Isostatic clamp, Solid-state battery cell, Battery device, and Electrical equipment

Abstract

This application discloses an isobaric clamp, a solid-state battery cell, a battery device, and an electrical device. The solid-state battery cell includes a battery body and an isobaric clamp. The battery body includes a solid electrolyte layer and an electrode layer stacked along a first direction. The isobaric clamp is used to apply a clamping force along the first direction to the battery body. The isobaric clamp includes a disc spring assembly and a movable pressure plate. The disc spring assembly is configured to have quasi-zero stiffness characteristics within its working deformation range, such that when the thickness of the battery body changes and drives the pressure plate to move, the fluctuation range of the clamping force provided by the disc spring assembly does not exceed 15% of its initial value. The disc spring assembly includes multiple disc springs of equal thickness, each disc spring having a thickness of t and a working compression stroke of h0, where h0 / t satisfies 1.5 ≤ h0 / t ≤ 1.7. The technical solution of this application can provide a stable clamping force to the battery body, improving the operational stability of the solid-state battery cell.

Description

Technical Field

[0001] This application relates to the field of batteries, and in particular to an isobaric clamp, a solid-state battery cell, a battery device, and an electrical device. Background Technology

[0002] Solid-state battery cells are the smallest independent units in solid-state battery technology. Their core feature is the use of solid electrolytes instead of liquid electrolytes in traditional lithium-ion batteries, which gives them certain advantages in terms of energy density, safety, and cycle life.

[0003] Since solid-state batteries do not contain liquid substances, their internal material interface contact stability is poor, which needs to be improved. Utility Model Content

[0004] In view of the above problems, this application provides an isobaric clamp, a solid-state battery cell, a battery device, and an electrical device, which can provide a stable clamping force for the solid-state battery and improve the operational stability of the solid-state battery cell.

[0005] In a first aspect, this application provides a solid-state battery cell, including a battery body and an isobaric clamp. The battery body includes a solid electrolyte layer and an electrode layer stacked along a first direction. The isobaric clamp is used to apply a clamping force along the first direction to the battery body. The isobaric clamp includes a disc spring assembly and a movable pressure plate. The disc spring assembly is configured to have quasi-zero stiffness characteristics within its working deformation range, such that when the thickness of the battery body changes and drives the pressure plate to move, the fluctuation range of the clamping force provided by the disc spring assembly does not exceed 15% of its initial value. The disc spring assembly includes multiple disc springs of equal thickness, each disc spring having a thickness of t and a working compression stroke of h0, where h0 / t satisfies 1.5 ≤ h0 / t ≤ 1.7.

[0006] In the technical solution of this application embodiment, the quasi-zero stiffness characteristics of the disc spring assembly provide a highly stable clamping force for the battery body. The disc spring assembly exhibits quasi-zero stiffness characteristics within its working deformation range. When the battery body undergoes thickness changes due to charge / discharge cycles, temperature variations, or mechanical vibrations, the deformation of the disc spring assembly and the clamping force show a weak nonlinear correlation. The clamping force fluctuation range is strictly controlled within ±15% of the initial value, reducing the risk of overvoltage or undervoltage caused by changes in battery thickness in traditional rigid clamps, and maintaining the stability of the internal interface of the solid-state battery cell. Stable clamping force reduces dynamic stress at the interface, lowers the risk of lithium dendrites piercing the electrolyte, and reduces the risk of localized overheating or capacity decay caused by void expansion. Furthermore, the movable pressure plate, as an intermediate connector between the disc spring assembly and the battery body, can efficiently transfer the deformation energy of the disc spring assembly to the battery body, avoiding energy loss or mechanical jamming. In particular, the disc spring assembly is selected within the range of h0 / t = 1.5 to 1.7, which falls precisely within the longest range of the quasi-zero stiffness plateau region of the disc spring. Within the same thickness variation stroke (Δh), the clamping force variation (ΔF) of this solution is smaller, resulting in more stable pressure output. The disc spring in this range maintains near-zero stiffness characteristics over a wider deformation range, meaning it can adapt to a greater range of volume variations in solid-state battery cells, offering more design margin and stronger fault tolerance. This range provides a sufficiently long flat region while ensuring the disc spring has the necessary stiffness and load capacity, achieving an optimal engineering balance between load capacity and stroke length. Therefore, the above technical solution is simple in structure, easy to implement, and achieves stable clamping of solid-state battery cells with fewer components, improving the operational stability of solid-state battery cells while also enhancing their rate performance and energy efficiency.

[0007] In some embodiments, h0 / t satisfies 1.6 ≤ h0 / t ≤ 1.7. In the above structure, the core range where h0 / t = 1.6 to 1.7 is the flattest region for quasi-zero stiffness in the force-displacement curve of the disc spring. Operating within this range, the elastic restoring force of the disc spring changes negligibly with deformation. This provides a constant pressure to the solid-state battery interface that is infinitely close to an ideal state, minimizing the slight changes in interface contact resistance caused by pressure fluctuations, resulting in a more stable voltage curve and more consistent performance during battery cycling. Within this range, the disc spring can provide the maximum and most stable output force with minimal self-deformation space, allowing for a more compact design of the isobaric clamp structure, thereby minimizing the negative impact on the volumetric and gravimetric energy densities of the solid-state cell.

[0008] In some embodiments, the fluctuation range of the clamping force does not exceed 10% of its initial value. The above-described structure controls the clamping force fluctuation within ±10%, further reducing the change in the interfacial micro-contact area caused by pressure fluctuations. Therefore, the isobaric clamp can provide continuous and optimal interfacial contact for the solid-state battery cells, reducing and stabilizing the interfacial impedance to its theoretical minimum. Stable low impedance allows for rapid and uniform ion transport, resulting in less polarization and better performance during high-rate charge and discharge. Energy loss during charge and discharge (mainly from internal resistance) is minimized, improving the battery's coulombic efficiency and energy efficiency.

