CN2550541Y - Non-interruption hydraulic source of deep sea hydraulic system composed of corrugated pipe and external placer spring - Google Patents

Abstract

The utility model discloses a ceaseless hydraulic pressure source for deep sea hydraulic system, which comprises a bellows and an external spring; wherein, the bellows is arranged inside a housing, a end of the bellows is seal-jointed with a fixed plate, the other end of the bellows is seal-jointed with the other fixed plate which has an opening; a compression spring is arranged between a fixed plate and the internal end face of the housing; the hole on the other fixed plate is communicated with the hydraulic pressure source by the pipeline. The utility model is characterized in that firstly, the deformation can be generated to change the interior volume with the variation of the differential pressure between interior and exterior; secondly, the requirement of the differential pressure between interior and exterior can be satisfied by the resilience generated by the deformation of the bellows; thirdly, according to different depth underwater operation, the same quantity of deformation of the bellows can be generated to balance the working differential pressure of the hydraulic system in disregard of different depth of water.

Description

The uninterrupted hydraulic power of forming by bellows and external spring of deep-sea hydraulic system

Technical field

The utility model relates to pressurized machine or fluid pressure transducer, is the uninterrupted hydraulic power of a kind of deep-sea underwater hydraulic system.

Background technique

The deep-sea underwater hydraulic system generally adopts return pressure and the self balancing self adaption fuel tank of extraneous hydraulic pressure, the output pressure reduction that the absolute value of its delivery pressure equals hydraulic power add extraneous hydraulic pressure and.Therefore, conventional hydraulic is by single accumulator stored energy, provide the method for using under the emergency condition be subjected to the hydraulic power depth of water of living in probabilistic influence serious, almost can't proper functioning.

For example: for an output pressure reduction is the hydraulic system of 10MPa, and having selected a volume for use is 10 liters accumulator.If on the ground, but the pressure of preliminary filling 5Mpa when the hydraulic system rapid decompression, can discharge 3.9 liters hydraulic oil at most.And this accumulator is used for the deep-sea underwater hydraulic system, at least the pressure that needs preliminary filling 20Mpa, it not only under water 1000 meters can't work with interior, releasable flow also becomes very little, (depth of water unit is that rice, flux unit are for rising) as shown in the table more than 1000 meters the time:

The depth of water of living in	1500	2000	2500	3000	3500	4000	4500	5000	5500	6000	6500	7000
													Can discharge flow	1.5	1	0.8	0.6	0.5	0.4	0.35	0.3	0.25	0.2	0.2	0.2

Therefore, at present the deep-sea underwater hydraulic system all be badly in need of the higher uninterrupted hydraulic pressure of a kind of energy storage efficiency can supplier so that in its source that runs out of steam, lose under the situation of whole power supplies and still can finish all essential hydraulic emergencies actions even.

Summary of the invention

The purpose of this utility model is the uninterrupted hydraulic power of a kind of bellows of design deep-sea underwater hydraulic system.This hydraulic power can the deep-sea underwater hydraulic system run out of steam the source, lose under the situation of whole power supplies for it provides emergent hydraulic pressure energy, so that hydraulic system is finished all essential hydraulic emergencies actions even.

The uninterrupted hydraulic power of being made up of bellows and external spring of deep-sea hydraulic system comprises casing, pressure spring, two fixed plates, bellows, bellows one end that is contained in the casing is tightly connected with a fixed plate, and the bellows the other end is tightly connected with the fixed plate of another piece perforate, and pressure spring is contained between a fixed plate and casing interior edge face, aperture pipeline on another piece fixed plate and hydraulic power are communicated with, and have the hole that is communicated with seawater on the casing.

The design of said bellows and pressure spring should be satisfied following criterion with selecting for use:

Bellows maximum displacement W and useful area F _e:

F _e·W＝Q $W=2\mathrm{nw}=\frac{n{(D_H-D_B)}^4}{2^4\·E{h_0}^3}(p+\frac{2P_n}{\mathrm{\π}\·D_B}+\frac{2p{D}_B}{4})$

In the formula: n---the bellows wave number

The maximum displacement (mm) that w---bellows half-wave allows

D _B---inside diameter of bel (mm)

D _H---outside diameter of bel (mm)

The inside and outside differential pressure that p---bellows bears (MPa)

h ₀---bellows thickness (mm)

P _n---pressure spring maximum load (N)

Bellows maximum displacement W is the working stroke of pressure spring 3, the rigidity p ' that maximum working load of being determined by following formula and working stroke are just decided spring (N/mm): $p^{\′}=\frac{P_n}{W}$

The limit load P of spring _lFor:

P _l＝1.25×P _n

Spring inside diameter D is pre-determined by structural requirement, by P _lLook into D and to get the standard spring

The active spring coils number $m=\frac{{P_d}^{\′}}{P^{\′}}$ And get reference value

Number of total coils m '=m+2 bellows allows displacement to table look-up by useful area with maximum.Material can be selected the anticorrosion stainless steels of high strength such as 1Cr17Ni2 for use.

