CN115203836A - Spring for fuel cell stack, design and model selection method thereof and fuel cell stack - Google Patents
Spring for fuel cell stack, design and model selection method thereof and fuel cell stack Download PDFInfo
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- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
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Abstract
The application discloses a spring for a fuel cell stack, a design model selection method of the spring and the fuel cell stack, and belongs to the technical field of fuel cells. A method of designing a spring for a fuel cell stack, the method comprising: obtaining the ranges of the diameter D of the spring, the maximum compression h of the spring and the thickness t of the spring according to the performance requirement of the fuel cell stack on the spring; the method comprises the steps of establishing a response surface of an assembly force F and an optimal deformation delta of the fuel cell stack by taking a boundary condition of a spring geometric parameter diameter D as an input constraint function through a range of the spring diameter D, a range of a maximum spring compression h and a range of a spring thickness t, and obtaining optimal D, h and t by taking a maximum relative flexibility coefficient target condition in the spring buffering and compensation processes. The application quantifies the displacement and the assembly force of the galvanic pile buffering and compensation in the galvanic pile life cycle, ensures the sealing property and the performance of the galvanic pile, and can prevent the galvanic pile from influencing the performance and the service life of the galvanic pile due to overlarge assembly force.
Description
Technical Field
The application belongs to the technical field of fuel cells, and particularly relates to a spring for a fuel cell stack, a design and model selection method of the spring and the fuel cell stack.
Background
A Proton Exchange Membrane Fuel Cell (PEMFC) is an electrochemical device that directly converts chemical energy of fuel into electrical energy, and has the advantages of high energy conversion rate, low emission, low pollution, low noise, and convenient maintenance. In general, a single fuel cell is mainly composed of a Membrane Electrode Assembly (MEA) and a bipolar plate with gas flow channels, which are alternately stacked, wherein the MEA is generally prepared from a gas diffusion layer, a catalyst layer, and a polymer electrolyte membrane by a hot-pressing process. In order to obtain higher performance of the fuel cell, the contact resistance between the bipolar plate and the membrane electrode needs to be as small as possible, so that a certain force needs to be applied to the stack to compress the gas diffusion layer and ensure that the sealant line is compressed to achieve the sealing effect.
Fuel cell stacks are typically made up of tens to hundreds of individual cells connected in series. In the whole life cycle of the fuel cell stack, the operation temperature can be as high as 80 ℃, the low-temperature storage temperature can be as low as-40 ℃, and the inside of the stack can expand and contract along with the change of the temperature; meanwhile, the operation of the galvanic pile also has pneumatic load, and the pneumatic load both change the assembly force of the galvanic pile. Under the action of long-term load, the membrane electrode and the sealing rubber wire of the key parts of the galvanic pile can be loosened to a certain degree. During the relaxation process, the assembly force in the stack with unchanged compression ratio in the stack is reduced. The contact resistance between the gas diffusion layer and the polar plate is increased, the sealing reliability is reduced, and the performance and the service life of the galvanic pile are influenced. In order to solve the above problems, the design of the stack usually needs to use a spring, such as a disc spring (for short), for buffering and compensation, so that the total compression of the gas diffusion layer and the rubber wire inside the stack is increased, the compression of the disc spring is released, and meanwhile, the assembly force inside the stack is reduced, and the compression of the disc spring is released.
The disc spring is a spring formed by forming a hole in the center of a disc into a conical disc shape, and has a special function in function different from the traditional spring. For example, the disc spring has the characteristics of capability of bearing large load with small deformation, short stroke, small required space, convenience in combination and use, easiness in maintenance and replacement, high economic safety, long service life and the like. Meanwhile, the disc spring is also considered to be a spring with high design difficulty, and when the disc spring is used in a stacked manner, slight size difference has a large influence on the load, and the phenomenon that the relationship between the displacement and the load is reversed is also generated. Therefore, based on the important function of the disc spring in the fuel cell stack and the characteristics of the disc spring, the type selection and design of the spring such as the disc spring inside the fuel cell stack are particularly important. However, no research has been found in the related art on the design options for springs used in fuel cell stacks.
Disclosure of Invention
In view of the above-mentioned problems, the present invention is directed to solving, at least to some extent, one of the technical problems in the related art. Therefore, the invention provides a spring for a fuel cell stack, a design and model selection method thereof and the fuel cell stack, which can fill the blank of research on the design and model selection of the spring used in the fuel cell stack, ensure the sealing property and performance of the fuel cell stack and overcome the defects in the prior art.
In order to solve the technical problem, the present application is implemented as follows:
according to one aspect of the present application, an embodiment of the present application provides a method for designing and selecting a spring for a fuel cell stack, the method including:
obtaining the range of the diameter D of the spring, the range of the maximum compression h of the spring and the range of the thickness t of the spring according to the performance requirement of the fuel cell stack on the spring; the method comprises the steps of establishing a response surface of an assembly force F and an optimal deformation delta of the fuel cell stack by taking a boundary condition of a spring geometric parameter diameter D as an input constraint function through a range of the spring diameter D, a range of a maximum spring compression h and a range of a spring thickness t, and obtaining the optimal spring diameter D, the maximum spring compression h and the spring thickness t by taking a relative maximum flexible coefficient in a spring buffering and compensating process as a target condition.
Further, the range of obtaining the diameter D of the spring, the range of the maximum compression h of the spring, and the range of the thickness t of the spring according to the performance requirement of the fuel cell stack on the spring includes: establishing a matching principle of a fuel cell stack and a spring; based on the matching principle, the dimensions of the fuel cell stack and the springs are considered.
Further, the establishing of the matching principle of the fuel cell stack and the spring comprises the following steps: the static assembly force of the fuel cell stack matches the compression of the springs; matching dynamic assembly force compensation and buffering performance of the fuel cell stack; matching of springs to fuel cell stack boundary conditions.
