CN1211599C - Interactive constant force dish spring support hanger frame - Google Patents

Abstract

The present invention relates to a constant-force disk spring support hanger which is composed of a fixed frame, a swing frame, a main shaft, a load shaft, a pull rod shaft, a disk spring assembly, etc. The constant-force disk spring support hanger is characterized in that a pull rod is arranged between the pull rod shaft and the disk spring assembly, and a rolling front pressing plate is arranged on the pull rod; two circular arc grooves are arranged on the rolling front pressing plate, and a roller ball is arranged in the rolling front pressing plate which corresponds to a circular arc convex surface arranged on the side surface of the fixed frame to form an inner supporting surface of the roller ball. The present invention has the advantages that the constant-force disk spring support hanger can efficiently eliminate the shearing force deformation of the pull rod and efficiently reduce the influence of friction force on constant degree, and the constant degree is high. Moreover, the constant-force disk spring support hanger can be widely used for occasions, such as boilers, power stations, petrifaction, metallurgy, etc., which have thermal drift and need to eliminate the influence of displacement.

Description

Interactive constant force dish spring support hanger frame

Technical field:

The present invention relates to a kind of suspension and support, especially a kind of constant force disc shape spring support hanger frame.

Background technique:

Suspension and support is mainly used in cogeneration power plant boiler, petrochemical industry, metallurgical equipment, suspention and the support and other of pipeline need be eliminated the place that produces thermal stress and reduce to vibrate because of hot.

At present, various suspension and supports can be divided into following two big classes by its used elastic element:

One. cylindrical spring suspension and support: as (as Fig. 1) such as JB2654, GB10181, ITT.Generally have load arm in horizontal line upper and lower revolution, Horizontal displacement is little, invariance degree height, but have volume big, Heavy Weight, shortcoming such as load is little.

Two. disc shape spring support hanger frame: as the patented technology (as Fig. 2) of " drawplate type constant-force disk spring support hanger ".General load arm is turned round above horizontal line, has volume little, and in light weight, load is big, but has Horizontal displacement big, shortcomings such as invariance degree difference.

By Fig. 1, Fig. 2 is the suspension and support of the different elastic elements of two classes as can be known, its basic structure is identical, the cylinder spring bearing hanger gos deep into spring inner because of arm-tie, so arm-tie is long, and disc spring bearing hanger, because of reasons in structure, pull bar can only be placed in the fixed frame, and the positioning action that front pressuring plate rises makes the gap quite little (about as seen the dish spring uses data, in June, 1997, ISBNT-111-05555-1 China Machine Press was 350 pages) in order to reduce the fixed frame size, shorten arm-tie length, adopt in the design of former disc shape spring support hanger frame:

1. load arm displacement above horizontal line.

2. the arm-tie axle moves near the main shaft vertical line.

3. select the big dish spring of energy storage for use, the distance of dwindling arm-tie axle and main shaft.

4. pass lubriation material on the part lining at front pressuring plate and pull bar.

5. the F to producing ₂Power is carried out pretreatment when design.

Though mode is a lot, fixed frame is still much larger than the cylinder spring bearing hanger, and the raising of invariance degree index is very difficult, gets rid of all factors, and principal element is F ₂Stochastic variable is big, can't accurately hold.

Another point is exactly that load is regulated, and in the cylinder spring bearing hanger, is furnished with the mechanism that band load is regulated, principle such as Fig. 3, regulative mode changes BD (main shaft and arm-tie axle) distance exactly, achieves the goal by the angle that changes ∠ ABD, and not only mechanism is not only complicated, Heavy Weight, and after regulating invariance degree being had certain influence, disc spring bearing hanger is because of very sensitive to ∠ ABD, after the adjusting, very big to the invariance degree influence, so up to the present there is not adjustable formal product to occur as yet.And a large amount of site operations show, the scene that is adjusted in of load is not (design is little with actual error) that all can use, and indivedual also existence are effective after regulating not yet.Only use when mounted or obsolete at all load adjustment device, do not adorn not all rightly, adorned and be a kind of waste.

Summary of the invention:

The objective of the invention is to: the problem at present all types of suspension and supports exist provides a kind of new interactive constant force dish spring support hanger frame.

The object of the present invention is achieved like this: with the three design method cancellation arm-ties that connect mechanism, substitute rigid friction with the mode of the rotation of rolling, change load value with the mode of change displacement amount.

The invention has the advantages that: the cancellation arm-tie, compact structure, the reliability height, the invariance degree index is good, and adjusting load is easy.

Description of drawings:

Fig. 1 is a constant force cylindrical spring support hanger structure schematic representation;

Fig. 2 is the constant force disc shape spring support hanger frame structural representation;

Fig. 3 is the design principle figure of pulling plate structure;

Fig. 4 is the trace frictional force analysis principle figure of pulling plate structure;

Fig. 5 is the backhaul frictional force analysis principle figure of pulling plate structure;

Fig. 6 is the design method schematic diagram of three mechanisms of company;

Fig. 7 is the working principle schematic representation of three mechanisms of company;

Fig. 8 is the interactive constant force dish spring support hanger frame structural representation;

Fig. 9 is the load regulation structure schematic representation of interactive constant force dish spring support hanger frame off-centre;

Among Fig. 1,2: fixed frame (1), slewing frame (2), arm-tie axle (3), arm-tie (4), front pressuring plate (5), pull rod shaft (6), pull bar (7), main shaft (8), load axle (9).

