CN86100396B - Speed regulation clutch with omega valve and compound spring - Google Patents

Speed regulation clutch with omega valve and compound spring Download PDF

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Publication number
CN86100396B
CN86100396B CN86100396A CN86100396A CN86100396B CN 86100396 B CN86100396 B CN 86100396B CN 86100396 A CN86100396 A CN 86100396A CN 86100396 A CN86100396 A CN 86100396A CN 86100396 B CN86100396 B CN 86100396B
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China
Prior art keywords
valve
speed
spring
diameter
oil
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Expired
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CN86100396A
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Chinese (zh)
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CN86100396A (en
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董勋
黄文伟
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Shanghai Jiaotong University
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Shanghai Jiaotong University
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Priority to CN86100396A priority Critical patent/CN86100396B/en
Publication of CN86100396A publication Critical patent/CN86100396A/en
Publication of CN86100396B publication Critical patent/CN86100396B/en
Expired legal-status Critical Current

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  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

The present invention relates to an oil film speed regulating clutch with an omega valve and a combined spring, which belongs to the technical field of speed regulating clutches. The omega valve which is arranged on a driven shaft and rotates together with the driven shaft is used as an information feedback device for speed regulation, and the combined spring formed from ordinary linear springs through connection in series or connection in parallel is used for controlling a piston to move to a stated position so as to obtain the required corresponding combined degree between friction plates of the oil film speed regulating clutch so that the purposes of speed regulation and stable operation can be obtained. The present invention can be used as a transmission device and a speed regulating device for various types of machinery so as to realize the purposes of reduced energy consumption, prolonged service life, improved productivity and reduced cost.