Further, the dimensions of interest for establishing the fuel cell stack and the springs include: (1) Dividing the assembly force F of the fuel cell stack by the number m of the springs distributed in the plane to serve as the selection criterion of the working compression force of the springs; (2) Under the premise of meeting the condition (1), the larger the spring flexibility coefficient is, the better the spring flexibility coefficient is, in the optional buffering and compensation range of the fuel cell stack is; (3) The spring geometry diameter D is adapted to approximate the width of the bipolar plate reaction zone for uniform application of assembly force from a contact boundary condition point of view.
Further, on the premise that the dimensional consideration condition (1) and the dimensional consideration condition (2) are met, the range of the spring diameter D, the range of the spring thickness t and the range of the maximum compression amount h of the spring are sequentially provided.
Further, the working compression force of the spring is the corresponding compression force when the spring delta =0.75 h; and/or the diameter D of the spring is not affected by the thickness t of the spring and the maximum compression h of the spring.
Further, the method specifically comprises: acquiring a buffer expected value of the compression amount of the fuel cell stack and a buffer expected value of the assembly force of the fuel cell stack; acquiring a compensation expected value of the compression amount of the fuel cell stack and a compensation expected value of the compression force; establishing a matching relation between the diameter of the spring and the size of the bipolar plate to determine the range of the diameter D of the spring and the range of the number of the springs distributed in the plane; establishing a functional relation between the static assembly force of the fuel cell stack and the distribution quantity of the springs in a plane so as to determine the compression force range of a single spring; obtaining the range of the spring thickness t according to the range of the spring diameter D and the range of the compression force of a single spring; arranging in-line springs in the vertical direction to increase the buffering and compensating capacity of the springs through the in-line springs, and determining the range of the maximum compression h of the springs and the number of the in-line disc springs according to the expected compensation value of the compression of the fuel cell stack; and obtaining the optimal spring diameter D, the maximum spring compression h and the spring thickness t according to the range of the spring diameter D, the range of the maximum spring compression h and the range of the spring thickness t under the condition that the maximum flexibility coefficient is the target.
Further, the obtaining of the range of the spring thickness t from the range of the spring diameter D and the single spring compression force range includes: for the disc spring without the supporting surface, the range of the thickness t of the spring can be obtained according to the following formula;
in the formula:
wherein, F is the load of a single disc spring, C is the spring index, D is the diameter of the spring (the outer diameter of the disc spring), D is the inner diameter of the spring (the disc spring), t is the thickness of the spring (the disc spring), and h is 0 -calculated value of deflection at flattening of the disc spring, δ -deflection of the spring (disc spring), E-modulus of elasticity, μ -poisson's ratio.
Further, the obtaining of the buffer expected value of the compression amount of the fuel cell stack and the buffer expected value of the assembly force of the fuel cell stack comprises: establishing a mapping relation among the length of the fuel cell stack, the expansion coefficient of the bipolar plate and the operating temperature to obtain a buffer expected value of the compression amount of the fuel cell stack; and establishing a mapping relation between the pneumatic load and the reaction area of the fuel cell stack to obtain a buffering expected value of the assembly force of the fuel cell stack.
Further, the obtaining of the compensated expected value of the compression amount and the compensated expected value of the compression force of the fuel cell stack includes: and (3) considering creep deformation of the fuel cell stack assembly force locking device under the long-term stress and relaxation of the rubber wire under the long-term load condition to obtain a compensation expected value of the compression amount of the fuel cell stack and a compensation expected value of the compression force.
According to another aspect of the present application, there is also provided a spring for a fuel cell stack, which is designed and selected by the method for designing and selecting a spring for a fuel cell stack as described above and is applied to a fuel cell stack; the spring for the fuel cell stack is made of metal, resin or modified resin; the fuel cell stack spring includes a disc spring.
Further, the spring for a fuel cell stack is formed by laminating a plurality of single-layer modified resin layers; the modified resin layer includes at least two fiber reinforced resin layers.
Further, the at least two fiber-reinforced resin layers comprise at least two of a carbon fiber-reinforced epoxy resin layer, a glass fiber-reinforced epoxy resin layer, a basalt fiber-reinforced epoxy resin layer, a wood fiber-reinforced epoxy resin layer and an aramid fiber-reinforced epoxy resin layer.
Further, the outer surface of the spring for the fuel cell stack is provided with a protective coating.
Further, the total thickness of the carbon fiber reinforced epoxy resin layer is 0.2-0.6 times of the thickness of the spring for the fuel cell stack, and the total thickness of the glass fiber reinforced epoxy resin layer is 0.8-0.4 times of the thickness of the spring for the fuel cell stack.
Further, the thickness of the single-layer modified resin layer is 0.1 mm-0.2 mm.
According to another aspect of the present application, there is also provided a fuel cell stack, which includes a core assembly, and a spring obtained by performing design selection by using the method for designing and selecting a spring for a fuel cell stack as described above or the spring for a fuel cell stack as described above.
The technical scheme of the invention at least has the following beneficial effects:
in the embodiment of the invention, the provided method for designing and selecting the springs for the fuel cell stack is characterized in that a constraint function which takes the performance requirement of the fuel cell stack on the springs and the boundary condition of the spring diameter D as the input is used, a response surface of the assembly force F and the optimal deformation delta of the fuel cell stack is established through the spring diameter D, the maximum compression amount h of the springs and the spring thickness t, the design process of the optimal D, h and t is obtained, and the design objective function is that the relative maximum flexibility coefficient is obtained in the process of spring buffering and compensation. Therefore, through the proposal of the design model selection method, the invention quantifies the buffer and compensation displacement and assembly force of the galvanic pile in the whole life cycle of the galvanic pile, can compensate the attenuation of the assembly force caused by the relaxation of the sealing rubber wire, and further can ensure the sealing performance and performance of the galvanic pile; meanwhile, the galvanic pile can be buffered when being subjected to expansion and contraction and pneumatic load, and the performance and the service life of the galvanic pile are prevented from being influenced due to overlarge assembly force.