[0009] In some embodiments, the thickness H of a single disc spring satisfies: 0.1 mm ≤ H ≤ 2 mm. In the above structure, a disc spring with H ≤ 2 mm exhibits higher force-displacement response sensitivity. Under the same compression stroke, its deformation is easier, allowing for a more precise response to micron-level changes in battery thickness. H ≥ 0.1 mm ensures that a single disc spring can provide an engineering-meaning, measurable deformation stroke. This allows a single disc spring to have sufficient effective stroke, enabling a disc spring assembly composed of multiple disc springs to provide a sufficiently long total stroke to reliably compensate for cumulative thickness changes in the battery during long-term cycling.

[0010] In some embodiments, the isobaric clamp includes a disc spring assembly and a first clamping plate, a second clamping plate, and a third clamping plate arranged sequentially along a first direction. The battery body is disposed between the first and second clamping plates, and the third clamping plate is disposed on the side of the second clamping plate opposite to the first clamping plate. The disc spring assembly is disposed between the second and third clamping plates. The second clamping plate, as a movable pressure plate, can reciprocate along the first direction to apply clamping force to the battery body. In the above structure, the first clamping plate, as a fixed base end, provides a reaction force fulcrum. The second clamping plate, as a movable actuating end, directly applies pressure to the battery body. The third clamping plate, as an adjustable force-applying end, is the input end of the preload force of the disc spring assembly. The disc spring assembly, as an automatically adjusting force source, is placed between the second and third clamping plates. The first and third clamping plates, as rigid support plates, can disperse any localized concentrated stress that may be generated by the disc spring assembly into uniform surface pressure, which is then transmitted to the battery body through the second clamping plate. The force transmission path is clear and direct (third clamping plate → disc spring assembly → second clamping plate → battery body → first clamping plate), with high mechanical efficiency, no intermediate redundant links, and minimal energy loss. This ensures that the elastic force generated by the disc spring can be effectively transmitted to the battery interface without loss. The second clamping plate is constrained between the first clamping plate and the disc spring assembly, and is usually used in conjunction with a guide rod (such as the connecting rod in the previous claim), so that it can only translate in the first direction (the battery thickness direction) and cannot tilt or rotate. Furthermore, the above structure replaces point contact or line contact, using a large-area surface contact to apply pressure, maximizing the protection of the brittle internal structure of the battery body and preventing it from being damaged under clamping pressure.

[0011] In some embodiments, the disc spring assembly includes multiple layers of disc springs stacked along a first direction. Each disc spring layer includes multiple disc springs arranged in an array, and the number N of disc springs in each layer satisfies: N = P / F. Here, P is the working pressure required by the isobaric clamp, and F is the average elastic force provided by a single disc spring within its quasi-zero stiffness range. In the above structure, the multi-layered, array-distributed structure allows multiple disc spring force points to collectively form a force field applied to the second clamping plate. This ensures that the interface pressure between the edge and center regions of the battery body is essentially consistent, effectively preventing failure at the edge due to insufficient pressure. Furthermore, a precise, calculable, and quantifiable design criterion is provided through specific formula calculations, transforming abstract pressure requirements into a specific number of disc springs.

[0012] In some embodiments, the number of layers M in the disc spring assembly satisfies M > I / i, where I is the expected thickness change travel of the battery body during charging and discharging, and i is the quasi-zero stiffness range travel of a single disc spring. Combining the above constraints with the formula N = P / F, by adjusting the number of layers (M) and the number of layers per layer (N), different total pressure (P) and total travel (I) requirements can be flexibly achieved within the same installation space. The formula M > I / i ensures that the total compensation travel (M*i) of the disc spring assembly is greater than the maximum cumulative thickness change (I) that may occur in a single solid-state battery cell throughout its entire lifespan. This ensures that the disc spring assembly always operates within its quasi-zero stiffness range, thereby stabilizing the clamping force fluctuation within ±10% throughout the entire battery design life, achieving long-term stability. By simply increasing the number of layers M (in series), the travel can be superimposed (total travel ≈ M*i), thus utilizing the optimal force stability of the disc springs while meeting the battery's requirement for total compensation travel. This achieves an optimal solution for performance and function.

[0013] In some embodiments, the disc spring assembly includes two layers of disc springs stacked along a first direction, each layer containing an equal number of disc springs. The disc springs in the two layers, positioned opposite each other, are connected in parallel along the first direction. In the above structure, after the two disc springs are connected in parallel, the total elastic force provided by them under the same compression stroke (displacement) is twice that of a single disc spring. This allows for greater clamping force within a limited space. By using two layers in parallel, the total output force at that location can be doubled (2F) without increasing the overall height of the clamp in the first direction. For solid-state battery systems requiring higher operating pressures (P) (such as some oxide systems), this parallel structure is a key means of meeting pressure requirements. The two disc springs connected in parallel form a more stable support unit, better resisting lateral forces and ensuring that the force is always applied perpendicularly, preventing premature fatigue failure of the disc springs due to off-center loading. Without significantly increasing cost and technical complexity, the performance of the isobaric clamp is improved, as well as the reliability and safety of the solid-state battery cells are enhanced.

[0014] In some embodiments, the disc spring pair includes a first disc spring and a second disc spring. The large end of the first disc spring abuts against the first clamping plate, and the small end faces the second clamping plate. The large end of the second disc spring abuts against the second clamping plate, and the small end faces the first clamping plate and contacts the small end of the first disc spring. The first and second disc springs are symmetrically arranged along a first direction. In the above structure, the large ends of the two conical disc springs are fixed to the two clamping plates respectively, and the small ends contact each other, forming a stable symmetrical mechanical structure. In the back-to-back combination, the lateral components of the forces generated by the two disc springs are equal in magnitude, opposite in direction, and cancel each other out. Ultimately, only the pure axial clamping force is transmitted to the battery body. This greatly reduces internal friction, making the movement of the second clamping plate extremely smooth, ensuring the high sensitivity and high mechanical efficiency of the isobaric clamp. The two disc springs are connected back-to-back in parallel, and their deformation is synchronous. The total compression stroke of this combination is slightly less than twice the stroke of a single disc spring, but much greater than that of a combination of parallel (series) disc springs. It provides double the elasticity while also providing a longer effective working stroke. This allows the combination to meet high-pressure requirements while also adapting to variations in the thickness of solid-state battery cells.