The utlity model has following characteristics:

1) can produce deformation with the variation of inside and outside differential pressure and change its internal capacity;

2) spring-back force that relies on the bellows distortion to produce can satisfy the requirement of inside and outside differential pressure;

3) for the underwater operation of different depth, bellows all can produce the operating pressure differential of identical deformation quantity with the balanced hydraulic system, is not subjected to the influence of the depth of water.

Description of drawings

Fig. 1 is a structural representation of the present utility model;

Fig. 2 is the dangerous spot schematic representation of bellows.

Embodiment

As shown in Figure 1, the uninterrupted hydraulic power of being made up of bellows and external spring of deep-sea hydraulic system comprises casing 1, pressure spring 3, two fixed plates 4,6, bellows 5, bellows 5 one ends that are contained in the casing 1 are tightly connected with a fixed plate 4, bellows 5 the other ends are tightly connected with the fixed plate 6 of another piece perforate, pressure spring 3 is contained between a fixed plate 4 and casing interior edge face, and aperture pipeline on another piece fixed plate 6 and hydraulic power A are communicated with, and have the hole 2 that is communicated with seawater on the casing 1.

The design of bellows and external pressure spring should be satisfied following criterion with selecting for use:

Bellows maximum displacement W and useful area F _e:

F _e·W＝Q $W=2\mathrm{nw}=\frac{n{(D_H-D_B)}^4}{2^4\·E{h_0}^3}(p+\frac{2P_n}{\mathrm{\π}\·D_B}+\frac{2p{D}_B}{4})$

In the formula: n---the bellows wave number

The maximum displacement (mm) that w---bellows half-wave allows

D _B---inside diameter of bel (mm)

D _H---outside diameter of bel (mm)

The inside and outside differential pressure that p---bellows bears (MPa)

h ₀---bellows thickness (mm)

P _n---pressure spring maximum load (N)

Bellows maximum displacement W is the working stroke of pressure spring 3, the rigidity p ' that maximum working load of being determined by following formula and working stroke are just decided spring (N/mm): $p^{\′}=\frac{P_n}{W}$

The limit load P of spring _jFor:

P _j＝1.25×P _n

Spring inside diameter D is pre-determined by structural requirement, by P _jLook into and get the standard spring with the 4th edition the 3rd of the proportionately big chief editor's " mechanical design handbook " earlier of D (back abbreviation " machine " 4-3) table 11-2-19.

The active spring coils number $m=\frac{{P_d}^{\′}}{P^{\′}}$ And show 11-2-10 by " machine " 4-3 and get reference value

Number of total coils m '=m+2

Bellows is looked into " machine " 4-3 table 11-21-4 by useful area and maximum permission displacement and is selected for use with " machine " 4-3 table 11-21-5.Material selection 1Cr17Ni2.

The bellows dangerouse cross-section need carry out Stress Check:

As shown in Figure 2, the dangerous spot of bellows is at Gu Buchu A, B and the C of Gu Feng place, D

At first determine nondimensional parameter k, δ, m during check: $k=\frac{R_H}{R_B},\mathrm{\δ}=\frac{h_0}{R_B},m=\frac{r_B}{R_B}$

In the formula: R _H---bellows outer radius (mm)

R _B---bellows inside radius (mm)

r _B---bellows ripple internal diameter (mm)

Look among " machine " 4-3 Figure 11-21-3 according to k, δ, m and to find Gu Buchu (r=R _B) (σ _1w) _w(σ ₂₀) _w, find out (the r=R of Gu Feng place by Figure 11-21-4 simultaneously _H) (σ _1w) _w(σ ₂₀) _w, according to formula ${\stackrel{\‾}{\mathrm{\σ}}}_w=\frac{{\mathrm{\σ}}_w{R_H}^{2}n}{E{h}_{0}W}$ Calculate radial stress σ _1wAnd σ ₂₀, in the stress sign of paddy portion's point A and some B, when W＞0,11-21-3 determines by " machine " 4-3 table.