The spring for the fuel cell stack in some preferred embodiments of the invention can be made of non-metal materials, thereby meeting the requirement of a fuel cell module on light weight and relieving the problems of large mass, insulation and the like of a metal disc spring used by the fuel cell stack.
Additional aspects and advantages of the present application will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the present application.
Drawings
FIG. 1 is a schematic diagram of springs for a fuel cell stack according to certain exemplary embodiments of the present disclosure;
FIG. 2 is a first Force-Displacement graph of a fuel cell stack spring provided in accordance with certain exemplary embodiments of the present disclosure;
FIG. 3 is a first Force-Flexibility graph of a fuel cell stack spring provided in accordance with certain exemplary embodiments of the present disclosure;
FIG. 4 is a second Force-Displacement graph of a fuel cell stack spring according to certain exemplary embodiments of the present disclosure;
FIG. 5 is a second Force-Flexibility graph of springs for a fuel cell stack according to certain exemplary embodiments of the present disclosure;
FIG. 6 is a third Force-Flexibility graph of a fuel cell stack spring provided in accordance with certain exemplary embodiments of the present disclosure;
FIG. 7 is a fourth Force-Flexibility graph of a spring for a fuel cell stack according to certain exemplary embodiments of the present disclosure;
fig. 8 is a third Force-Displacement graph of a fuel cell stack spring according to some exemplary embodiments of the present disclosure.
Detailed Description
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, but not all, embodiments of the present application. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present application without making any creative effort belong to the protection scope of the present application.
The spring plays important role in the fuel cell galvanic pile, and different fuel cell galvanic piles need to match the springs of different models or sizes to use the spring of most adaptation to cushion and compensate, guarantee the sealing reliability of fuel cell galvanic pile, and then guarantee the performance and the life-span of fuel cell galvanic pile. However, in the related art, no research on the design and selection of the spring for the fuel cell stack has been found before the filing date of the present application, and therefore, research and development is to be conducted to fill the gap in this respect. In addition, when the spring is applied to the fuel cell stack, the type or the size of the spring is considered, and the material problem of the spring is also considered; the existing springs used in the fuel cell stack are basically made of metal materials, so that the existing springs have the problems of various bottlenecks such as large mass, poor corrosion resistance, poor fatigue property and the like, and cannot adapt to the development trend of light weight in the fuel cell industry. In addition, in the application process of the fuel cell, the galvanic pile needs to be insulated from the outside so as to avoid threat to the personal safety; based on the consideration of intensity, the end plate of spring both ends centre gripping also generally is the metal material, and there is tiny gap in spring range hookup location and the position of contacting with the end plate simultaneously, remains moisture easily and leads to the galvanic pile insulating effect to descend. Therefore, research and development of a fuel cell stack spring made of a non-metal material are required to meet the demand of fuel cell modules for light weight.
In view of this, the technical solution of the embodiment of the present application provides a method for designing and selecting a spring for a fuel cell stack, and a fuel cell stack including the spring for a fuel cell stack, which can ensure the sealing property and the electrical property of the fuel cell stack, prevent the stack from affecting the performance and the service life of the stack due to an excessive assembly force, and meet the requirement for light weight of the fuel cell stack. See below for a description of specific embodiments.
Referring to fig. 1 to 7, in some embodiments of the present application, a method for designing and selecting a spring for a fuel cell stack is provided, where the method for designing and selecting a spring includes:
according to the performance requirement of the fuel cell stack on the spring, the range of the diameter D of the spring, the range of the maximum compression amount h of the spring and the range of the thickness t of the spring are obtained;
the method comprises the steps of establishing a response surface of an assembly force F and an optimal deformation delta of the fuel cell stack by taking a boundary condition of a spring geometric parameter diameter D as an input constraint function through a range of the spring diameter D, a range of a maximum spring compression h and a range of a spring thickness t, and obtaining the optimal spring diameter D, the maximum spring compression h and the spring thickness t by taking a relative maximum flexible coefficient in a spring buffering and compensating process as a target condition.
The embodiment of the invention quantifies the buffer and compensation displacement and assembly force of the fuel cell stack in the whole life cycle of the stack by providing the design and model selection method of the spring for the fuel cell stack, can compensate the attenuation of the assembly force caused by the looseness of the sealing rubber wire, and further can ensure the sealing property and performance of the stack.
According to the embodiment of the invention, through the design and model selection method of the spring for the fuel cell stack, the stack can be buffered when being subjected to thermal expansion and cold contraction and pneumatic load, and the influence on the performance and the service life of the stack caused by overlarge assembly force is prevented.
Therefore, by adopting the technical scheme provided by the embodiment of the invention, the sealing property, the safety and the reliability of the fuel cell stack can be improved, and the service life of the fuel cell stack can be prolonged.
Alternatively, the fuel cell stack spring may be a disc spring, which is simply referred to as a disc spring.
Fig. 1 shows a geometric parameter diagram of a spring, and referring to fig. 1, the spring for a fuel cell stack is a disc spring, a diameter (outer diameter) of the spring (disc spring) is denoted as D, an inner diameter of the spring is denoted as D, a total deflection of the spring, that is, a maximum compression amount of the spring is denoted as H, a thickness of the spring is denoted as t, a free height of the spring is denoted as H, and H = H + t.
Fig. 2 to 7 show Force-Displacement (compression Force-compression amount) graphs of springs and Force-Flexibility (compression Force-Flexibility) graphs of springs, and referring to fig. 2 to 7, for the springs, as D ≈ 2d, h =h + t, the control parameters of the Force-Displacement relation curves and the Force-Flexibility relation curves of the springs actually only have the diameter D, the thickness t and the maximum compression amount h. Therefore, for a certain type of fuel cell stack, the assembly force F and the optimal deformation δ are input parameters, and there can be numerous combinations of D, t, and h to satisfy the required relationship of F and δ.
Specifically, a method for designing and selecting the spring for the fuel cell stack will be described in detail below.
