CN1052172A - Hydraulic motor with constant-stress rolling track and radial spherical pistons - Google Patents
Hydraulic motor with constant-stress rolling track and radial spherical pistons Download PDFInfo
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- CN1052172A CN1052172A CN 89109027 CN89109027A CN1052172A CN 1052172 A CN1052172 A CN 1052172A CN 89109027 CN89109027 CN 89109027 CN 89109027 A CN89109027 A CN 89109027A CN 1052172 A CN1052172 A CN 1052172A
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Abstract
The present invention is strong and a kind of unidirectional reinforcement inner curve radial plunger type motor such as a kind of two-way grade.The raceway rings longitudinal profile is an equal contact stress torque pulsating movement free raceway curve; Horizontal section has the raceway groove that contacts with steel ball or 2 on roller; The piston small end is a spherical surface body, and big end is square cylinder, but teeter.The present invention can reduce the contact stress between rolling element and the raceway, limits local slippage, increases substantially the operating life of oil hydraulic motor.Unidirectional reinforcement oil hydraulic motor is used for the heavy operating mode of unidirectional loads, can obtain bigger effect.
Description
The present invention relates to the improvement of inner curve radial plunger steel ball or roller oil hydraulic motor or pump.
The inner curve radial plunger type motor is a kind of low speed high torque oil hydraulic motor, and it has compact structure, and the output torque pulsation is little, cranking performance rating height, advantage such as low-speed stability is good.It and high speed and high pressure Variable plunger pump can be formed hydrostatic transmission system.It can save the speed reducer in the transmission system, realizes directly driving, and complete machine structure is simplified; It can realize stepless change, easy-to-operat; It can improve the coupling of power train and internal-combustion engine, saves fuel consume; It is convenient to realize the seriation of product, forms the various deformation machine, opens up market widely.From development trend, the static pressure transmission may reach for mechanical transmission, hydraudynamic drive and electric drive in boundless mechanical field.
Current, obstruction inner curve radial plunger type motor main cause of extensive use in hydrostatic transmission system is: it is at the pressure height, and load is heavy, and the operating life on the machine of long operational time does not reach requirement.
Studies show that the operating life L of inner curve radial plunger type motor
10Depend on the contact stress σ o value between rolling element and the raceway, and the ringing frequency n Z of this stress, promptly
L
10∝ 1/(nzσ
010) (1）
In the formula: the single plunger number of Z-oil hydraulic motor;
The rotating speed of n-oil hydraulic motor.
We propose oil hydraulic motor objective function of optimization design function and are thus:
Z σ
10→ minimum; (2)
Obviously as seen, what play a decisive role is σ o value, because 10 powers of operating life and σ o value are inversely proportional to.
The numerical value of contact stress σ o can calculate according to hertz formula:
σo＝ (3N)/(2πab) （3）
In the formula: the N-normal force;
The oval major semi axis length of a-surface of contact;
The oval semi-minor axis length of b-surface of contact;
μ
1, μ
2The Poisson's ratio of-rolling element, raceway material;
E
1, E
2The Young's modulus of-rolling element, raceway material
ξ, η-elliptic integral function, its value depend on rolling element and raceway
Principal curvatures ρ
11, ρ
12And ρ
21, ρ
22
Σ ρ-rolling element and the raceway principal curvatures sum in longitudinal and transverse two sections
Σρ＝ρ
11+ρ
12+ρ
21+ρ
22（6）
In the contact ellipse the inside, the distribution of contact stress σ is the semiellipse spheroid:
σ= (3N)/(πab) (1-( (x)/(a) )
2-( (y)/(b) )
2)
1/2（7）
This shows, rolling element contacts with raceway rings, is the problem of a solid, at each locational contact stress σ o of raceway rings, it not only depends on the raceway curve shape of raceway rings in longitudinal profile, also depends on the profilogram shape of raceway rings horizontal section raceway groove simultaneously.
The raceway curve of existing inner curve radial plunger type motor has plenty of according to geometric viewpoint design, as the cosine cycloid that can process with simple eccentric wheel pattern.In the running of this oil hydraulic motor, when distributor makes plunger cavity from communicating with inflow pipeline, be transformed into when communicating, of short duration plunger cavity oil circuit choke-out process must be arranged with oil returning tube.At this moment,,, make that contact stress raises suddenly between pressure and rolling element and the raceway, cause noise, destroy raceway fluid in the extrusion chamber if raceway still forces plunger displacement.The output torque of this oil hydraulic motor has bigger pulsation.Distribution of contact inequality on the oil hydraulic motor raceway has higher peak value at local location, has limited the operating life of oil hydraulic motor.