[0015] In some embodiments, the isobaric clamp further includes at least one connecting rod. A first clamping plate and a second clamping plate are fixedly connected to both ends of the connecting rod. The second clamping plate has a through hole that mates with the connecting rod. The second clamping plate is slidably connected to the connecting rod through the through hole and can reciprocate along the axial direction of the connecting rod. In the above structure, the connecting rod restricts the degree of freedom of movement of the second clamping plate, allowing it to only perform linear reciprocating motion along the axial direction of the connecting rod. The first clamping plate is supported by the connecting rod, and the spring force of the disc spring forms a closed force flow through the path "third clamping plate → connecting rod → first clamping plate," allowing pressure to be stably applied to the battery. At the same time, the robust connecting rod frame greatly improves the overall rigidity and natural frequency of the entire isobaric clamp.

[0016] Secondly, this application provides an isobaric clamp for applying a clamping force along a first direction to a battery body. The isobaric clamp includes a disc spring assembly and a pressure plate. The disc spring assembly is configured to have quasi-zero stiffness characteristics within its working deformation range, and the pressure plate is movable along the first direction. The disc spring assembly ensures that when the thickness of the battery body changes and drives the pressure plate to move, the fluctuation range of the clamping force provided by the disc spring assembly does not exceed 15% of its initial value. The disc spring assembly includes multiple disc springs of equal thickness, each disc spring having a thickness of t and a working compression stroke of h0, where h0 / t satisfies 1.5 ≤ h0 / t ≤ 1.7.

[0017] In the above structure, the disc spring assembly is selected with h0 / t ranging from 1.5 to 1.7, which falls precisely within the longest range of the disc spring's quasi-zero stiffness plateau region. Within the same thickness variation stroke (Δh), the clamping force variation (ΔF) of this scheme is smaller, achieving a more relatively "constant force" output. Disc springs in this range can maintain quasi-zero stiffness characteristics over a wider deformation range, meaning they can adapt to a greater range of volume variations in solid-state battery cells, providing more design margin and stronger fault tolerance. This range provides a sufficiently long flat region while ensuring the disc spring has the necessary stiffness and load capacity, achieving an optimal engineering balance between load capacity and stroke length. Therefore, the above technical solution is simple in structure and easy to implement, achieving stable clamping of solid-state battery cells with fewer components, improving the operational stability of solid-state battery cells, and simultaneously enhancing their rate performance and energy efficiency.

[0018] Thirdly, this application provides a battery device that includes the solid-state battery cell described in the above embodiments.

[0019] Fourthly, this application provides an electrical device that includes the battery device described in the above embodiments, the battery device being used to provide electrical energy.

[0020] The above description is only an overview of the technical solution of this application. In order to better understand the technical means of this application and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this application more obvious and understandable, the following are specific embodiments of this application. Attached Figure Description

[0021] The features, advantages, and technical effects of exemplary embodiments of this application will now be described with reference to the accompanying drawings.

[0022] Figure 1 This is a schematic diagram of the structure of a solid-state battery cell according to an embodiment of this application;

[0023] Figure 2 Load-deformation test curves for disc springs with multiple h0 / t values;

[0024] Figure 3 This is a schematic diagram of the structure of a solid-state battery cell according to another embodiment of this application;

[0025] Figure 4 This is a schematic diagram of the structure of a solid-state battery cell according to another embodiment of this application;

[0026] Figure 5 This is a schematic diagram of the structure of an isobaric fixture according to an embodiment of this application.

[0027] Detailed Explanation of Reference Numerals

[0028] 1. Solid-state battery cell; X, first direction; 10. Battery body; 20. Isobaric clamp; 201. Disc spring assembly; 202. Pressure plate; 203. First clamping plate; 204. Second clamping plate; 205. Third clamping plate; 206. First disc spring; 207. Second disc spring; 208. Spring pair; 209. Through hole. Detailed Implementation

[0029] The embodiments of the technical solution of this application will now be described in detail with reference to the accompanying drawings. These embodiments are only used to more clearly illustrate the technical solution of this application and are therefore merely examples, and should not be used to limit the scope of protection of this application.

[0030] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms “comprising” and “having”, and any variations thereof, in the specification, claims, and foregoing description of the drawings are intended to cover non-exclusive inclusion.

[0031] In the description of the embodiments of this application, technical terms such as "first" and "second" are used only to distinguish different objects and should not be construed as indicating or implying relative importance or implicitly specifying the number, specific order, or primary and secondary relationship of the indicated technical features. In the description of the embodiments of this application, "multiple" means two or more, unless otherwise explicitly defined.

[0032] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0033] In the description of the embodiments in this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0034] In the description of the embodiments of this application, the term "multiple" refers to two or more (including two), similarly, "multiple sets" refers to two or more (including two sets), and "multiple pieces" refers to two or more (including two pieces).

[0035] In the description of the embodiments of this application, the technical terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of this application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of this application.

[0036] In the description of the embodiments of this application, unless otherwise expressly specified and limited, technical terms such as "installation," "connection," "joining," and "fixing" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in the embodiments of this application can be understood according to the specific circumstances.

[0037] Solid-state battery cells typically consist of stacked solid electrolyte and electrode layers. The solid-solid interface between the electrode layers and the solid electrolyte in a solid-state battery cell is relatively poor, easily leading to increased interfacial impedance. Due to the characteristics of solid-state batteries, close contact between the solid electrolyte and the electrodes is required, necessitating the application of pressure to ensure normal charging and discharging. Similarly, during cell testing, pressure is applied to the cell to guarantee normal charging and discharging, requiring the use of clamps.

[0038] In related technologies, fixing clamps at fixed positions restricts battery deformation, preventing normal expansion and contraction. This results in the battery not receiving the required pressure or exceeding the operating pressure, leading to reduced battery performance. Alternatively, some solutions offer automated pressure control, where sensors detect the pressure on the battery and transmit it to a control system (e.g., a processor, microcontroller). The control system adjusts the pressure based on the difference between the actual pressure and the operating voltage. However, these solutions are bulky, costly, and complex to implement. Automated pressure control inevitably requires sensors, control systems, and pressure structures, which occupy significant volume, leading to a substantial decrease in energy density after battery assembly, defeating the purpose of improving battery performance. The cost of automated control structures is often one to several orders of magnitude higher than the battery manufacturing cost. Automated control requires selecting sensors, control systems, and control structures based on the specific battery used, resulting in long development cycles and complex technical routes.