In some embodiments, the ranges for spring diameter D, spring maximum compression h, and spring thickness t are obtained according to the performance requirements of the fuel cell stack for the spring, including:
establishing a matching principle of a fuel cell stack and a spring;
based on the matching principle, the considered dimensions of the fuel cell stack and the spring are established.
The principle of establishing the matching between the fuel cell stack and the spring mainly comprises three aspects:
(1) The static assembly force of the fuel cell stack matches the compression of the springs; this situation can be considered by the Force-displacement curve of the spring.
(2) Matching dynamic assembly force compensation and buffering performance of the fuel cell stack; this situation can be considered by the Force-Flexibility curve of the spring.
(3) Matching of springs to fuel cell stack boundary conditions. That is, the disc spring can be applied to the fuel cell with an advantage in terms of its boundary condition, that is, a large and uniform contact area with the inner end plate of the disc spring.
Wherein, the Force-displacement curve can be divided into 4 stages:
1) 0-0.25h stage: the phase elastic coefficient increase is gradually accelerated, the acceleration slope is less than that of the phase 2) and the phase 3) but greater than that of the phase 4), the rate of increase (decrease) of the compressive force is the greatest among the four phases, the phase buffering and compensation both cause the greatest assembly force fluctuation among the four phases, and therefore the phase is not recommended to be used.
2) 0.25h-0.5h stage: the elasticity coefficient increase in the stage is accelerated rapidly, the acceleration slope reaches the maximum in four stages, and the stage is also not recommended to use on the basis of the principle that the buffering and compensating capacity brought by the rapid acceleration with flexibility is used up as much as possible.
3) 0.5h-0.75h stage: the increase in the compliance coefficient at this stage is slowed down relative to stage 2), while the acceleration slope is still only after stage 2); the compliance coefficient of the end of stage 3) is already close to stage 4), and is not much different from the elastic limit of the spring.
4) 0.75h-h stage: the increase of the flexibility coefficient in the stage is minimum in four stages, the flexibility coefficient reaches the maximum in value, and the increase of the assembling force also reaches the minimum in the stage of the minimum increase of the flexibility coefficient, so that the fluctuation of the assembling force is minimum when the compression amount changes in the interval.
In summary, when the disc spring has a certain pre-compression force and performs compensation and buffering of the pre-compression force near the pre-compression force, the working point of the disc spring is near 0.75h, the working compression force of the disc spring is corresponding to the compression force of the disc spring at 0.75h, and the fluctuation of the compression force of the disc spring is minimal at the buffering amount of 0.75 h-h. When the disc spring compensates the compression force, the 0.5-0.75h stage can provide the compensation stability which is second to 0.75-h, and the fluctuation increase of the compression force is only larger than that of the stage 4) under the same compression compensation amount.
In some embodiments, the dimensions of the fuel cell stack and springs are established in consideration, consisting essentially of:
(1) Dividing the assembly force F of the fuel cell stack by the number m of the springs distributed in the plane to serve as the working compression force selection criterion of the springs;
(2) Under the premise of meeting the condition (1), the larger the spring flexibility coefficient is, the better the spring flexibility coefficient is, in the optional buffering and compensation range of the fuel cell stack is;
(3) The spring's geometric parameter diameter D is adapted to approximate the width of the bipolar plate reaction zone for uniform application of assembly force from a contact boundary condition perspective.
The working compression force of the spring is the corresponding compression force when the disc spring delta =0.75 h. Accordingly, the above dimension (1) may be a value obtained by dividing the assembly force F of the fuel cell stack by the number m of in-plane spring distributions, which is used as a compression force selection criterion when the spring δ =0.75 h.
According to the embodiment, in the design and model selection process of the spring for the fuel cell stack, firstly, the performance requirement of the fuel cell stack on the disc spring and the boundary condition of the geometric parameter D are used as input constraint functions, F and delta response surfaces are established through the ranges of D, h and t, the optimal design process of D, h and t is obtained, and the design objective function is the relative maximum flexibility coefficient in the disc spring buffering and compensating process.
Specifically, on the premise of meeting the consideration dimensional condition (1) and the consideration dimensional condition (2), the range of the diameter D of the spring, the range of the thickness t of the spring and the range of the maximum compression h of the spring are sequentially provided; and selecting a group of D, h and t as the optimal design under the condition that the maximum flexibility coefficient is the target condition.
It should be noted that the above-mentioned boundary conditions with the geometric parameter D, or the width of the spring with the geometric parameter D adapted to approach the reaction region of the bipolar plate from the point of view of the contact boundary conditions, are primarily intended to mean that the diameter D of the spring or the number of springs distributed in the plane needs to be adapted to the dimensions of the shape of the bipolar plate. For example, when a rectangular bipolar plate is used, the diameter D of the spring may be adapted to the width of the bipolar plate, that is, the diameter D of the spring may be close to (equal to or slightly smaller than) the width of the bipolar plate, and a plurality of springs may be uniformly arranged along the length direction of the bipolar plate, and the number of the springs distributed in a plane is determined according to the length of the bipolar plate, which is beneficial to uniformly applying the assembly force.
The determination regarding the range of the spring diameter D, the range of the spring maximum compression amount h, and the range of the spring thickness t is specifically described below.
[ range of spring diameter D ]
The range of spring diameter D can be determined primarily from two aspects, one, the matching of parameter diameter D to the fuel cell stack and the other, the relationship of parameter diameter D to the physical properties of the disc spring itself.
Regarding the matching of the parameter diameter D to the fuel cell stack:
the diameter of the disk spring, i.e., D, is selected in relation to the size of the bipolar plate, and generally, the number m × D of the disk spring in-plane distribution should match the length of the bipolar plate, and the diameter D of the disk spring is close to the reaction width of the bipolar plate.