What existing inner curve radial plunger type motor extensively adopted is the uniform acceleration raceway curve that designs according to the kinology viewpoint.This raceway curve is the relative kinematic rule according to given plunger one rolling element pair: promptly zero velocity-uniform acceleration-uniform velocity-etc. retardation-zero velocity characteristics of motion.To the acceleration change curve of this plunger-rolling element pair, do once and the quadratic integral computing, can try to achieve its speed, and displacement changing curve.Be provided with the zero-speed section on this raceway curve, when the choke-out of plunger cavity oil circuit, trunk piston set is not subjected to displacement, high pressure and the noise of having avoided " pocketed oil " to cause.Suitably distribute zero-speed, etc. acceleration, constant speed, etc. the argument of sections such as deceleration, can make each plunger relative velocity sum keep constant, can eliminate the pulsation of oil hydraulic motor output torque in theory, but, owing to do not take into account the influence of frictional force between plunger and cylinder hole, in fact torque pulsation fails to eliminate fully in the calculating.On the raceway of this oil hydraulic motor, the distribution of contact stress value is still uneven, and the peak stress position is at first destroyed, and has limited its operating life.
The existing raceway curve of inner curve radial plunger type motor on the forward and backward both direction is symmetrical, has identical contact fatigue strength.This oil hydraulic motor is used for folk prescription to rotation, perhaps a direction load is heavy, during the light occasion of other direction load, the operating life of oil hydraulic motor is heavy by load, the raceway intensity of this direction that the operating time is long is determined, therefore, whole motor is equivalent to have only " half " motor to bring into play effect.
The cross section curve of general radial plunger-steel ball hydraulic motor raceway groove, the normal circular curve that a bit contacts with steel ball that adopts, the radius of curvature of circular arc is slightly larger than the steel ball radius.
The cross section bus of general radial plunger-roller oil hydraulic motor raceway rings is a straight line.It is line in theory with cylindrical roller and contacts, and the contact stress value is reduced, and operating life improves.But, since the component machining error, reasons such as distortion and matching gap, and two buses of roller and roller surface can not keeping parallelism.In fact often remain a contact, the contact stress value is quite high.Meanwhile, roller has inclination slightly, and side rolling trend is just arranged, and makes between roller end face and the side plate to produce big frictional force, stops roller to roll, and makes the local slippage of generation in the surface of contact of roller and raceway, causes wearing and tearing.
The plunger and the cylinder hole of existing inner curve radial plunger type motor are all cylindrical, and plunger can only move along its centerline direction relative to the cylinder hole, and relative swing can not be arranged.In the oil hydraulic motor of reality, owing to reasons such as the error of component, matching gap, stress deformations, the cylinder centerline hole always is not positioned in the symmetry plane of raceway rings horizontal section, this just may cause that steel ball contacts with raceway groove side, or the roller side the edge effect that contacts with roller surface, and the contact stress peak value is raise.
Plane shelves ring is equipped with in the roller both sides of existing radial plunger-roller oil hydraulic motor.During the oil hydraulic motor running, the sliding friction of metal to metal is arranged between roller and the baffle ring.