[0039] To address the aforementioned issues, embodiments of this application provide a solid-state battery cell that utilizes the quasi-zero stiffness characteristics of a disc spring assembly to provide a highly stable clamping force for the battery body. The disc spring assembly exhibits quasi-zero stiffness within its operating deformation range. When the battery body undergoes thickness changes due to charge-discharge cycles, temperature variations, or mechanical vibrations, the deformation of the disc spring assembly and the clamping force show a weak nonlinear correlation. The clamping force fluctuation range is strictly controlled within ±15% of the initial value, reducing the risk of overvoltage or undervoltage caused by changes in battery thickness in the rigid clamp and maintaining the stability of the internal interface of the solid-state battery cell. The stable clamping force reduces dynamic stress at the interface, lowers the risk of lithium dendrites piercing the electrolyte, and reduces the risk of localized overheating or capacity decay caused by void expansion. Furthermore, the movable pressure plate, acting as an intermediate connector between the disc spring assembly and the battery body, efficiently transfers the deformation energy of the disc spring assembly to the battery body, avoiding energy loss or mechanical jamming.

[0040] In particular, the disc spring assembly is selected within the range of h0 / t = 1.5 to 1.7, which falls precisely within the longest range of the disc spring's quasi-zero stiffness plateau region. Within the same thickness variation stroke (Δh), the clamping force variation (ΔF) of this scheme is smaller, enabling a more consistent pressure output. Disc springs in this range can maintain quasi-zero stiffness characteristics over a wider deformation range, accommodating a greater range of volume variations in solid-state battery cells, providing more design margin and stronger fault tolerance. This range provides a sufficiently long flat region while ensuring the disc spring has the necessary stiffness and load capacity, achieving an optimal engineering balance between load capacity and stroke length. Therefore, the above technical solution is simple in structure, easy to implement, and achieves stable clamping of solid-state battery cells with fewer components, improving the operational stability of solid-state battery cells while simultaneously enhancing their rate performance and energy efficiency.

[0041] Please refer to the reference. Figures 1 to 3 , Figure 1 This is a schematic diagram of the structure of a solid-state battery cell 1 according to an embodiment of this application. Figure 2 Load-deformation test curves for disc springs with multiple h0 / t values. Figure 3 This is a schematic diagram of the structure of a solid-state battery cell 1 according to another embodiment of this application.

[0042] As shown in the figure, an embodiment of this application provides a solid-state battery cell 1, including a battery body 10 and an isobaric clamp 20. The battery body 10 includes a solid electrolyte layer and an electrode layer stacked along a first direction X. The isobaric clamp 20 is used to apply a clamping force along the first direction X to the battery body 10. The isobaric clamp 20 includes a disc spring assembly 201 and a movable pressure plate 202. The disc spring assembly 201 is configured to have quasi-zero stiffness characteristics within its working deformation range, such that when the thickness of the battery body 10 changes and drives the pressure plate 202 to move, the fluctuation range of the clamping force provided by the disc spring assembly 201 does not exceed 15% of its initial value. The disc spring assembly 201 includes a plurality of disc springs with equal plate thickness, the plate thickness of a single disc spring is t, the working compression stroke is h, and h / t satisfies 1.5≤h0 / t≤1.7.

[0043] like Figure 2 The figure shows the load-deformation test curves for disc springs with different h0 / t values. The horizontal axis represents the percentage of the disc spring's deformation relative to its net height, and the vertical axis represents the load borne at the corresponding percentage of deformation. As can be seen from the figure, the three curves within the range of 1.5 ≤ h0 / t ≤ 1.7 all exhibit significantly better mechanical characteristics than disc springs with other parameters: their load-deformation curves contain a significant and flat "quasi-zero stiffness region" (marked by the dashed box in the figure), meaning that within this deformation range, the load changes very little, while the disc spring's deformation can vary considerably.

[0044] When h0 / t < 1.5, the load-deformation curve of the disc spring is approximately a straight line, exhibiting positive stiffness characteristics, meaning that the deformation increases almost linearly with increasing load; the greater the load, the greater the deformation. When h0 / t > 1.7, the load-deformation curve of the disc spring is approximately a parabola, exhibiting nonlinear stiffness characteristics: before the inflection point of the curve, the deformation increases with increasing load (positive stiffness stage); after the inflection point, it enters the negative stiffness stage, where continued increase in deformation leads to a decrease in load.

[0045] In the technical solution of this application embodiment, the quasi-zero stiffness characteristic of the disc spring assembly 201 provides a highly stable clamping force for the battery body 10. The disc spring assembly 201 exhibits quasi-zero stiffness within its working deformation range. When the thickness of the battery body 10 changes due to charge / discharge cycles, temperature variations, or mechanical vibrations, the deformation of the disc spring assembly 201 and the clamping force show a weak nonlinear correlation. The clamping force fluctuation range is strictly controlled within ±15% of the initial value, reducing the risk of overvoltage or undervoltage caused by changes in battery thickness in traditional rigid clamps, and maintaining the stability of the internal interface of the solid-state battery cell 1. A stable clamping force reduces dynamic stress at the interface, lowers the risk of lithium dendrites piercing the electrolyte, and reduces the risk of localized overheating or capacity decay caused by void expansion. Furthermore, the movable pressure plate 202, as an intermediate connector between the disc spring assembly 201 and the battery body 10, can efficiently transfer the deformation energy of the disc spring assembly 201 to the battery body 10, avoiding energy loss or mechanical jamming.

[0046] In particular, the disc spring assembly 201 selects a h0 / t range of 1.5 to 1.7, which happens to be located in the longest range of the disc spring's quasi-zero stiffness plateau region. Within the same thickness variation stroke (Δh), the clamping force variation (ΔF) of this design is smaller, achieving a relatively "constant force" output. Disc springs in this range can maintain quasi-zero stiffness characteristics over a larger deformation range; simply put, the disc spring can apply nearly equal clamping force to the solid-state battery cell 1 as its thickness changes. Therefore, it means it can adapt to a wider range of volume variations in the solid-state battery cell 1, with more design margin and stronger fault tolerance. This range provides a sufficiently long flat region while ensuring the disc spring has the necessary stiffness and load capacity, achieving the optimal engineering balance between load capacity and stroke length.