Illustratively, the width of the bipolar plate is in the range of 100-130mm, the length is in the range of 300-420mm, it can be known that the diameter D of the belleville springs can be selected in the range of 80-120mm, and the number of the distribution of the belleville springs in the length direction of the bipolar plate can be 3-4.
More specifically, taking the width of the matched bipolar plate as 105mm and the length as 420mm as an example, the diameter D of the disc spring should be 80-100mm, the number of the disc springs should be 3-4, the stack assembly force is 30kN, and the compression force range of a single disc spring is 7500-10000N.
Regarding the relationship between the parameter diameter D and the physical property of the disc spring:
in the case where the matching of the parameter diameter D to the fuel cell stack is satisfied, the diameter D as the first proposed parameter is not constrained by the other two parameters thickness t and maximum compression h. Therefore, the geometric constraint of the fuel cell stack on D is taken as a selection parameter range of D, and the influence of D on the consideration dimension condition (1) and the consideration dimension condition (2) in the parameter range is described.
As shown in fig. 2, the influence of the parameter diameter D on the consideration of the dimensional condition (1) can be seen from fig. 2, where the stiffness of the disc spring is smaller as the diameter D is larger, and the stiffness of the disc spring is larger as the diameter D is smaller.
As shown in fig. 3, the influence of the parameter diameter D on the consideration of the dimensional condition (2) can be seen from fig. 3, where the larger the diameter D, the larger the compliance of the disc spring, and the smaller the diameter D, the smaller the compliance of the disc spring.
Thus, the diameter D affects the maximum value and the minimum value of the compliance coefficient, and has a small influence on the incremental development tendency of the compliance coefficient, which matches the phenomenon in consideration of the dimensional condition (1).
Thus, for a stack of dimensions 105mm by 420mm, a reasonable range of disc spring diameter D is 80-100mm.
[ range of spring thickness t ]
The range of the spring thickness t can be determined mainly from two aspects, namely, the relation between the parameter thickness t and the physical property of the disc spring, and the matching between the parameter thickness t and the fuel cell stack.
Regarding the relation between the parameter thickness t and the physical property of the disc spring:
as shown in fig. 4, the influence of the parameter thickness t on the consideration of the dimensional condition (1) can be seen from fig. 4, where the stiffness of the disc spring is larger when the thickness t is larger, and the stiffness of the disc spring is smaller when the thickness t is smaller. The deeper order of the values is that when the diameter is 90mm, h is 2.3mm, and the thickness is 3.2mm and 3.5mm, respectively, the compression is nearly the same when the respective compression force ratio is the same, and the respective maximum deformation h is the same.
As shown in fig. 5, the influence of the parameter thickness t on the consideration of the dimensional condition (2) can be seen from fig. 5, where the greater the thickness t is, the smaller the thickness t is, the greater the compliance of the disc spring is, and on the premise that the diameter D and the maximum compression amount h are the same, for the shape of the flexible curve, the thickness t determines the left and right movement of the horizontal position of the flexible curve in the coordinate axis, and has a small influence on the shape of the curve.
Therefore, the thickness t does not influence the maximum value and the minimum value of the flexibility coefficient, the incremental development trend of the flexibility coefficient is slightly influenced, and only the compression force corresponding to the flexibility coefficient is influenced, so that the method is matched with the phenomenon in the consideration dimension condition (1).
Regarding the matching of the parameter thickness t to the fuel cell stack:
when the diameter D of the disc spring ranges from 80mm to 100mm for a stack with an assembly force of 30kN, according to the relation of compression force and compression displacement of the disc spring:
in the formula:
wherein, F is the load of a single disc spring, C is the spring index, D is the diameter of the spring (the outer diameter of the disc spring), D is the inner diameter of the spring (the disc spring), t is the thickness of the spring (the disc spring), and h is 0 -calculated value of deflection at flattening of the disc spring, δ -deflection of the spring (disc spring), E-modulus of elasticity, μ -poisson's ratio.
It can be calculated that the reasonable selection range of the thickness t is between 3.0 and 3.5mm, and the assembly force increase brought by the thickness increment of every 0.5mm is about 5 kN.
[ Range of spring maximum compression amount h ]
The range of the maximum compression amount h of the spring can be determined mainly from two aspects, namely, the relationship between the maximum compression amount h of the parameter spring and the physical property of the disc spring, and the maximum compression amount h of the parameter spring is matched with the fuel cell stack.
Regarding the relationship between the parameter spring maximum compression h and the physical property of the disc spring:
the numerical relation between the maximum compression amount h and the diameter D is h = tan alpha x (D-D), under the premise that alpha is fixed, the diameter D determines the maximum flexibility coefficient of the disc spring, and the thickness t determines the maximum compression force of the disc spring (the shape of the cross section determines the shape of the compression curve of the disc spring, so that the engineering application of variable cross section optimization design is required for the compression curve shape of the disc spring and has certain design capacity).
As shown in fig. 6, the parameter sensitivity of α can be considered at a constant diameter D and thickness t. As can be seen from fig. 6, when h decreases (increases), the maximum compliance and the maximum compression force decrease (increase) at the same time, and the compliance curve becomes smooth (steep), and the difference between the peaks and valleys of the compliance curve becomes small (large), and the compliance curve becomes smooth, which is characterized by relatively uniform compensation for the relative displacement assembly force variation within the range of 0 to h of the disc spring. Exemplarily, taking a disc spring with a diameter D =80mm and a thickness t =3.0mm as an example, a flexibility coefficient curve at different maximum compression h values is shown in fig. 6, where the maximum compression h =1.5mm is optimal at an assembly force of 0-22.5kN, and δ =0.75h is matched with the optimal assembly force of 15kN; when the maximum compression h =2.0mm, the performance is optimal in the assembling force range of 22.5-27kN, and when delta =0.75h, the matching assembling force is 22.5kN; it is optimal in the range 27-37.5kN for h =2.3mm and matching assembly force is 30kN for δ =0.75 h.