Of the present invention to reduce the contact stress between rolling element and the raceway, restriction local slippage therebetween improves its rolling situation, reaches the purpose that improves the oil hydraulic motor operating life.Strong inner curve radial plunger type motor such as a kind of two-way grade and a kind of inner curve radial plunger type motor of unidirectional reinforcement have been proposed for this reason.The optimal curve of raceway rings longitudinal profile and horizontal section has been proposed.It in the longitudinal profile of raceway rings equal contact stress torque pulsating movement free raceway curve, it reduces the contact stress between rolling element and the raceway as far as possible, and keep evenly at main section, ensure that oil hydraulic motor does not have the pulsation phenomenon of entrap phenomenon and output torque simultaneously again; The raceway rings horizontal section is the continuous smooth raceway sheave profile that contacts with 2 of steel balls, or the straight line type raceway sheave profile that contacts with 2 of roller arc generatrixs; They had both reduced the contact stress between rolling element and the raceway, and the local slippage between the surface of contact is reduced to a minimum; The piston small end is a spherical surface body, and big end is square cylinder, and piston-rolling element pair can be swung in raceway cross section direction, even have at the oil hydraulic motor component under the situation of installation and processing error, rolling element is contacted appropriately with 2 of raceway grooves; The roller two ends are embedded with steel ball, suffered surface friction drag when rolling in order to reduce roller.The oil hydraulic motor of unidirectional reinforcement, it is heavy to the load of a running or a direction to be used for folk prescription, and the operating mode of long operational time can obtain bigger effect.Under this total design, following six summary of the invention are proposed:
1. plunger piston hydraulic motor such as rolling track and radial such as pulsating movement free such as strong equal contact stress torque such as two-way grade;
2. unidirectional reinforcement equal contact stress torque pulsating movement free rolling track and radial plunger piston hydraulic motor;
3. contact continuous smoothed curve raceway groove with 2 of steel balls;
4. contact straight line V-type rolling channel groove with 2 of roller arc generatrixs;
5. sphere piston one rolling element pair;
6. the roller of two ends embedding steel ball.
Equal contact stress torque pulsating movement free raceway curve of the present invention, its important technological parameters is the contact fatigue strength characteristic according to material, considers dynamic (dynamical) effect and definite.During the raceway curve, determining earlier the Yun Dong Gui Trace of rolling element central point, then, is round with the radius of rolling element, the outsourcing route of Zuo Gui Trace curve, Here it is raceway curve.
If the effect number of times of oil hydraulic motor is W, wait in the strong type oil hydraulic motor two-way, the work argument phi lowers w of forward and antiport equates:
φw＝ (π)/(w) （8）
Raceway curve in each work argument all is made up of following section: interior zero-speed section φ o, equal contact stress section φ s, torque balance section φ b and outer zero-speed section φ o.
Inside and outside zero-speed section φ o is separately positioned near the inside and outside dead point of curve.It is the one section circular arc concentric with oil hydraulic motor.Radial displacement does not take place in plunger-rolling element pair in this section, avoided the entrap phenomenon of plunger cavity.φ o is taken as 2～4 °.
In the equal contact stress section φ s, the contact stress value between rolling element and the raceway is than other section height, and the contact stress value has here determined the operating life of oil hydraulic motor.This section adopts the equal contact stress curve, does not have the peak point of contact stress, does not promptly have the weak especially point of contact fatigue strength.
The equal contact stress curve is that the differential equation according to the equal contact stress curve gets.
With the coordinate of following and rolling element central motion Gui Trace (ρ, φ), first derivative d ρ/d φ, second dervative d
2ρ/d φ
2The representation of relevant parameters, substitution hertz formula (3～5), and make σ o=constant, the differential equation of Here it is equal contact stress curve (rolling element central motion Gui Trace curve).Act on each active force on the piston make a concerted effort be:
ΣP＝P
h+P
j+P
f+P
c+P
s（9）
In the formula: suffered hydraulic coupling on the Ph-piston;
P
h=ρ (πd
2 O)/4 （10）
The p-oil liquid pressure, establishing p in the calculating is constant;
d
o-piston diameter;
P
jThe inertial force that-piston-the rolling element pair is subjected to;
P
j＝m
ρω
2 d 2 ρ/dφ
2（11）
m
ρThe quality of-piston-rolling element pair;
ω-oil hydraulic motor angular velocity of rotation;
P
fThe frictional force that-piston is subjected to;
P
f＝μP
htgβ＝μP
hdρ/ρdφ （12）
The pressure angle of β-raceway curve;
Friction factor between μ-piston skirt and the cylinder body guiding groove;
Pc-piston-rolling element pair is subjected to centrifugal force;
Pc＝mρω
2ρm （13）
The center of gravity of ρ m-piston-rolling element pair is to the distance at oil hydraulic motor center;
The spring force that the Ps-piston is subjected to;
Ps＝Cs△ρs
The rigidity of Cs-spring;
The amount of deformation of △ ρ s-spring.
Acting on a normal force on the point of contact is:
Angle between the normal of α-rolling element and raceway groove point of contact and the raceway groove symmetry center face.