[0047] Therefore, the above technical solution has a simple structure and is easy to implement. It achieves stable clamping of the solid-state battery cell 1 with fewer components, improves the operational stability of the solid-state battery cell 1, and at the same time improves the rate performance and energy efficiency of the solid-state battery cell 1.

[0048] In some embodiments of this application, h0 / t satisfies 1.6 ≤ h0 / t ≤ 1.7. In the above structure, the core range where h0 / t = 1.6 to 1.7 is the flattest quasi-zero stiffness region in the force-displacement curve of the disc spring. Operating within this range, the elastic restoring force of the disc spring changes negligibly with deformation. This provides a constant pressure to the solid-state battery interface that is infinitely close to an ideal state, minimizing the slight changes in interface contact resistance caused by pressure fluctuations, resulting in a more stable voltage curve and more consistent performance during battery cycling. Within this range, the disc spring can provide the maximum and most stable output force with minimal self-deformation space. This allows for a more compact design of the isobaric clamp 20, thereby minimizing the negative impact on the volumetric and gravimetric energy densities of the solid-state cell.

[0049] In some embodiments of this application, the fluctuation range of the clamping force does not exceed 10% of its initial value. The above-described structure controls the clamping force fluctuation within ±10%, further reducing the change in the interfacial micro-contact area caused by pressure fluctuations. Therefore, the isobaric clamp 20 can provide continuous and optimal interfacial contact for the solid-state battery cell 1, reducing and stabilizing the interfacial impedance to its theoretical minimum. Stable low impedance allows for rapid and uniform ion transport, resulting in less polarization and better performance during high-rate charge and discharge. Energy loss during charge and discharge (mainly from internal resistance) is minimized, improving the battery's coulombic efficiency and energy efficiency.

[0050] In some embodiments of this application, the thickness H of a single disc spring satisfies: 0.1mm ≤ H ≤ 2mm. In the above structure, the disc spring with H ≤ 2mm has higher force-displacement response sensitivity.

[0051] Under the same compression stroke, its deformation is easier, allowing for a more precise response to micron-level changes in battery thickness. H ≥ 0.1 mm ensures that a single disc spring provides an engineering-meaning, measurable deformation stroke. This ensures sufficient effective stroke for a single disc spring, enabling the disc spring array 201, composed of multiple disc springs, to provide a sufficiently long total stroke to reliably compensate for cumulative thickness changes in the battery over long-term cycling. The pressure distribution of the disc spring matrix is ​​more uniform compared to a single disc spring. Without a separator, the pressure exerted by the disc spring on the battery surface is in the form of a hollow ring. Under the same operating pressure, using a single large-sized disc spring causes pressure concentration in the hollow ring of the disc spring's outer diameter, resulting in significant pressure non-uniformity and requiring a thicker separator for pressure averaging. The advantage of using a small-sized disc spring matrix is ​​its uniform pressure distribution, allowing for the use of thinner separators and weight reduction.

[0052] like Figure 4As shown, in some embodiments of this application, the isobaric clamp 20 includes a disc spring assembly 201 and a first clamping plate 203, a second clamping plate 204, and a third clamping plate 205 arranged sequentially along a first direction X. The battery body 10 is disposed between the first clamping plate 203 and the second clamping plate 204, and the third clamping plate 205 is disposed on the side of the second clamping plate 204 opposite to the first clamping plate 203. The disc spring assembly 201 is disposed between the second clamping plate 204 and the third clamping plate 205. The second clamping plate 204 serves as a movable pressure plate 202, capable of reciprocating along the first direction X to apply a clamping force to the battery body 10. The second clamping plate 204 is thus a movable pressure plate 202.

[0053] In the above structure, the first clamping plate 203 serves as a fixed base end, providing a fulcrum for the reaction force. The second clamping plate 204 serves as a movable actuating end, directly applying pressure to the battery body 10. The third clamping plate 205 serves as an adjustable force-applying end, acting as the input end for the preload of the disc spring assembly 201. The disc spring assembly 201, as an automatically adjusting force source, is positioned between the second and third clamping plates 205. The first and third clamping plates 203 and 205, acting as rigid support plates, can disperse any localized concentrated stress that may be generated by the disc spring assembly 201 into uniform surface pressure, which is then transmitted to the battery body 10 via the second clamping plate 204. The force transmission path is clear and direct (third clamping plate 205 → disc spring assembly 201 → second clamping plate 204 → battery body 10 → first clamping plate 203), with high mechanical efficiency, no intermediate redundant links, and minimized energy loss. This ensures that the elastic force generated by the disc spring can be effectively transmitted to the battery interface without loss. The second clamping plate 204 is constrained between the first clamping plate 203 and the disc spring assembly 201, and is usually used in conjunction with a connecting rod to ensure that it can only translate in the first direction X, and cannot tilt or rotate. Furthermore, the above structure replaces point contact or line contact, and applies pressure with a large-area surface contact, maximizing the protection of the fragile internal structure of the battery body 10 and preventing it from being damaged under clamping pressure.

[0054] In some embodiments of this application, the disc spring assembly 201 includes multiple disc spring layers stacked along a first direction X. Each disc spring layer includes multiple disc springs arranged in an array, and the number N of disc springs in each disc spring layer satisfies: N = P / F. Wherein, P is the working pressure required to be provided by the isobaric fixture 20, and F is the average elastic force provided by a single disc spring in its quasi-zero stiffness range.

[0055] By employing a multi-layered structure with arrayed distribution in each layer, multiple disc spring force points collectively form a force field applied to the second clamping plate 204. This ensures that the interface pressure between the edge and center regions of the battery body 10 is essentially consistent, effectively preventing premature failure at the edges due to insufficient pressure. Furthermore, a precise, calculable, and quantifiable design principle is provided through specific formula calculations, transforming abstract pressure requirements into a concrete number of disc springs.