Among Fig. 3: A ₁The pull bar (7) of disc spring bearing hanger passes the position of front pressuring plate in the some representative graph 2, and the A point is pull rod shaft (6), and the B point is arm-tie axle (3), and the C point is load axle (9), and the D point is main shaft (8), and the E point is C vertical line and the horizontal intersection point of D, and F is the power of elastic element, F ₁Be the power of transmitting.

Among Fig. 4, Fig. 5: be the analysis of disc spring bearing hanger positive return frictional force, AO is the distance that produces moment of components point, F ₂' represent trace frictional force, F ₂" represent backhaul frictional force.According to the equalising torque formula be:

W× ED＝∠ABD× BD×F±∠ABO× AO×F ₂

Initial state F ₁=F ± O=F

Trace state F ₁'=F+F ₂' ≠ F

Backhaul state F ₁"=F-F ₂" ≠ F

In initial state, because of AO is zero, so balance.

At the trace state, though F is arranged ₂' increase, but F is also in variation, so can balance.

At the backhaul state, be balance as trace, its Angular Dimension is all the same, but because of the change of frictional force direction, F ₂' by just becoming negative F ₂", the real balance destroyed is compared with trace, just in time differs 2F ₂Value, on the contrary with the backhaul calculated equilibrium, trace also differs 2F by contrast ₂Value, this just product when actual detected in the moment of positive backhaul, produce the main cause of maximum value and minimum value.

So under the condition of same vertical displacement AO, arm-tie is long more, ∠ ABO is more little, F ₂Just little, the max min difference is just little, and invariance degree is just high.

Among Fig. 6: Z is the double row bearing center, all the other same Fig. 3.

Among Fig. 7: during the slewing frame revolution, pull bar turns round the schematic representation of certain angle synchronously.

Among Fig. 8: fixed frame (1), slewing frame (2), pull bar (5), pull rod shaft (7), main shaft (8), load axle (9), arc structure (10), arc groove (11) roller (12), dished spring assembly (13), pressing plate (14), pull bar cap (15) rolling front pressuring plate (16).

Below in conjunction with accompanying drawing the embodiment of the invention is further described:

As seen from Figure 8, fixed frame links to each other with slewing frame by main shaft, there is arc structure the fixed frame side, slewing frame can be around main shaft gyration, pull rod shaft and load axle are housed on the slewing frame, be equipped with the fixed frame side can be by the rolling front pressuring plate of circular movement, one end of rolling front pressuring plate and dished spring assembly fixes, the other end of dished spring assembly has pressing plate, one end of pull bar passes the rolling front pressuring plate and dished spring assembly, pressing plate and pull bar cap are fixed, and the pull bar the other end links to each other with slewing frame by pull rod shaft.

When slewing frame during around main shaft gyration, drive pull bar, interlock rolling front pressuring plate and dished spring assembly are made circular movement along the arc structure of fixed frame side.In slewing frame when revolution,, the axial connecting line of its load axle and main shaft can be done asymmetric or symmetrical revolution above or below horizontal at spindle axis.

What rotate in the drawings is the rolling front pressuring plate, and pull bar passes the rolling front pressuring plate and links to each other with slewing frame by pull rod shaft, revolution in the time of rolling front pressuring plate and dished spring assembly and slewing frame, but angle difference.

On structural design, fixed frame and movable front pressuring plate are deformed into large-scale double row bearing, the biside plate of fixed frame (1) is exactly the inner ring of double row bearing, and the rolling front pressuring plate is exactly the cylindrical of double row bearing, centre can pack into respectively as required ball, roller or needle roller, and in all contact frictions, the friction factor minimum of roller, and under different pressure, its Young's modulus is constant substantially, the F of stochastic variable maximum ₂, be simplified to fixing amount.

Load is regulated and is seen Fig. 9, and eccentric bearing block respectively is housed on the biside plate of slewing frame, and the load axle is through on the eccentric bearing block, according to principle of moment balance, by changing the distance between the CD, just changes load by changing displacement amount.

Giving an actual example below illustrates that load is 23748N, displacement 303.78mm

Example 1, example 2 are selected Φ 160A type dish spring for use, and dish spring compression 0.25,0.50,0.75 o'clock, its dish spring coefficient was 0.28,0.53,0.77, is the slope of cumulative type, and approximate straight line is similar to the cylinder spring.

Example 3 is selected Φ 160C series dish spring for use, and dish spring compression 0.25,0.50,0.75 o'clock, its dish spring coefficient was 0.53,0.82,0.95, be typical dish spring curve, but initial force is similar to the cylinder spring with termination power.