Regarding the matching of the parameter maximum compression h to the fuel cell stack:
through the numerical value of adjusting maximum compression h, can change the difference of compliance curve crest trough, also can adjust the smooth degree of curve, at the compensation stage, the compliance curve is gentle to mean: namely, in the compensation stage, the same displacements of 0.75h-0.5h,0.5h-025h,0.25h-0h are compensated, and the reduction of the assembly force in the three stages is relatively uniform. The phenomenon that the assembly force is reduced less in one stage and is reduced more severely in the next stage does not exist, and the compensation force can be smoothly provided in the full working range, and the buffer stage is disadvantageous in the common application. The gentle curve of the flexibility means that the displacement assembling force for buffering the same is increased more, and the steep curve of the flexibility means that the change of the displacement assembling force for buffering a certain amount in the compensation stage is smaller in the range of 0.5h to 0.75h, but the compensation performance is reduced sharply in the two latter stages. The steeper flexibility curve during the damping phase means less variation in the assembly force for the same displacement of the damping. The quality of the different compensation characteristics caused by h is actually determined by the use environment. In the application of the fuel cell, the shape of the disk spring flexibility coefficient-deformation amount or rigidity coefficient-assembly force curve needs to be matched with the attenuation process of the assembly force inside the fuel cell stack, namely the attenuation amplitude of the assembly force has an influence on the performance of the fuel cell stack within an allowable range. The attenuation amplitude is further divided into a plurality of sections, the corresponding time amplitude of each assembly force section is different under the influence of the mechanical characteristics of materials in the galvanic pile, and the optimal assembly force compensation performance of the disc spring is corresponding to the assembly force section with the maximum time amplitude in the galvanic pile.
Wherein, the optimal assembly force compensation performance of the disc spring is as follows: in the assembly force interval with the largest time amplitude, the larger the flexibility coefficient (stiffness coefficient) of the disc spring, the better the flexibility coefficient (stiffness coefficient) (the smaller the stiffness coefficient), the better the flexibility coefficient.
In summary, when the compensation displacement interval of the fuel cell stack is 0-7.8mm, the reasonable value range of h is 2.3-2.8mm under the condition of 4 disc spring vertical lines.
Based on the above, the range of the spring diameter D, the range of the spring thickness t and the range of the maximum compression amount h of the spring are obtained, so that the spring diameter D, the spring thickness t and the maximum compression amount h of the spring can be optimally designed to obtain an optimal flexibility coefficient curve.
Specifically, the method for obtaining the optimal flexibility coefficient curve may include: the compensation capacity h of the disc spring is determined to be a certain value (e.g., 2.3 mm), and as shown in fig. 7, the peak value of the compliance coefficient can be adjusted by the diameter D, and the maximum assembly force can be adjusted by the thickness t to match the assembly force (30 kN) of the fuel cell stack. Through the analysis of the diameter D and the thickness t, the numerical value of the diameter D can adjust the vertical up-and-down movement of the flexible curve in the force-flexibility coefficient coordinate system, and the numerical value of the thickness t can adjust the left-and-right movement of the flexible curve in the force-flexibility coefficient coordinate system.
Therefore, with the determined F and δ requirements, the design can be optimized by adjusting the position of the compliance curve in the force vs. compliance coordinate axis system with respect to the design point, α decreasing, diameter D increasing and thickness t increasing.
Referring to fig. 8, in the case where a range of the spring diameter D, a range of the spring thickness t, and a range of the maximum compression amount h of the spring have been obtained, that is, D =80-90mm, t =3.0-3.5mm, and h =2.3-2.8mm are known, three better solutions can be output: d80_ h2.3_ t3.0, D90_ h2.3_ t3.2, D100_ h2.3_ t3.5. Since the maximum compression h is 2.3mm, the matched compensation and buffer intervals are the same, and as can be seen from fig. 8, the starting points and the end points of the compression displacement-compression force curves designed by the three disc springs are basically overlapped, and the matched assembly force of the fuel cell stack is about 36 kN. However, the maximum compliance coefficient distribution and the compression force interval are different, as shown in fig. 7, D90_ h2.3_ t3.2 has the best performance in the assembly force range of 0-34kN, D80_ h2.3_ t3.0 has the best performance in the assembly force range of 34-37.5kN, and D100_ h2.3_ t3.5 has the largest assembly force compensation range where the difference between the peak and the trough of the compliance coefficient is the lowest.
In some embodiments, the method for designing and selecting the spring for the fuel cell stack specifically comprises the following steps:
s1, obtaining a buffer expected value of the compression amount of a fuel cell stack and a buffer expected value of the assembly force of the fuel cell stack; the method specifically comprises the following steps:
s11, establishing a mapping relation among the length of the fuel cell stack, the expansion coefficient of the bipolar plate and the operating temperature to obtain a buffer expected value of the compression amount of the fuel cell stack;
s12, establishing a mapping relation between the pneumatic load and the reaction area of the fuel cell stack to obtain a buffering expected value of the assembly force of the fuel cell stack.
S2, acquiring an expected compensation value of the compression amount of the fuel cell stack and an expected compensation value of the compression force; the method specifically comprises the following steps:
and (3) considering creep deformation of the fuel cell stack assembly force locking device under the long-term stress and relaxation of the rubber wire under the long-term load condition to obtain a compensation expected value of the compression amount of the fuel cell stack and a compensation expected value of the compression force.
And S3, establishing a matching relation between the diameter of the spring and the size of the bipolar plate so as to determine the range of the diameter D of the spring and the range of the number m of the springs distributed in the plane.
S4, establishing a functional relation between the static assembly force of the fuel cell stack and the distribution quantity of the springs in a plane to determine the compression force range of a single spring; determining the range of the thickness t of the spring according to the range of the diameter D of the spring and the range of the compression force of the single spring;
and S5, arranging the in-line springs in the vertical direction to increase the buffering and compensating capacity of the springs through the in-line springs, and determining the range of the maximum compression h of the springs and the number of the in-line disc springs according to the expected compensation value of the compression of the fuel cell stack.
