or steam heating trouble, the device passes through high temperature steam heating condensate to produce the steam chamber, perhaps directly let in steam, realize the non return.
If the electric heating system breaks down, the device heats the condensed water through high-temperature steam, so that an air cavity is generated, and the non-return is realized.
When steam heating is carried out on condensed water, the flow of the heating steam iswAnd the angle of inclination
Maximum difference in liquid level between left and right side condensers
Cross sectional area of water tank
Supercooling degree of condensed water
Operating pressure of condenser
Heating steam pressure
For indirect heating by steam, the heat exchange area of the heating pipe needs to be considered
And deriving the heating steam flow according to the same manner of electric heating derivationw：
Namely:
for heating steam pressure
Temperature of steam
Under the conditions, the enthalpy of the steam;
for operating pressure of condenser
Temperature of water
Under the conditions, the enthalpy of the water.
Similarly, under the condition of swinging, the flow of the heating steamwComprises the following steps:
the specific formula needs to be solved specifically according to design parameters.
In conclusion, when the ship body tilts and swings left and right, the flow-resisting working medium in the air storage cavity 13 is converged to the non-return cavity 4 under the action of buoyancy, the liquid level is controlled below the outlet of the communicating pipeline 3, and the condensed water in the condensed water cavity 12 is blocked from flowing back to the condenser 2 through the non-return cavity 4, so that the non-return function of the condensed water is realized. The problems that the check valve used in the prior art has insufficient check sealing pressure, the sealing pressure required by the check valve is difficult to maintain only by means of gravity pressure drop, and the check effect is poor can be solved; the problems that the resistance of the check valve is too large, the drainage quantity of a hot well is influenced, and the inlet pressure of the condensate pump is too low, so that cavitation is generated and the safe operation of the condensate pump is influenced are solved; and the check valve is limited by the space for the ship and can only be arranged in the water tank, so that the maintenance is extremely difficult.
In the description of the present application, it should be noted that the terms "upper", "lower", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, which are only for convenience in describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and operate, and thus, should not be construed as limiting the present application. Unless expressly stated or limited otherwise, the terms "mounted," "connected," and "coupled" are to be construed broadly and encompass, for example, both fixed and removable coupling as well as integral coupling; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.
It is noted that, in the present application, relational terms such as "first" and "second", and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising a … …" does not exclude the presence of another identical element in a process, method, article, or apparatus that comprises the element.
The above description is merely exemplary of the present application and is presented to enable those skilled in the art to understand and practice the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. The utility model provides a marine anti-sway water tank which characterized in that includes:
the tank comprises a tank body (1), wherein a water outlet cavity (11), a water condensing cavity (12) and an air storage cavity (13) which are sequentially communicated are arranged in the tank body (1), and the air storage cavity (13) is positioned above the water condensing cavity (12) and is used for storing a choked flow working medium;
the two condensers (2) are arranged above the box body (1), each condenser (2) is communicated with a communicating pipeline (3) extending into the water condensation cavity (12), and an outlet of each communicating pipeline (3) and the corresponding communicated condenser (2) are respectively positioned at two ends of the water condensation cavity (12);
two non return chamber (4), establish respectively the both ends of congealing water cavity (12), and with congeal water cavity (12) intercommunication, the width in non return chamber (4) is less than the width of congealing water cavity (12), the export of intercommunication pipeline (3) stretches into in the non return chamber (4).
2. The marine anti-sway water tank of claim 1, characterized in that: the outermost end face of the check cavity (4) forms an inclined surface inclined outwards from the bottom face to the top face, and the outlet of the communicating pipeline (3) is located on one side close to the top face.
3. The marine anti-sway water tank of claim 1, characterized in that: be equipped with electric heating mechanism (6) in non return chamber (4), it sets up in non return chamber (4), electric heating mechanism (6) include two electric heater, are located two respectively the upside in non return chamber (4).
4. The marine anti-sway water tank of claim 1, characterized in that: the check cavity (4) is also communicated with a conveying pipeline (5) for conveying steam to the check cavity (4), or extends into a steam heating pipeline in the check cavity (4).
5. The marine anti-sway water tank of claim 1, characterized in that: the communicating pipeline (3) comprises a hot well (31) and a check pipe (32) which are communicated with each other, the connecting end of the hot well (31) and the check pipe (32) extends into the condensed water cavity (12), the other end of the hot well (31) is communicated with the condenser (2), and the outlet of the check pipe (32) and the condenser (2) are respectively positioned at two ends of the condensed water cavity (12).
6. The marine anti-sway water tank of claim 1, characterized in that: the cross section of the air storage cavity (13) is semicircular.
7. The marine anti-sway water tank of claim 1, characterized in that: and an inflation and exhaust valve (14) is arranged at the top of the air storage cavity (13).
8. A method for designing parameters of a marine anti-sway water tank, for designing the marine anti-sway water tank of claim 1, comprising the steps of:
determining the length of the horizontal direction of the communicating pipeline (3) in the water condensing cavity (12) according to the maximum inclination angle of the ship body and the maximum liquid level height difference of the two condensers (2), or the swing amplitude, the swing period and the maximum swing liquid level height difference of the two condensers (2);
and determining the volume of the air storage cavity (13) according to the length of the horizontal direction of the communicating pipeline (3) positioned in the water condensation cavity (12) and the section shape of the check cavity (4).
9. The parameter design method of claim 8, wherein:
under the inclined working condition according to the formula
The length of the communicating pipe (3) in the horizontal direction is determined in the water condensation cavity (12)LWherein, in the process,
is the maximum inclination angle of the ship body,
is the maximum liquid level difference of the two condensers (2).
10. The parameter design method of claim 8, wherein: when steam is used as a flow-resisting working medium, the working temperature of the electric heaters in the two non-return cavities (4) is determined according to the maximum inclination angle of the ship body, the maximum liquid level height difference of the two condensers (2), the cross section shape of the non-return cavities (4), the supercooling degree of condensed water and the operating pressure of the condensers.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB558821A (en) * | 1942-04-14 | 1944-01-24 | Northern Equipment Co | Feed water regulating apparatus for boilers |
| CN103380056A (en) * | 2011-02-25 | 2013-10-30 | 三菱重工业株式会社 | Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine |
| CN103375945A (en) * | 2012-04-12 | 2013-10-30 | 王云章 | Marine non-return air-cooling ammonia condenser |
| CN212516584U (en) * | 2020-06-19 | 2021-02-09 | 中国舰船研究设计中心 | Cabin spray test device for ship |
| CN113161026A (en) * | 2021-03-14 | 2021-07-23 | 中国船舶重工集团公司第七一九研究所 | Marine pressure driven passive containment heat exporting system |
-
2022
- 2022-07-28 CN CN202210896527.1A patent/CN114993067B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB558821A (en) * | 1942-04-14 | 1944-01-24 | Northern Equipment Co | Feed water regulating apparatus for boilers |
| CN103380056A (en) * | 2011-02-25 | 2013-10-30 | 三菱重工业株式会社 | Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine |
| CN103375945A (en) * | 2012-04-12 | 2013-10-30 | 王云章 | Marine non-return air-cooling ammonia condenser |
| CN212516584U (en) * | 2020-06-19 | 2021-02-09 | 中国舰船研究设计中心 | Cabin spray test device for ship |
| CN113161026A (en) * | 2021-03-14 | 2021-07-23 | 中国船舶重工集团公司第七一九研究所 | Marine pressure driven passive containment heat exporting system |
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| CN114993067A (en) | 2022-09-02 |
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