The suspension and support design of example 1 horizontal line top offset, calculated data see Table 1.

Initial state 100mm * sin70 ° * 5054N=200mm * W

W＝23748N

Intermediateness 100mm * sin55.25 ° * 95675N=328.32mm * W '

W′＝23943N

Final state 100mm * sin38.43 ° * 139000N=363.80mm * W "

W″＝23774N

The invariance degree formula:

Δ=[(maximum value-minimum value)/(maximum value+minimum value)] * 100%=0.4%

The design invariance degree is 0.4%, and the actual measurement product is much better than 6% criterion of acceptability in 1.5%.

Example 2 horizontal lines are the suspension and support of symmetrical displacement up and down, and design, calculated data see Table 2.

Initial state 51.61mm * sin100 ° * 50545N=108.18mm * W

W＝23747N

Intermediateness 51.61mm * sin62.1 ° * 95675N=183.12mm * W '

W′＝23831N

Final state 51.61mm * sin21 ° * 139000N=108.12mm * W "

W″＝23765N

The invariance degree formula:

Δ=[(maximum value-minimum value)/(maximum value+minimum value)] * 100%=0.18%

Design 0.18%, the actual measurement product is much better than 6% criterion of acceptability in 1%.

Example 3 horizontal lines are the suspension and support of symmetrical displacement up and down, and design, calculated data see Table 3.

Initial state 251.68mm * sin120 ° * 12162N=111.62mm * W

W＝23749N

Intermediateness 251.68mm * sin670 ° * 18817N=186.97mm * W '

W′＝23802N

Final state 251.68mm * sin28.9 ° * 21800N=111.62mm * W "

W″＝23755N

The invariance degree formula:

Δ=[(maximum value-minimum value)/(maximum value+minimum value)] * 100%=0.11%

Design 0.11%, the actual measurement product is much better than 6% criterion of acceptability in 1%.

Example 4 load are regulated, CD=186.52mm as shown in Table 2, and W=23747N,

ED＝108.18mm

Make CD '=200mm, ED '=116.00mm

According to principle of moment balance

W′×116.00mm＝23747 N×108.18mm

W′＝22146N

Adjusting ratio=[(23747-22146)/23747] * 100%=6.7%

Under the prerequisite that does not change invariance degree, load is regulated 1600N, reaches 22146N, adjusting ratio 6.7%.

Can show the cancellation arm-tie by above example, simplified design transfers the variable of largest random quantitatively to, can utilize different elastic elements, designs the various constant force disc shape spring support hanger frame of varying level displacement, different angles of revolution

Table 1

The displacement of dish spring	Initial	Middle	Stop
				50545	95675	139000
	BD	100	100				100
AD				108.51	108.51	108.51
	AB	88.46	127.85				167.28
CD				363.80	363.80	363.80
	ED	200	328.32				363.80
∠ABD				70	55.25	38.34
	∠BDA	50	75.51				106.62
∠DAB				60	49.23	34.95
	∠α	56.62	25.51				0

Table 2

The displacement of dish spring	Initial	Middle	Stop
				50545	95675	139000
	BD	51.61	51.61				51.61
AD				71.89	71.89	71.89
	AB	41.86	79.74				117.62
CD				186.52	186.52	186.52
	ED	108.18	183.12				108.18
∠ABD				100	62.1	21
	∠BDA	35.00	78.6				144.1
∠DAB				45	39.3	14.9
	∠α	54.55	10.95				-54.55

Table 3

The displacement of dish spring	Initial	Middle	Stop
				12162	18817	21800
	BD	251.68	251.68				251.68
AD				380.03	380.03	380.03
	AB	188.48	383.49				580.36
CD				188.54	188.54	188.54
	ED	111.62	186.97				111.62
∠ABD				120	70	28.9
	∠BDA	25	71.3				132.4
∠DAB				35	38.7	18.7
	∠α	53.7	0				-53.7

Claims (4)

1. interactive constant force dish spring support hanger frame comprises: fixed frame, slewing frame, dished spring assembly, rolling front pressuring plate, main shaft, pull bar, pull rod shaft, pressing plate, pull bar cap, load axle, load adjustment device, it is characterized in that: fixed frame links to each other with slewing frame by main shaft, slewing frame is linked to be interactive integral body by pull rod shaft and pull bar, rolling front pressuring plate and dished spring assembly, when slewing frame carries along main shaft gyration because of the load bearing, drive pull rod shaft and pull bar simultaneously, pull bar drives the rolling front pressuring plate again and the belleville spring assembly turns round simultaneously.

2. suspension and support according to claim 1 is characterized in that: there is the structure of circular arc the side of fixed frame.

3. according to claim 1,2 described suspension and supports, it is characterized in that: have the circular arc with the fixed frame side that corresponding arc groove is arranged on the rolling front pressuring plate, ball, the roller that can roll are housed.

4. suspension and support according to claim 1 is characterized in that: load adjustment device is contained in respectively on the biside plate of slewing frame.

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