Principal stress is by formula: σ _i ^B/H=σ _I0± σ _IwCalculate (i=1,2).

For the A point:

σ ₁≈σ _1w

σ ₂＝σ ₂₀+σ _2w

For the B point:

σ ₁≈-σ _1w

σ ₂＝σ ₂₀-σ _2w

Ask equivalent stress according to formula ${{\mathrm{\σ}}^A}_d=\sqrt{{{\mathrm{\σ}}_1}^2+{{\mathrm{\σ}}_2}^2-{\mathrm{\σ}}_1{\mathrm{\σ}}_2}$

Equivalent stress should be less than the σ of bellows material after multiply by safety coefficient _0.2

Therefore, as long as select appropriate bellows pattern and material can make bellows all can reach optimum Working in the seabed of any degree of depth.The stationarity of charge oil pressure and the continuity of flow when bellows can guarantee the hydraulic system proper functioning as elastic element simultaneously.

Because standard bellows withstand voltage properties does not reach deep-sea underwater hydraulic system working pressure requirement, can obtain the rigidity that meets the demands for guaranteeing bellows, must on existing standard bellows basis, be retrofited.Need increase the external pressure spring above bellows, spring and bellows are fixed in the casing for this reason.Guarantee that bellows is bearing under the operating pressure differential, its displacement is in allowed band.Bellows accumulator behind the remodeling should be able to bear the operating pressure differential of hydraulic system, has bigger draining flow simultaneously.

Specific embodiment:

For uninterrupted hydraulic power shown in Figure 1, adopt the novel high pressure-resistant bellows after retrofiting, adopt the structure of U type bellows, its volume is 10 liters.Each several part size such as following table:

Bellows	Inside diameter D B(mm)	Outer diameter D H(mm)	Pitch of waves t (mm)	Thickness of convolution a (mm)	Wave number n	Wall thickness h 0(mm)	Height overall H (mm)
								150	200	12.0	7.00	35	0.60	436
	Spring	Material diameter d (mm)	Mean diameter of coil D (mm)	Number of active coils m	Pitch t1 (mm)	Former long H0 (mm)
30								160	10.5	50.0	568

The bellows material is selected 1Cr17Ni2 for use, σ _0.2=635MPa, spring select Stainless Steel Wire 1Cr18Ni9 for use.

This bellows releasable flow under any depth of water all equates.Calculating shows that this bellows all can discharge about 3.78 liters fluid flow under any depth of water.

Claims (2)

1. the uninterrupted hydraulic power of forming by bellows and external spring of deep-sea hydraulic system, it is characterized in that: it comprises casing (1), pressure spring (3), two fixed plates (4), (6), bellows (5), bellows (5) one ends that are contained in the casing (1) are tightly connected with a fixed plate (4), bellows (5) the other end is tightly connected with the fixed plate (6) of another piece perforate, pressure spring (3) is contained between a fixed plate (4) and casing interior edge face, aperture pipeline on another piece fixed plate (6) and hydraulic power (E) are communicated with, and have the hole (2) that is communicated with seawater on the casing (1).

2. the uninterrupted hydraulic power of being made up of bellows and external spring of deep-sea hydraulic system according to claim 1, the design that it is characterized in that said bellows (5) and pressure spring (3) should satisfy following criterion with selecting for use:

Bellows maximum displacement W and useful area F _e:

F _e·W＝Q $W=2\mathrm{nw}=\frac{n{(D_H-D_B)}^4}{2^4\·E{h_0}^3}(p+\frac{2P_n}{\mathrm{\π}\·D_B}+\frac{2p{D}_B}{4})$

In the formula: n---the bellows wave number

The maximum displacement (mm) that w---bellows half-wave allows

D _B---inside diameter of bel (mm)

D _H---outside diameter of bel (mm)

The inside and outside differential pressure that p---bellows bears (MPa)

h ₀---bellows thickness (mm)

P _n---pressure spring maximum load (N)

Bellows maximum displacement W is the working stroke of pressure spring 3, the rigidity p ' that maximum working load of being determined by following formula and working stroke are just decided spring (N/mm): $p^{\′}=\frac{P_n}{W}$

The limit load P of spring _jFor:

P _j=1.25 * P _nSpring inside diameter D is pre-determined by structural requirement, by P _jLook into D and to get standard spring active spring coils number $m=\frac{{P_d}^{\′}}{P^{\′}}$ And get reference value number of total coils m '=m+2 bellows and table look-up by useful area and maximum permission displacement.

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