For steel ball hydraulic motor:
Σρ = 4/(dB) + 1/(Rc) + 1/(RG) （15）
Rc-raceway curve with the steel ball point of contact on radius of curvature;
d
B-steel ball size;
R
G-raceway groove curve with the steel ball point of contact on radius of curvature.
For the roller oil hydraulic motor
Σρ＝ 2/(dr) + 1/(Rr) + 1/(Rc) （16）
d
r-roller diameter;
R
rThe radius of curvature of-roller arc generatrix;
The radius of curvature R c of raceway curve is:
Utilize electronic computer can find the solution above-mentioned differential equation easily, try to achieve rolling element central motion Gui Trace curve the each point coordinate figure (ρ, φ).Thus, can be in the hope of raceway curvilinear coordinates (ρ c, φ c):
ρc＝ρCosε+ (d)/2 Cos（β-ε） （18）
φc＝φ-ε （19）
ε＝arctg (d/2Sinβ)/(ρ+d/2Cosβ) （20）
Equal contact stress section argument phi lowers s is:
φs＝ (π)/(Z) -2φo-φb （21）
In the torque balance section φ b, plunger is finished retarded motion.Its deceleration value also changes.The curve of φ b section is according to the oil hydraulic motor output pulseless condition of torque and definite.In the pulseless condition of this torque, taken into account the frictional force P of piston skirt and guiding groove
fInfluence, rather than generally only consider the balance of each momentary velocity of piston.Because torque pulsation mainly influences the tick-over stability of oil hydraulic motor, therefore, can ignore inertial force P in the calculating
jInfluence with centrifugal force Pc.
The torque that single piston produces is:
M
i＝ρT＝ρΣPtgβ＝ρ（P
h-P
f）tgβ
＝P
h（1-μ (dρ)/(ρdφ) ）（ (dρ)/(dφ) ） （22）
Can draw thus, when input oil pressure and flow were constant, the condition that oil hydraulic motor output torque is not pulsed was:
Σ (1-μ (d ρ)/(ρ d φ))
i((d ρ)/(d φ))
i=constant (23)
The variation of each piston motion parameter sum of oil hydraulic motor is the cycle with phase declinate △ φ always.△ φ is
△φ＝ (2πm)/(WZ) （24）
In the formula: the greatest common divisor of m-W and Z.
The argument phi lowers b of torque balance section is:
φb＝△φ＝ (2πm)/(WZ) （25）
After the curve for the treatment of zero-speed section φ o and equal contact stress section φ s is determined, coordinate ρ and first derivative (d ρ)/(d φ) value according to its curve, substitution torque balance equation (23) can be tried to achieve first derivative (d ρ)/(d φ) curve of the curve of corresponding torque balance section φ b.This curve is done an integral operation, can try to achieve the rolling element central motion rail Trace and the raceway curve of torque balance section.
So far, whole equal contact stress torque pulsating movement free raceway curve is all tried to achieve.
Unidirectional reinforced equal contact stress torque pulsating movement free raceway curve of the present invention can guarantee that rolling motor rotates and reverse all normal smooth operation.But the bearing capacity and the operating life of this oil hydraulic motor postive direction running are much higher.
The design of unidirectional reinforced equal contact stress oil hydraulic motor and above-mentioned two-way the same of strong type of waiting, just the equal contact stress section argument phi lowers s1 of postive direction is greater than reciprocal argument phi lowers s2.Promptly
φs1＞φs2 （26）
Increase φ s1 value, can reduce contact stress σ o value, improve its operating life.Increase the degree of φ s1 value, the difference that depends on positive and negative direction operating load reaches the different requirements to operating life.
When increasing φ s1, should reduce φ s2 simultaneously, keep:
φs1+φs2＝2φs （27）
Like this, unidirectional reinforced only be that the two-way strong type oil hydraulic motor that waits is at raceway rings and the different a kind of amelioration product of two parts of thrust plate.And these two part installation direction differences can change the direction of reinforcement, to producing and using all very convenient.
A kind of raceway groove curve that contacts with 2 of steel balls of the present invention is a smooth continuous curve.When determining curve, both consider to reduce as far as possible the contact stress value, considered to reduce as far as possible the relative slippage between interior rolling element of surface of contact and the raceway groove again.Slippage increases the energy loss of rolling relatively, quickens the wearing and tearing of raceway groove.