[0056] In some embodiments of this application, the number of layers M of the disc spring assembly 201 satisfies M > I / i, where I is the expected thickness change stroke of the battery body 10 during charging and discharging, and i is the quasi-zero stiffness range stroke of a single disc spring. Combining the above constraints with the formula N = P / F, by adjusting the number of layers (M) and the number of layers per layer (N), different total pressure (P) and total stroke (I) requirements can be flexibly achieved within the same installation space. The formula M > I / i ensures that the total compensation stroke (M*i) of the disc spring assembly 201 is greater than the maximum cumulative thickness change (I) that the solid-state battery cell 1 may experience throughout its entire lifespan. This ensures that the disc spring assembly 201 always operates within its quasi-zero stiffness range, thereby stabilizing the clamping force fluctuation within ±10% throughout the entire battery design life, achieving long-term stability. By simply increasing the number of layers M (in series), the stroke can be superimposed (total stroke ≈ M*i), thus utilizing the optimal force stability of the disc springs while meeting the battery's requirement for total compensation stroke. This achieves an optimal solution for performance and function.

[0057] The force-displacement curve of the disc spring obtained from this formula shows that h0 / t has a relatively long quasi-zero stiffness range between 1.6 and 1.7. When designing the disc spring, ensure that h0 / t is between 1.6 and 1.7. Plot the theoretical force-displacement curve of the disc spring using the above formula, and adjust the disc spring parameters to ensure that the quasi-zero stiffness range of this curve meets the design requirements. After fabricating the actual disc spring, fine-tune the disc spring parameters based on the measured force-displacement curve to complete the disc spring design.

[0058] Specifically, the disc spring load formula can be used:

[0059]

[0060] Disc springs are designed for battery bodies 10 with different shapes and thicknesses. Here, E is Young's modulus, μ is Poisson's ratio (commonly 0.3), D and d are the outer and inner diameters respectively, h is the net height (maximum deformation), t is the disc spring thickness, and f is the deformation. The load factor ω is:

[0061] Where C = D / d

[0062] By plotting the theoretical force-displacement curve of the disc spring using the above formula, its quasi-zero stiffness range can be clearly identified.

[0063] P represents the requirements for maintaining normal operation of the battery body 10. It is determined by the electrode and electrolyte material system of the battery. For example, sulfide solid electrolytes may require a pressure of 10-20 MPa to ensure interfacial contact, while oxide systems may require a pressure of more than 20 MPa. This value is determined through electrochemical experiments. F represents the characteristics of the disc spring itself. After determining the model of the disc spring (i.e., determining parameters such as D, d, h, t, etc.), the average value of the spring force in its "quasi-zero stiffness range" is calculated using the disc spring load formula. N is the design result, which indicates how many disc springs need to be connected in parallel in each layer to synthesize the total force in order to meet the pressure requirements of the battery. I is determined by the battery's chemical system (such as the expansion rate of the lithium metal anode), design capacity, and expected lifespan. For example, the I value of a battery whose thickness increases by 10 μm after 100 cycles is much smaller than that of a battery whose thickness increases by 50 μm after 1000 cycles. The effective stroke i of a single disc spring is another characteristic of the disc spring itself. It refers to the deformation length corresponding to the "quasi-zero stiffness region" on its force-displacement curve. The number of disc spring layers M represents the number of layers, which means calculating how many layers of disc springs need to be connected in series to provide sufficient total buffer stroke.

[0064] The steps for designing different disc spring assemblies 201 using the above formula are usually as follows:

[0065] S1. Determine battery requirements: Obtain the battery's P (required pressure) and I (expected thickness change) through experiments.

[0066] S2. Initial selection of disc spring model: Customize a standard disc spring with an h0 / t ratio between 1.5 and 1.7 according to the installation space (diameter, height).

[0067] S3. Calculate disc spring parameters: Use the disc spring load formula to calculate the F (average spring force) and i (effective stroke) of the disc spring.

[0068] S4. Calculate the layout: Calculate the number of disc springs required for each layer according to N=P / F, and calculate the minimum number of layers required according to M=I / i, where N and M are selected by rounding up.

[0069] The following is a specific example to illustrate this.

[0070] S1. Determine battery requirements

[0071] Electrochemical testing determined that this battery requires a constant interfacial pressure of 15 MPa to achieve optimal performance. The electrode area of ​​the battery body is 10 cm². 2 The required total clamping force is: P = pressure × area = 15,000,000 Pa × 0.001 m 2=15,000N. Thickness variation range (I): Accelerated cycling tests and model predictions indicate that the maximum cumulative thickness variation of the lithium metal anode and interface is 0.1 mm over the entire battery lifespan.

[0072] S2, Initial Selection of Disc Spring Model

[0073] Material: 51CrV4 (common spring steel), Young's modulus (E): 206,000 N / mm 2 Given: Poisson's ratio (μ): 0.3, outer diameter of disc spring (D): 22mm, inner diameter of disc spring (d): 11.2mm, thickness of disc spring (t): 0.8mm, clearance height (h): 1.3mm, the following can be calculated:

[0074] h / t = 1.3 / 0.8 = 1.625;

[0075] C = D / d = 22 / 11.2 ≈ 1.964;

[0076] ω=((C+1) / (C-1)-2 / ln(C))*(C / (C-1))^2;

[0077] Substituting the values, we get: ω≈2.978.

[0078] S3, Calculate disc spring parameters

[0079] Substituting the parameters into the disc spring load formula, the load P under different deformations f is calculated. For this disc spring, the load P fluctuates slightly between 615N and 635N within the deformation range of f from 0.65mm to 0.85mm. Therefore: the average spring force of a single disc spring F = (615 + 635) / 2 ≈ 625N. The effective stroke of a single disc spring i = 0.85 - 0.65 = 0.20mm.

[0080] S4, Calculation Layout

[0081] Based on N = P / F, N = 15,000N / 625N = 24 (cells). Based on M > I / i, M > 0.1mm / 0.20mm = 0.5. Layers 1, 2, and 3 can be selected; to ensure long-term reliability and provide a safety margin, layer 2 is chosen. Layer 2 provides a total compensation travel of 2 × 0.20mm = 0.40mm, which is greater than the battery requirement of 0.10mm, providing sufficient design margin.