The in-line spring may be a plurality of springs stacked in a vertical direction.
And S6, obtaining the optimal spring diameter D, the optimal spring maximum compression h and the optimal spring thickness t according to the range of the spring diameter D, the range of the spring maximum compression h and the range of the spring thickness t under the condition that the maximum flexibility coefficient is the target.
According to this embodiment, the diameter of the spring is typically close to the reaction width of the bipolar plate.
According to this embodiment, the diameter D of the spring is not affected by the thickness t of the spring and the maximum compression h of the spring.
According to the embodiment, the compression force of the single spring is the corresponding compression force when the disc spring delta =0.75 h.
According to the embodiment, the number of the straight disc springs is even.
In some embodiments, a spring for a fuel cell stack is also provided, and the spring for a fuel cell stack is designed and selected by using the method for designing and selecting the spring for the fuel cell stack and is applied to the fuel cell stack.
Optionally, the fuel cell stack spring comprises a disc spring.
Optionally, the spring for the fuel cell stack is made of metal, resin or modified resin. Preferably, the material of the spring for the fuel cell stack is resin or modified resin.
In some embodiments, the material of the spring for a fuel cell stack is modified resin.
The spring design and model selection method provided by the embodiment of the invention is not only suitable for the spring made of metal, but also suitable for the design and model selection of the spring made of nonmetal, and particularly suitable for the design and model selection of the spring made of nonmetal, so that the problems of large mass, insulativity, corrosivity and the like caused by the fact that most of the existing springs for the fuel cell stack are made of metal can be solved, and the problems of difficult model selection or non-adaptive adopted size, influence on the sealing property or service life of the fuel cell stack and the like caused by the fact that the springs made of nonmetal are used for the fuel cell stack can be solved.
In the embodiment of the invention, the material of the spring is preferably one or more modified resins, so that the requirement of the fuel cell module on light weight can be met, and the problems of large mass, insulation and the like of the metal disc spring used in the conventional fuel cell stack are solved.
In some embodiments, the spring for a fuel cell stack is formed by laminating a plurality of single-layer modified resin layers; preferably, the modified resin layer includes at least two fiber reinforced resin layers.
In some embodiments, the at least two fiber-reinforced resin layers include at least two of a carbon fiber-reinforced epoxy layer, a glass fiber-reinforced epoxy layer, a basalt fiber-reinforced epoxy layer, a wood fiber-reinforced epoxy layer, and an aramid fiber-reinforced epoxy layer. For example, the spring for a fuel cell stack may be formed by laminating two or more modified resin layers selected from among a plurality of carbon fiber-reinforced epoxy resin layers, glass fiber-reinforced epoxy resin layers, basalt fiber-reinforced epoxy resin layers, wood fiber-reinforced epoxy resin layers, and aramid fiber-reinforced epoxy resin layers. In addition, in other embodiments, other types of modified resins can be used for the modified resin layer, and are not described in detail here.
Optionally, the spring, i.e. the disc spring, is formed by laminating and molding a layered carbon fiber reinforced epoxy resin layer and a layered glass fiber reinforced epoxy resin layer structure with anisotropy.
Optionally, the dish spring is the standard cross-section, and the cross-section skin is carbon fiber reinforcement epoxy layer, and the inlayer uses glass fibre reinforcement epoxy layer, and the material mode of laying is symmetrical structure on the cross-section.
In some embodiments, the outer surface of the fuel cell stack spring is provided with a protective coating, which may be an insulating layer. Illustratively, if insulation requirements are present, a durable fiberglass insulation coating may be applied to the outer surface of the disc spring.
In some embodiments, the total thickness of the carbon fiber reinforced epoxy resin layer is 0.2 to 0.6 times the thickness of the fuel cell stack spring, and the total thickness of the glass fiber reinforced epoxy resin layer is 0.8 to 0.4 times the thickness of the fuel cell stack spring.
In some embodiments, a thickness of a single layer of the modified resin layer is 0.1mm to 0.2mm.
In some embodiments, a fuel cell stack is provided, which includes a core assembly, and a spring obtained by design selection using the aforementioned method for design selection of a fuel cell stack spring or the aforementioned fuel cell stack spring.
In summary, based on the above arrangement, according to the technical solution provided by the embodiment of the present invention, the density of the adopted disc spring for fuel cell stack is only 1.5-2 g/cm 3 Compared with steel, the weight of the fuel cell module can be reduced by 80% in the same size, and the requirement of the fuel cell module on light weight can be met. The outer surface of the adopted disc spring for the fuel cell stack can be provided with a glass fiber insulating coating, so that the requirement of the fuel cell stack on insulation can be met. The embodiment of the invention quantifies the buffer and compensation displacement and assembly force of the galvanic pile in the whole life cycle of the galvanic pile, so that the attenuation of the assembly force caused by the looseness of the sealing rubber wire is compensated, and the sealing property and the performance of the galvanic pile are ensured. The embodiment of the invention can buffer the galvanic pile when the galvanic pile is subjected to thermal expansion and cold contraction and pneumatic load, and prevent the galvanic pile from influencing the performance and the service life of the galvanic pile due to overlarge assembly force.
Details not described in the present specification are known to those skilled in the art.
In the present disclosure, the terms "one embodiment," "some embodiments," "example," "specific example" or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Moreover, various embodiments or examples and features of various embodiments or examples described in this specification can be combined and combined by one skilled in the art without being mutually inconsistent.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (12)
1. A method for designing and selecting a spring for a fuel cell stack, the method comprising:
according to the performance requirement of the fuel cell stack on the spring, the range of the diameter D of the spring, the range of the maximum compression amount h of the spring and the range of the thickness t of the spring are obtained;
the method comprises the steps of establishing a response surface of an assembly force F and an optimal deformation delta of the fuel cell stack by taking a boundary condition of a spring geometric parameter diameter D as an input constraint function through a range of the spring diameter D, a range of a maximum spring compression h and a range of a spring thickness t, and obtaining the optimal spring diameter D, the maximum spring compression h and the spring thickness t by taking a relative maximum flexible coefficient in a spring buffering and compensating process as a target condition.
