Design analysis and test verification of a rigid–flexible, dual-mode coupling support structure for space-based rectangular curved prisms

Xin-Yin Jia; Xin-Yin Jia; Fei-Cheng Wang; Li-Bo Li; Zhao-Hui Zhang; Jia Liu; Bing-Liang Hu

doi:10.1364/AO.431394

Applied Optics
Vol. 60,
Issue 25,
pp. 7563-7573
(2021)
•https://doi.org/10.1364/AO.431394

Design analysis and test verification of a rigid–flexible, dual-mode coupling support structure for space-based rectangular curved prisms

Xin-Yin Jia, Fei-Cheng Wang, Li-Bo Li, Zhao-Hui Zhang, Jia Liu, and Bing-Liang Hu

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Xin-Yin Jia, Fei-Cheng Wang, Li-Bo Li, Zhao-Hui Zhang, Jia Liu, and Bing-Liang Hu, "Design analysis and test verification of a rigid–flexible, dual-mode coupling support structure for space-based rectangular curved prisms," Appl. Opt. 60, 7563-7573 (2021)

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Abstract

In view of the functional requirements of high reliability and stability support of optical components of space remote sensors, a rigid–flexible, dual-mode coupling support structure for space-based rectangular curved prisms (SRCPs) was designed. In-depth studies of the support principle and engineering realization of the SRCPs and optimization of the flexible adhesive structure were performed. Static and dynamic simulations were conducted on the mirror subassembly by means of finite element analysis, and test verification was also performed. The tests revealed that the surface shape error of the mirror subassembly after mechanical testing was ${0.021}\lambda$, the displacement of the mirror body was 0.008 mm, the inclination angle was $\sim 0.8^{\prime\prime}$, the mass of the mirror subassembly was 4.79 kg, the fundamental frequency was 283 Hz, and the maximum amplification of the total rms acceleration was 4.37. All indexes were superior to those of the design requirements. On this basis, bonding tests and mechanical tests of a rectangular curved prism reflector, a rectangular curved prism, and a rectangular plane reflector employing this proposed support structure were continued. The test results verified the reliability, stability, and universal applicability of the proposed rigid–flexible, dual-mode peripheral bonding support structure.

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Data Availability

Data underlying the results presented in this paper are not publicly available at this time but may be obtained from the authors upon reasonable request.

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Part Name	Material	Elasticity Modulus (GPa)	Poisson’s Ratio	Density ( $g \cdot {c m}^{- 3}$ )	Thermal Expansion Coefficient ( $10^{- 6} m \cdot^{\circ} C^{- 1}$ )
Curved prism	Fused quartz	67	0.2	2.2	0.5
Mirror frame	ZTC4	114	029	4.4	8.9
Adhesive structure	4J36 Inval alloy	145	0.25	8.1	0.5
Adjustment pad	TC4	109	0.28	4.44	9.1
Positioning pads	2A12T4	69	0.33	2.71	23.9
Fixing clamps	TC4	109	0.28	4.44	9.1

Mode Number	Frequency (Hz)	Modal Effective Mass Factor (%)
Mode Number	Frequency (Hz)	$X$	$Y$	$Z$
1	287.5	56.21^a	0.005	0.58
2	375.8	0.04	64.05^a	4.37
3	649.9	9.43	0.09	0.12
4	772.2	0.52	9.12	17.27^a
5	836.4	0.03	2.81	12.93
6	1057.6	6.01	0.004	0.01
7	1360.3	6.81	0.05	0.14
8	1493.4	0.004	0.08	49.11
9	1562.3	0.025	3.13	0.17
10	2204.7	2.40	0.003	0.14
Total effective mass factor (%)		81.48	79.34	84.84

Direction	Frequency (Hz)	Magnitude
$X$	5–12	5.2 mm (one-side peak)
	12–25	3 g
	25–30	3 g–2.5 g
	30–100	2.5 g
$Y$	5–12	5.2 mm (one-side peak)
	12–25	3 g
	25–26	3 g–6 g
	26–30	6 g
	30–55	6 g–4 g
	55–100	4 g–2 g
$Z$	5–10	5.2 mm (one-side peak)
	10–30	2 g
	30–35	2 g–4 g
	35–70	4 g
	70–75	4 g–2 g
	75–100	2 g

Parameter	Range	Magnitude
Frequency (Hz)	20–190	$+ 3 d B / o c t a v e$
	190–750	$0.00409216 g^{2} / H z$
	750–2000	$- 9 d B / o c t a v e$
Total rms acceleration ( $g_{r m r m s}$ )	—	2 g
Test time (min)	—	1
Direction	—	$X$ , $Y$ , $Z$

			Surface
			Shape Error	Maximum
			after	Amplification
			Mechanical	of
Name	Size (mm)	Material	Test	Acceleration
Curved	$216 \times 156 \times 42$	JGS1	$0.023 λ$	5.15
prism
Plane	$150 \times 83 \times 20$	JGS2	$0.021 λ$	4.3
reflector
Curved	$236 \times 144 \times 21$	ZF7LHT	$0.029 λ$	5.64
prism
reflector

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Tables (6)

Equations (4)

Applied Optics