Steel ball is an oval calotte with contacting of raceway groove.When steel ball rolled, in surface of contact, only on that of instantaneous center of rotation axle, the speed of related movement between steel ball and the raceway was zero, does not produce relative slippage.On the position near instantaneous center of rotation, because the resiliently deformable of contact material, slippage may not take place yet relatively.On the center of rotation position bigger apart from S, sliding phenomenon is more serious.
Increase the radius of curvature of steel ball and raceway groove contacting point, can shorten the length of the radius b of contact ellipse, reduce slippage.But, can increase contact stress σ o value like this.
In order to reduce by two normal forces on the point of contact, reduce each point in the surface of contact to instantaneous center of rotation apart from S, reduce slippage, all should reduce angle 2 α between two contact normas.But, reduce 2 α values excessively, as α＜Sin
-1When ((2b)/(d)), two contact ellipse will be partly overlapping.The contact stress value of overlapping part peak stress (seeing Fig. 4 b) occurs with superposition.
One of embodiment of the raceway groove curve that the present invention contacts with 2 of steel balls is decided to be raceway groove curvilinear equation:
y＝Ax
k（28）
Coefficient A and K are determined by following simultaneous equations in the formula:
AKx
（K-1）＝tg（Sin
-1(2b)/(d) ） （30）
In the formula: R
GThe radius of curvature of-raceway groove curve and steel ball contacting point
R
G＝（0.51～0.52）d;
The semiaxis length of b-contact ellipse face.By formula calculate with the parameter substitution of equal contact stress section (5), and the φ that calculates Chinese style (10) gets the high workload force value.
Can only in equal contact stress section φ s, adopt the raceway groove of 2 contacts, still adopt general single-point contact arc raceway groove at all the other sections.This does not influence the raising of oil hydraulic motor operating life.
The raceway sheave profile that contacts with 2 of roller arc generatrixs of the present invention is the V-shaped line of two rectilinear(-al)s.In order to make two distances between the point of contact be substantially equal to half of roller length L, angle 2 θ between the V-shaped line should be: 2 θ ≌ 2Cos
-1((d)/(Rr)), wherein d is the nominal diameter of roller; Rr is the radius of curvature of roller arc generatrix.Increase the Rr value and can reduce contact stress σ o value, but improved requirement machining accuracy.
Sphere piston of the present invention-rolling element pair, its piston divides big or small two, and the piston microcephaly is a spherical surface body, and it is free to rotate and move along the cylinder centerline hole in cylindrical cylinder hole; The piston major part is a square cylinder, in its planar guide groove on cylinder body, can move along center, cylinder hole and move in the plane parallel with guiding groove.Therefore, whole sphere piston-rolling element pair is finished only along the cylinder centerline hole and is moved and swing around piston microcephaly spherical surface body center in the plane parallel with guiding groove.
Sphere piston-rolling element pair can have certain swing degrees of freedom in the cylinder body cross section, this just makes 2 of the profile lines of the raceway groove in rolling element and the raceway rings horizontal section contact, even there is machining error in each part of oil hydraulic motor, part deformation and gap etc.In order to remedy the shortcoming of spherical surface body piston seal poor performance, seal groove is arranged, the combination seal of forming by zero shape rubber seal and U-shaped plastic sealing ring in the groove on the spherical surface body.
Two ends of the present invention are embedded with the roller of steel ball, and it makes the sliding friction between general roller and the side plate washer become rolling friction, and between rolling body and the steel ball, because the existence of antifriction ball pad is arranged, its friction factor is very little, does not produce catching phenomenon, helps improving the operating life of raceway.
As previously mentioned, the operating life L of oil hydraulic motor of the present invention
10And 10 powers of contact stress σ o value are inversely proportional between rolling element and the raceway.A little reduction of contact stress just can make the oil hydraulic motor operating life obtain significantly to improve.For example, σ o value reduces by 7%, L
10Bring up to 2 times; σ o value reduces by 20%, L
10Bring up to 10 times; σ o value reduces by 26%, L
10Bring up to 20 times.Experiment shows, equal contact stress oil hydraulic motor of the present invention, and with physical dimension, the general uniform acceleration oil hydraulic motor that type is identical is compared, and operating life can improve several times to ten several times.The efficiency characteristic of oil hydraulic motor and low-speed stability also have sizable raising.