Description

Variable-speed clutch with Ω valve and cluster spring
The invention belongs to variable-speed clutch.
Variable-speed clutch claims oil film speed-regulating clutch, slip lid clutch, Ω clutch or speed governing friction clutch again.It is a kind of novel clutch that utilizes the fluid viscosity transferring power and carry out speed governing.It can realize stepless speed regulation by the combination degree of the friction plate between control driving shaft and the driven shaft on a large scale.All need the machine of varying duty running, and all available variable-speed clutch reaches changed speed operation and realizes purpose of energy saving.Water pump that drive motor power is 25KW for example, adopt the variable-speed clutch speed governing after, and adopt valve regulated to compare can to save electric energy 12% to 45%, its utilization can also prolong service life of a machine, improves throughput, has very big economic benefit.
Realize speed governing as how concrete technological scheme? how to make the stabilization of speed of output shaft? this is the key problem in technology of variable-speed clutch.U.S. Pat-3913715 disclosed a kind of speed governing friction clutch that utilizes centrifugal force and rotating angular acceleration sensitive valve to control in 1975.The special public clear 53-9952 of Japanese JP-disclosed a kind of overload buffer device in 1978, and this device also is a kind of variable-speed clutch in fact.A Ω valve is housed on the driven shaft of this overload buffer device, because the Ω valve rotates with driven shaft, can realizes the purpose of oil pressure control, and concrete Ω valve is listed three kinds of different structure diagrams.Above-mentioned two kinds of patents, the latter is development and the improvement on the former principle basis, can both realize that speed governing makes stabilization of speed.But latter's performance may be excellent than the former, provides the driving shaft maximum speed and be the speed adjusting performance below 1500 rev/mins.
Purpose of the present invention is from the angle of theoretical and engineering practice, proposes a kind of variable-speed clutch with the concrete Ω valve arrangement of cluster spring and another kind, and provides simple design method.
Compare with the special public clear 53-9952 of JP-, the present invention has a kind of novel cluster spring and another kind of concrete Ω valve arrangement.Three kinds of concrete Ω valve arrangements of the special public clear 53-9952 of the structure of this Ω valve and JP-are all different.Cluster spring is installed in the right side of control piston, can improve the high speed performance and the speed adjustable range of variable-speed clutch, also can improve the transmitted power of speed governing.Adopt variable-speed clutch of the present invention, still can realize normal and good speed governing when the driving shaft rotating speed is 3000 rev/mins.The driving shaft rotating speed suitably improves still effective again.
Fig. 1 is the structure diagram of variable-speed clutch of the present invention;
Fig. 2 is the structure diagram of Ω valve of the present invention;
Fig. 3 is a kind of remodeling of spool;
Fig. 4 is the another kind remodeling of spool;
Fig. 5 is the schematic representation of Ω valve performance line chart.
As shown in Figure 1, variable-speed clutch of the present invention has driving shaft 1, driven shaft 6, friction plate group 2, control piston 4, bearing 7 and is contained in Ω valve 3 on the driven shaft 6.Lubricant oil is full of friction plate group 2, by the liquid viscous friction between the friction plate, makes driving shaft drive the driven shaft revolution.The size of frictional force depends on the combination degree between control piston 4 and friction plate.P LRepresent the pressure of lubricating oil path, P cRepresent the pressure of control oil channel.
Technical characteristics of the present invention is that this variable-speed clutch has Ω (omega) valve 3 of cluster spring 5 and particular configuration.This is two critical components realizing variable-speed clutch stepless speed regulation and stabilized (steady-state) speed.
As shown in Figure 2, Ω of the present invention (omega) valve is made up of valve body 11, spool 12, valve gap 13 and standard link, and it is contained on the driven shaft and rotation therewith.Spool 12 is radially arranged and can radially be moved back and forth, when output speed surpasses required value, spool outwards moves under action of centrifugal force, thereby connect draining hole 14, the oil pressure of control piston reduces, and causes reducing of control piston end thrust, and piston moves right, combination degree between friction plate reduces, and driven shaft slows down; Thereby can make driven shaft remain on steady running on the rotating speed of requirement.
The spool 12 of Ω valve is that a diameter is d 1Cylindrical body, it is d that there is a diameter its lower end 5Short cylinder 15.It is d that a diameter is arranged in the end of short cylinder 15 2Oil pocket 16.The height l of short cylinder 1, can be taken as the diameter d that approximates draining hole 14 5Be provided with annular oil cavity 17 on valve gap 13, oil pocket 17 is P by oil circuit 19 with pressure cControl oil channel connect.Oil pocket 16 is connected by the oil circuit 18 and the hyperbaric chamber of control piston 4.Each physical dimension of Ω valve can design according to fluid continuous-flow condition and the proper principle of ratio collocation.The pass of advising each size is: spool height l=(1～3) d 1, d 2=(0.5～0.6) d 1, d 3=(0.2～0.4) d 1, l 1=d 5; Shift motion S≤the d of spool in valve body 3 2/ (4 * d 2); d 3≤ &lt;math>&lt;msqrt><msup><mi>d</mi><msub><mi>2</mi></msup><mi>1</mi></msub><msup><mi>-d</mi><msub><mi>2</mi></msup><mi>3</mi></msub></msqrt></math> 。
The d of valve core diameter 1(mm) and the turning radius R(mm of spool barycenter G) product value, can be according to the principle that guarantees that Ω valve and variable-speed clutch load speed are complementary, according to nominal operation rotation speed n (r.p.m) with control oil pressure P c(kgf/cm 2), try to achieve or utilize to look into by calculating and get by strict theory analysis and the Ω valve performance line chart that calculates.
Fig. 5 is used for trying to achieve d 1The schematic representation of the Ω valve performance line chart of * R value.D has been arranged 1* R value can be determined the position of Ω valve that is definite R value according to the general structure of variable-speed clutch; Thereby also just determined d 1Value.Also can determine d earlier 1Value is again by d 1And d 1* R value is tried to achieve the R value.d 1After value is determined,, can try to achieve each structural parameter according to the dimension scale relation of advising above.