2. The method of claim 1, wherein the obtaining of the range of the spring diameter D, the range of the maximum spring compression h and the range of the spring thickness t according to the performance requirement of the fuel cell stack on the spring comprises:
establishing a matching principle of a fuel cell stack and a spring;
based on the matching principle, the dimensions of the fuel cell stack and the springs are considered.
3. The method of claim 2, wherein the establishing a matching rule between the fuel cell stack and the spring comprises:
the static assembly force of the fuel cell stack matches the compression of the spring;
matching dynamic assembly force compensation and buffering performance of the fuel cell stack;
matching of springs to fuel cell stack boundary conditions.
4. The method of claim 2, wherein the establishing the dimensions of the fuel cell stack and the spring under consideration comprises:
(1) Dividing the assembly force F of the fuel cell stack by the number m of the springs distributed in the plane to serve as the selection criterion of the working compression force of the springs;
(2) On the premise of meeting the condition (1), the larger the spring flexibility coefficient is, the better the spring flexibility coefficient is in the optional buffering and compensation range of the fuel cell stack;
(3) The spring's geometric parameter diameter D is adapted to approximate the width of the bipolar plate reaction zone for uniform application of assembly force from a contact boundary condition perspective.
5. The method of claim 4, wherein the range of the spring diameter D, the range of the spring thickness t, and the range of the maximum compression h of the spring are sequentially provided on the premise that the dimension consideration condition (1) and the dimension consideration condition (2) are satisfied.
6. The design model selection method of the spring for the fuel cell stack as claimed in claim 4, wherein the working compression force of the spring is the corresponding compression force when the spring is delta =0.75 h;
and/or the diameter D of the spring is not affected by the thickness t of the spring and the maximum compression h of the spring.
7. The method for designing and selecting a spring for a fuel cell stack according to any one of claims 1 to 6, wherein the method specifically comprises:
obtaining a buffer expected value of the compression amount of the fuel cell stack and a buffer expected value of the assembly force of the fuel cell stack;
acquiring a compensation expected value of the compression amount of the fuel cell stack and a compensation expected value of the compression force;
establishing a matching relation between the diameter of the spring and the size of the bipolar plate to determine the range of the diameter D of the spring and the range of the number of the springs distributed in the plane;
establishing a functional relation between the static assembly force of the fuel cell stack and the distribution quantity of the springs in a plane so as to determine the compression force range of a single spring;
acquiring the range of the spring thickness t according to the range of the spring diameter D and the range of the compression force of a single spring;
arranging in-line springs in the vertical direction to increase the buffering and compensating capacity of the springs through the in-line springs, and determining the range of the maximum compression h of the springs and the number of the in-line disc springs according to the expected compensation value of the compression of the fuel cell stack;
and obtaining the optimal spring diameter D, the optimal maximum spring compression h and the optimal spring thickness t according to the range of the spring diameter D, the range of the maximum spring compression h and the range of the spring thickness t under the condition that the maximum flexibility coefficient is the target condition.
8. The method of claim 7, wherein the obtaining of the buffer expected value of the compression amount of the fuel cell stack and the buffer expected value of the assembly force of the fuel cell stack comprises:
establishing a mapping relation among the length of the fuel cell stack, the expansion coefficient of the bipolar plate and the operating temperature to obtain a buffer expected value of the compression amount of the fuel cell stack;
establishing a mapping relation between the pneumatic load and the reaction area of the fuel cell stack to obtain a buffer expected value of the assembly force of the fuel cell stack;
and/or the acquiring of the compensation expected value of the compression amount of the fuel cell stack and the compensation expected value of the compression force comprises: and (3) considering creep deformation of the fuel cell stack assembly force locking device under the long-term stress and relaxation of the rubber wire under the long-term load condition to obtain a compensation expected value of the compression amount of the fuel cell stack and a compensation expected value of the compression force.
9. A fuel cell stack spring, which is designed and selected by the method for designing and selecting a fuel cell stack spring according to any one of claims 1 to 8, and is applied to a fuel cell stack; the spring for the fuel cell stack is made of metal, resin or modified resin; the spring for the fuel cell stack comprises a disc spring.
10. The fuel cell stack spring according to claim 9, wherein the fuel cell stack spring is formed by laminating a plurality of single-layer modified resin layers;
the modified resin layer includes at least two fiber reinforced resin layers.
11. The fuel cell stack spring according to claim 10, wherein the at least two fiber-reinforced resin layers include at least two of a carbon fiber-reinforced epoxy resin layer, a glass fiber-reinforced epoxy resin layer, a basalt fiber-reinforced epoxy resin layer, a wood fiber-reinforced epoxy resin layer, and an aramid fiber-reinforced epoxy resin layer;
and/or the outer surface of the spring for the fuel cell stack is provided with a protective coating;
and/or the total thickness of the carbon fiber reinforced epoxy resin layer is 0.2-0.6 times of the thickness of the spring for the fuel cell stack, and the total thickness of the glass fiber reinforced epoxy resin layer is 0.8-0.4 times of the thickness of the spring for the fuel cell stack;
and/or the thickness of the single modified resin layer is 0.1 mm-0.2 mm.
12. A fuel cell stack comprising a core assembly, and a spring obtained by design-selection using the method for design-selection of a spring for a fuel cell stack according to any one of claims 1 to 8 or the spring for a fuel cell stack according to any one of claims 9 to 11.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN115663255A (en) * | 2022-12-26 | 2023-01-31 | 天津中科先进技术产业有限公司 | High-strength lightweight stack end plate and fuel cell stack |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN115663255A (en) * | 2022-12-26 | 2023-01-31 | 天津中科先进技术产业有限公司 | High-strength lightweight stack end plate and fuel cell stack |
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