Following accompanying drawing has shown principle of the present invention, and embodiment's concrete structure is provided.
Fig. 1, the free-body diagram of raceway in the vertical and horizontal section.
Fig. 2, the two-way strong type equal contact stress torque pulsating movement free raceway curve that waits reaches contact stress σ o, tg β, the isoparametric variation diagram of radius of curvature 1/Rc.
Fig. 3, unidirectional reinforced equal contact stress torque pulsating movement free raceway curve, and contact stress σ o, tg β, the isoparametric variation diagram of radius of curvature 1/Rc.
Fig. 4, the local slippage schematic representation in the raceway groove curve, contact stress σ and surface of contact; A, steel ball single-point contact arc raceway groove; B, 2 inter_curve raceways of steel ball groove; C, 2 contacts of roller V-type rolling channel groove.
Fig. 5, sphere piston one steel ball pair, a, structural drawing; B, combination seal (enlarged view).
Fig. 6, sphere piston-roller pair, the scheme of a, a steel ball of the every end band of roller; The scheme of b, a plurality of steel balls of the every end band of roller.
Fig. 7, an embodiment's of employing sphere piston of the present invention-steel ball pair longitudinal sectional view.
Fig. 8, an embodiment's of employing sphere piston of the present invention-roller pair longitudinal sectional view.
Fig. 9, an embodiment's of the unidirectional reinforced raceway of employing of the present invention and sphere piston-steel ball pair longitudinal sectional view.
Figure 10, an embodiment's of the unidirectional reinforced raceway of employing of the present invention and sphere piston-roller pair longitudinal sectional view.
Figure 11, the present invention are used for an embodiment's the transverse sectional view of the vehicle bridge driver of engineering Transport Machinery vehicle static pressure transmission.It is made up of two hydraulic motor with constant-stress rolling track and radial spherical pistons arranged side by side.The splined hole at the middle part of left and right hydraulic motor cylinders (4) is connected with the left and right half (26) that drives vehicle bridge, directly removes to drive left and right wheels.Drive shell is connected with axle tube, forms driving axle housing.
Among the figure, the 1-raceway rings; 2-sphere piston-steel ball pair; 3-sphere piston-roller pair; The 4-cylinder body; 5-plane thrust plate; The spherical surface body of 6-piston; The seal groove of 7-piston; The 8-black box; The square cylinder of 9-piston; The 10-steel ball; The 11-roller; 12-antifriction ball pad; 13-antifriction watt shape pad; 14-cylinder hole; Guiding groove on the 15-cylinder body; 16-U moulds the material seal ring; 17-zero shape rubber seal; The circular hydrostatic support oil pocket of 18-; The square hydrostatic support oil pocket of 19-; The 20-choke; 21-steel ball rolling channel groove; The steel ball of 22-roller; 23-roller baffle plate; 24-antifriction ball pad; The arc generatrix of 25-roller; 26-vehicle drive axle semiaxis; The 27-actuator housing; The 28-bearing seat; The V-arrangement raceway groove of 29-roller, the strong equal contact stress torque of the two-way grade of 30-pulsating movement free raceway curve; The unidirectional reinforcement equal contact stress of 31-torque pulsation raceway curve.
The P-oil inlet and outlet; The D-leakage hole; The c-instantaneous center of rotation; Any is to the distance of instantaneous center of rotation on the S-surface of contact; SR-sphere piston radius of sphericity.
Claims (6)
1, a kind of inner curve radial plunger type motor or pump, by raceway rings [1], plunger-steel ball pair [2] or plunger-roller pair [3], cylinder body [4] and plane thrust plate main parts size such as [5] are formed, it is characterized in that: the longitudinal profile of the internal surface of raceway rings [1] is a strong equal contact stress torque pulsating movement free raceway curve such as two-way grade [30], and the forward working cap angle φ z of this curve equates with reverse operation argument phi lowers F: φ z=φ F=φ w=(π)/(w); Curve in each work argument phi lowers w is by interior zero-speed section φ o, and equal contact stress section φ s, torque balance section φ b reach outer zero-speed section φ o and form; Zero-speed section cap angle φ o=2～4 °, equal contact stress section argument phi lowers s=(π)/(w)-2 φ o-φ b, torque balance section argument phi lowers b=(2 π m)/(Zw); In the zero-speed section, curve is to be the circular arc in the center of circle with the oil hydraulic motor rotating center, in equal contact stress section φ s, and the coordinate of each point on the curve (ρ, φ), first derivative ((d ρ)/(d φ)) and second dervative ((d
2ρ)/(d φ
2)) value substitution formula (3-20), the contact stress δ o value of being tried to achieve all should equate; In torque balance section φ b, coordinate of each point on the curve (ρ, φ) and first derivative ((d ρ)/(d φ)) value, substitution formula (23), the gained result all should equate.