The structure of spool also can adopt other slightly different forms.Shown in Figure 3 is hollow spool, has an axial hole 21 in spool central authorities, the last lower oil cavitie of Ω valve is linked up, thereby oil circuit 19 can save.Spool shown in Figure 4 except that be hollow, its axial hole 21 tops also are provided with a throttle orifice 31, utilize the throttling action of throttle orifice, can make moving of spool more steady.Certainly other structural forms can also be arranged, but essential structure all is the same with basic design method, does not give unnecessary details one by one.
Another critical component of the present invention is a cluster spring 5, and it is the actuator of control piston motion.It all is non-linear requiring the piston motion rule coordinated mutually with the Ω valve and the variation of respective carrier ability.And the power of general spring and distortion are linear, the two inharmonious speed adjusting performance and bearing capacity of just influencing.And to make nonlinear spring, and be subjected to the restriction of technology and material, be difficult to again realize.The present invention adopts two Hookean springs to make up dexterously, makes it and can carry out speed governing in company with the Ω valve, can improve bearing capacity and expanding governing by designing requirement again, gives full play to the function of variable-speed clutch.
Cluster spring is by two stiffness coefficient differences, and the cylindrically coiled spring parallel connection or the tandem compound that are uneven in length form.A variable-speed clutch can be provided with one or more (for example 3～16), and this cluster spring is contained in the rear side of control piston equably.Determining of the stiffness coefficient of cluster spring and structural parameter is complementary with the load and the change in rotational speed rule of variable-speed clutch.
Tandem compound and two kinds of forms of parallel connection combination are compared, and combination in parallel can obtain more reasonable and compact structure, thereby the preferential employing combining form in parallel of recommending.The calculating principle and the computational methods of tandem compound spring are similar with cluster spring in parallel.So following the design to cluster spring in parallel is illustrated.
Cluster spring in parallel can be formed by two different cylindrically coiled spring suits of diameter.The little person's length of stiffness coefficient is big, is sleeved on the outside.Its stiffness coefficient and structural parameter can calculate by the following method.
If: the friction plate number is m,
The cluster spring number is j,
The stiffness coefficient of flexible (stiffness coefficient is little) spring is K 1, its length is L 1,
The stiffness coefficient of rigidity (stiffness coefficient is big) spring is K 2, its length is L 2,
The control oil pressure that is complementary with Ω valve and load speed is P c,
The control piston bearing area is A,
It is F that oil film between friction plate produces axial force,
Ω valve speed adjustable range is i=i 1To i=i 2; And i 1＜1, i 1＞i 2, i 2＞0,
With speed ratio i 1The oil slick thickness that adapts is h 1, h 1Value determine according to manufacture level and quality of processing.
One, load is permanent moment of torsion
Make L 2=L 02+ Δ L 2
In the formula: Δ L 2The decrement of stiffness spring under the load of-maximum functional,
L 02-amount of spring compression is Δ L 2The time spring length.
Δ L then 2=(m-1) 1-i 2/ 1-i 1h 1
Make L 1=L 01+ Δ L 1
In the formula: Δ L 1The decrement of flexure spring under the load of-maximum functional, its value is definite according to assembly condition,
L 01-decrement is Δ L 1The time spring length.
The stiffness coefficient K of flexure spring 1
K 1＝Pc(i=i2)A-F(i-i2)/j(ΔL1-ΔL2)
In the formula: P c(i=i 2)-expression speed ratio i=i 2The time the control oil pressure,
F(i=i 2)-expression speed ratio i=i 2The time the oil film axial force.
The stiffness coefficient K of stiffness spring 2
K 2 = P c (i=i 1 )A-F(i=i 1 )-jK 1 ［ΔL 1 -(m-1)h 1 ］ j(m-1)h 1 ( i 1 -i 2 1-i 1 )
Two, load is applicable to centrifugal working machine for becoming moment of torsion
L 1＝L 01+ΔL 1
L 2＝L 02+ΔL 2
Its definition is same as described above, just is divided into two zones by cluster spring length, and its speed adjustable range is respectively i=i 1～i 2And i=i 2～i 3, and i 1＜1, i 1＞i 2, i 2＞i 3, i 3＞0
ΔL 2＝(m-1)h 11-i 2/1-i 1(i 1/i 2) 2
Flexure spring stiffness coefficient K 1
K 1＝P c(i=i 2)A-F(i-i 2)/j(ΔL 1-ΔL 2)
The stiffness coefficient K of stiffness spring 2
&lt;math><msub><mi>k</mi><mi>2</mi></msub><mi>=</mi><mfrac><mrow><msub><mi>P</mi><mi>c</mi></msub><msub><mi>(i=i</mi><mi>1</mi></msub><msub><mi>)A-F(i=i</mi><mi>1</mi></msub><msub><mi>)-jK</mi><mi>1</mi></msub><msub><mi>［ΔL</mi><mi>1</mi></msub><msub><mi>-(m-1)h</mi><mi>1</mi></msub><mi>］</mi></mrow><mrow><msub><mi>j(m-1)h</mi><mi>1</mi></msub><mi>［</mi><mfrac><mrow><msup><mi>i</mi><msub><mi>2</mi></msup><mi>1</mi></msub><msup><mi>-i</mi><msub><mi>2</mi></msup><mi>2</mi></msub><msup><mi>-i</mi><msub><mi>2</mi></msup><mi>1</mi></msub><msub><mi>i</mi><mi>2</mi></msub><msub><mi>+i</mi><mi>1</mi></msub><msup><mi>i</mi><msub><mi>2</mi></msup><mi>2</mi></msub></mrow><mrow><msub><mi>(1-i</mi><mi>1</mi></msub><msup><mi>)i</mi><msub><mi>2</mi></msup><mi>2</mi></msub></mrow></mfrac><mi>］</mi></mrow></mfrac></math>
Three, load is for becoming moment of torsion, and non-centrifugal working machine need design cluster spring according to the characteristic of working machine.
This shows, the design method of above-mentioned Ω valve cluster spring, both based on rigorous theoretical analysis, the form with a kind of practicality provides again, and is simple, grasps easily and promotes, and those skilled in the art all can be competent at.
Variable-speed clutch proposed by the invention since have cluster spring and with the Ω valve of its coupling, can realize ideally that speed governing and running are stable, can be adapted to various loading condition, be a kind of novel speed-regulating actuator.This device can be used for blower fan water pump, engineering machinery, and mining machinery as transmission and arrangements for speed regulation, can be received raising throughput in the various machineries such as boats and ships, increases the service life, energy saving, positive effect such as reduce cost.