[0082] Based on the above calculations, we designed an optimized pressure clamp disc spring assembly 201 configuration for this solid-state battery, which requires a clamping force of 15,000N and has a thickness variation of 0.1mm: 2 layers, 12 disc springs per layer. It provides a clamping force of 15,000N (15MPa on 10cm). 2It provides a compensation stroke of 0.40mm. Throughout the stroke, clamping force fluctuations are controlled within a very small range (615N to 635N). The above calculations yield the optimal layout: a two-layer disc spring design, with 12 disc springs in each layer.

[0083] In some embodiments of this application, the disc spring assembly 201 includes two layers of disc springs stacked along a first direction X. Each layer contains an equal number of disc springs, and the disc springs in opposite positions are connected in parallel along the first direction X. In the above structure, after the two disc springs are connected in parallel, the total elastic force they provide under the same compression stroke (displacement) is twice that of a single disc spring. It can provide greater clamping force in a limited space. By using two layers in parallel, the total output force at that location can be doubled (2F) without increasing the overall height of the clamp in the first direction X. For solid-state battery systems that require higher operating pressure (P) (such as some oxide systems), this parallel structure is a key means to meet pressure requirements. The two disc springs connected in parallel form a more stable support unit, which can better resist lateral forces, ensure that the force is always applied perpendicularly, and prevent premature fatigue failure of the disc springs due to off-center loading. Without significantly increasing cost and technical complexity, the performance of the isobaric clamp 20 and the reliability and safety of the solid-state battery cell 1 are improved.

[0084] In some embodiments of this application, the disc spring pair includes a first disc spring 206 and a second disc spring 207. The large end of the first disc spring 206 abuts against the third clamping plate 205, and the small end faces the second clamping plate 204. The large end of the second disc spring 207 abuts against the second clamping plate 204, and the small end faces the third clamping plate 205 and contacts the small end of the first disc spring 206. The first disc spring 206 and the second disc spring 207 are symmetrically arranged along a first direction X.

[0085] In the above structure, the large ends of two conical disc springs are fixed to two clamping plates respectively, and the small ends are in contact with each other, forming a stable symmetrical mechanical structure. In the back-to-back combination, the lateral components of the forces generated by the two disc springs are equal in magnitude, opposite in direction, and cancel each other out. Ultimately, only the pure axial clamping force is transmitted to the battery body 10. This structure reduces internal friction, making the movement of the second clamping plate 204 extremely smooth, ensuring the high sensitivity and high mechanical efficiency of the isobaric clamp 20. The two disc springs are connected back-to-back in parallel, and their deformation is synchronized. The total compression stroke of this combination is slightly less than twice the stroke of a single disc spring, but much greater than that of a combination of parallel (series) disc springs. While providing double the elasticity, it also provides a longer effective working stroke. This allows the combination to meet high pressure requirements and adapt to thickness variations in the solid-state battery cell 1.

[0086] In some embodiments of this application, the isobaric clamp 20 further includes at least one connecting rod, optionally four connecting rods. The first clamping plate 203 and the third clamping plate 205 are fixedly connected to both ends of the connecting rod. The second clamping plate 204 has a through hole 209 that mates with the connecting rod. The second clamping plate 204 is slidably connected to the connecting rod through the through hole 209 and can reciprocate along the axial direction of the connecting rod.

[0087] In the above structure, the connecting rod restricts the degree of freedom of movement of the second clamping plate 204, allowing it to only reciprocate linearly along the axial direction of the connecting rod (i.e., the first direction X / battery thickness direction). The first clamping plate 203 is supported by the connecting rod, and the spring force of the disc spring forms a closed force flow through the path "third clamping plate 205 → connecting rod → first clamping plate 203", allowing pressure to be stably applied to the battery. The robust connecting rod frame greatly improves the overall rigidity and natural frequency of the entire isobaric clamp 20.

[0088] In some alternative embodiments, the solid-state battery cell 1 includes a battery body 10 and an isobaric clamp 20. The battery body 10 includes a solid electrolyte layer and an electrode layer stacked along a first direction X. The isobaric clamp 20 is used to apply a clamping force along the first direction X to the battery body 10. The isobaric clamp 20 includes a disc spring assembly 201 and a movable pressure plate 202. The disc spring assembly 201 is configured to have quasi-zero stiffness characteristics within its working deformation range, such that when the thickness of the battery body 10 changes and drives the pressure plate 202 to move, the fluctuation range of the clamping force provided by the disc spring assembly 201 does not exceed 10% of its initial value. The disc spring assembly 201 includes a plurality of disc springs with equal plate thickness, each disc spring having a plate thickness of t and a working compression stroke of h0, where h0 / t satisfies 1.5 ≤ h0 / t ≤ 1.7. The thickness H of each disc spring satisfies: 0.1 mm ≤ H ≤ 2 mm. The isobaric clamp 20 includes a first clamping plate 203, a second clamping plate 204, a third clamping plate 205, and a disc spring assembly 201 arranged sequentially along a first direction X. The battery body 10 is disposed between the first clamping plate 203 and the second clamping plate 204. The third clamping plate 205 is disposed on the side of the second clamping plate 204 opposite to the first clamping plate 203. The disc spring assembly 201 is disposed between the second clamping plate 204 and the third clamping plate 205. The second clamping plate 204 serves as a movable pressure plate 202, capable of reciprocating along the first direction X to apply a clamping force to the battery body 10. The isobaric clamp 20 also includes at least one connecting rod. The first clamping plate 203 and the second clamping plate 204 are fixedly connected to both ends of the connecting rod. The second clamping plate 204 has a through hole 209 that mates with the connecting rod. The second clamping plate 204 is slidably connected to the connecting rod through the through hole 209 and is capable of reciprocating along the axial direction of the connecting rod. The disc spring assembly 201 includes two layers of disc springs stacked along a first direction X, each layer including 12 disc springs arranged in an array.