Claims (7)

1, a kind of variable-speed clutch, the Ω valve 3 that it has driving shaft 1, driven shaft 6, friction plate group 2, control piston 4, bearing 7 and is contained on the driven shaft 6 and rotates therewith, spool 12 radial arrangement of Ω valve 3 also can radially move back and forth, and it is characterized in that:
(1) it also has one or more (for example 3～16) cluster spring 5, the rear side of control piston 4 is installed or be installed in equably to this cluster spring or a plurality of cluster spring, and each cluster spring cylindrically coiled spring different by two stiffness coefficients and that be uneven in length is in parallel or be in series.
(2) said Ω valve 3 is made up of valve body 11, spool 12, valve gap 13 and standard link, wherein:
(2.1) have on the valve body 11 oil circuit 18 that joins with high-voltage oil cavity and 19 and diameter be d 3Draining hole 14;
(2.2) spool 12 is that a diameter is d 1Cylindrical body, it is d that there is a diameter its lower end 3Short cylinder 15, it is d that a diameter is arranged in the end of short cylinder 15 2Oil pocket 16, and connect by the oil circuit 18 and the hyperbaric chamber of control piston;
(2.3) valve gap 13 is provided with annular oil cavity 17, and is P by oil circuit 19 with pressure cControl oil channel connect.
2, clutch according to claim 1 is characterized in that cluster spring in parallel can be made up of two different cylindrically coiled spring suits of diameter, and the little person's length of stiffness coefficient is big, is sleeved on the outer ring.
CN86100396A 1986-01-14 1986-01-14 Speed regulation clutch with omega valve and compound spring Expired CN86100396B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN86100396A CN86100396B (en) 1986-01-14 1986-01-14 Speed regulation clutch with omega valve and compound spring

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN86100396A CN86100396B (en) 1986-01-14 1986-01-14 Speed regulation clutch with omega valve and compound spring

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CN86100396A CN86100396A (en) 1987-07-29
CN86100396B true CN86100396B (en) 1988-08-24

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CN86100396A Expired CN86100396B (en) 1986-01-14 1986-01-14 Speed regulation clutch with omega valve and compound spring

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100339602C (en) * 2004-12-15 2007-09-26 中国船舶重工集团公司第七一一研究所 Speed regulating clutch control system with pilot type servo valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0310969D0 (en) * 2003-05-13 2003-06-18 Ricardo Uk Linmited Clutches

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100339602C (en) * 2004-12-15 2007-09-26 中国船舶重工集团公司第七一一研究所 Speed regulating clutch control system with pilot type servo valve

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