[0089] like Figure 5 As shown, an embodiment of this application provides an isobaric clamp 20 for applying a clamping force along a first direction X to a battery body 10. The isobaric clamp 20 includes a disc spring assembly 201 and a pressure plate 202. The disc spring assembly 201 is configured to have quasi-zero stiffness characteristics within its working deformation range, and the pressure plate 202 is movable along the first direction X. The disc spring assembly 201 ensures that when the thickness of the battery body 10 changes and drives the pressure plate 202 to move, the fluctuation range of the clamping force provided by the disc spring assembly 201 does not exceed 15% of its initial value. The disc spring assembly 201 includes multiple disc springs of equal thickness, each disc spring having a thickness of t and a working compression stroke of h0, where h0 / t satisfies 1.5 ≤ h0 / t ≤ 1.7.

[0090] In the above structure, the disc spring assembly 201 is selected with h0 / t ranging from 1.5 to 1.7, which falls precisely within the longest range of the disc spring's quasi-zero stiffness plateau region. Within the same thickness variation stroke (Δh), the clamping force variation (ΔF) of this scheme is smaller, achieving a more relatively "constant force" output. The disc spring in this range can maintain quasi-zero stiffness characteristics over a larger deformation range, meaning it can adapt to a wider range of volume changes in the solid-state battery cell 1, providing greater design margin and stronger fault tolerance. This range provides a sufficiently long flat region while ensuring the disc spring has the necessary stiffness and load capacity, achieving an optimal engineering balance between load capacity and stroke length. Therefore, the above technical solution is simple in structure, easy to implement, and achieves stable clamping of the solid-state battery cell 1 with fewer components, improving the operational stability of the solid-state battery cell 1, while also improving its rate performance and energy efficiency.

[0091] Embodiments of this application provide a battery device including the solid-state battery cell 1 described in the above embodiments. Embodiments of this application also provide an electrical device including the battery device described in the above embodiments, the battery device being used to provide electrical energy. Both the battery device and the electrical device in the embodiments of this application include the aforementioned solid-state battery cell 1, thus achieving the aforementioned technical effects, and will not be elaborated further here.

[0092] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and not to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application, and they should all be covered within the scope of the claims and specification of this application. In particular, as long as there is no structural conflict, the various technical features mentioned in the embodiments can be combined in any way. This application is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A solid-state battery cell, characterized in that, include: The battery body includes a solid electrolyte layer and an electrode layer stacked along a first direction; An isobaric clamp is used to apply a clamping force along the first direction to the battery body. The isobaric clamp includes a disc spring assembly and a movable pressure plate. The disc spring assembly is configured to have quasi-zero stiffness characteristics within its working deformation range, such that when the thickness of the battery body changes and drives the pressure plate to move, the fluctuation range of the clamping force provided by the disc spring assembly does not exceed 15% of its initial value. The disc spring assembly includes multiple disc springs with equal plate thickness. The plate thickness of a single disc spring is t, and the working compression stroke is h0, where h0 / t satisfies 1.5≤h0 / t≤1.

7.

2. The solid-state battery cell according to claim 1, characterized in that, The h0 / t condition satisfies 1.6≤h0 / t≤1.

7.

3. The solid-state battery cell according to claim 2, characterized in that, The fluctuation range of the clamping force shall not exceed 10% of its initial value.

4. The solid-state battery cell according to claim 1, characterized in that, The thickness H of a single disc spring satisfies: 0.1mm ≤ H ≤ 2mm.

5. The solid-state battery cell according to any one of claims 1-4, characterized in that, The isobaric clamp includes the disc spring assembly and a first clamping plate, a second clamping plate, and a third clamping plate arranged sequentially along the first direction. The battery body is disposed between the first clamping plate and the second clamping plate, the third clamping plate is disposed on the side of the second clamping plate opposite to the first clamping plate, and the disc spring assembly is disposed between the second clamping plate and the third clamping plate. The second clamping plate, which serves as the movable pressure plate, can reciprocate along the first direction to apply a clamping force to the battery body.

6. The solid-state battery cell according to claim 5, characterized in that, The disc spring assembly comprises multiple layers of disc springs stacked along a first direction. Each disc spring layer includes multiple disc springs arranged in an array. The number N of disc springs in each disc spring layer satisfies: N = P / F. Wherein, P is the working pressure required by the isobaric fixture, and F is the average elastic force provided by a single disc spring within its quasi-zero stiffness range.

7. The solid-state battery cell according to claim 6, characterized in that, The number of layers M of the disc spring assembly satisfies M>I / i, where I is the expected thickness change stroke of the battery body during charging and discharging, and i is the quasi-zero stiffness range stroke of a single disc spring.

8. The solid-state battery cell according to claim 7, characterized in that, The disc spring assembly includes two disc spring layers stacked along the first direction. Each disc spring layer contains an equal number of disc springs, and the disc springs in opposite positions in the two disc spring layers are connected in parallel along the first direction.

9. The solid-state battery cell according to claim 8, characterized in that, The disc spring pair includes: The first disc spring has its large end abutting against the first clamping plate and its small end facing the second clamping plate. The second disc spring has its large end abutting against the second clamping plate, and its small end facing the first clamping plate and contacting the small end of the first disc spring. The first disc spring and the second disc spring are symmetrically arranged along the first direction.

10. The solid-state battery cell according to any one of claims 6-9, characterized in that, The isobaric clamp further includes at least one connecting rod. The first clamping plate and the second clamping plate are fixedly connected to both ends of the connecting rod. The second clamping plate is provided with a through hole that cooperates with the connecting rod. The second clamping plate is slidably connected to the connecting rod through the through hole and can reciprocate along the axial direction of the connecting rod.

11. An isobaric clamp, characterized in that, The isobaric clamp is used to apply a clamping force along a first direction to the battery body, and includes: The disc spring assembly is configured to have quasi-zero stiffness characteristics within its operating deformation range; The pressure plate can move along the first direction; The disc spring assembly ensures that when the thickness of the battery body changes and the pressure plate moves, the fluctuation range of the clamping force provided by the disc spring assembly does not exceed 15% of its initial value. The disc spring assembly includes multiple disc springs with equal plate thickness. The plate thickness of a single disc spring is t, and the working compression stroke is h0. h0 / t satisfies 1.5≤h0 / t≤1.

7.

12. A battery device, characterized in that, Includes solid-state battery cells as described in any one of claims 1-10.

13. An electrical appliance, characterized in that, The electrical equipment includes the battery device as described in claim 12, the battery device being used to provide electrical energy.

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