2, a kind of inner curve radial plunger type motor or pump, by raceway rings (1), plunger one steel ball pair (2) or plunger one roller pair (3), cylinder body (4) and plane thrust plate main parts size such as (5) are formed, it is characterized in that: the longitudinal profile of the internal surface of raceway rings (1) is a unidirectional reinforcement equal contact stress torque pulsating movement free raceway curve (31), and the forward work range φ z of this curve is greater than reverse operation argument phi lowers F: φ Z＞φ W＞φ F; And φ Z+ φ F=(2 π)/(W); Each is the curve in work range angle φ Z or the φ F forward or backwards, by zero-speed section φ o, and forward equal contact stress section φ sz or reverse equal contact stress section φ sF, torque balance section φ b and outer zero-speed section φ o composition; Zero-speed section argument phi lowers o=2～4 °, torque balance section argument phi lowers b=(2 π m)/(WZ), forward equal contact stress section amplitude φ sz is greater than reverse equal contact stress section amplitude φ sF: φ sz＞φ sF, and φ sz+ φ sF=(2 π)/(W)-4 φ o-2 φ b; In zero-speed section φ o, curve is to be the circular arc in the center of circle with the oil hydraulic motor center, in equal contact stress section φ sz or φ sF forward or backwards, and the coordinate of each point on the curve (ρ, φ) first derivative ((d ρ)/(d φ)) and second dervative (((d
2P)/(d φ
2))) value substitution formula (3-20), the contact stress σ o value of being tried to achieve all should equate that in torque balance section φ b, coordinate of each point on the curve (ρ, φ) and first derivative ((d ρ)/(d φ)) value, substitution formula (23), gained result are all equal.
3, oil hydraulic motor as claimed in claim 1 or 2 or pump, it is characterized in that: the horizontal section of the internal surface of raceway rings (1) is the continuous smooth raceway groove curve (21) that contacts with (10) two of the steel balls of plunger one steel ball pair (2), the radius of curvature R on curve and the steel ball point of contact
G=(0.51～0.52) d, angle 2 α of the normal on two point of contact of curve are slightly larger than 2Sin
-1((2b)/(d)).
4, oil hydraulic motor as claimed in claim 1 or 2 or pump is characterized in that: the horizontal section of the internal surface of raceway rings (1) is the V-shaped line of the raceway groove that contacts with 2 of the arc generatrixs of the roller (11) of plunger, roller pair (3); V-shaped line is by two rectilinear(-al)s, therebetween angle 2 θ ≌ 2Cos
-1((d)/(Rr)); The straight-line intersection place can establish grinding undercut.
5, oil hydraulic motor as claimed in claim 1 or 2 or pump, it is characterized in that: the plunger of plunger-steel ball pair (2) or plunger-roller pair (3) is a sphere piston, be that the plunger small end is spherical surface body (6), on seal groove (7) is arranged, the black box of being made up of O shape rubber seal (17) and U-shaped plastic sealing ring (16) (8) wherein is housed; The big end of piston is square cylinder (9), and it is arranged in each guiding groove of cylinder body (4) (15).
6, oil hydraulic motor as claimed in claim 1 or 2 is characterized in that: the two ends of the roller of plunger-roller pair (3) respectively are embedded with at least one steel ball (22); Each contacts steel ball with the plate washer (23) of raceway both sides; The hemisphere antifriction pad (24) that the tinsel of plastic covering layer is made is housed between steel ball and the rolling body, and projection is arranged at the top of antifriction pad, stretches in the positioning hole of rolling body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89109027 CN1018277B (en) | 1989-11-28 | 1989-11-28 | Hydraulic motor with constant-stress rolling track and radial spherical pistons |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89109027 CN1018277B (en) | 1989-11-28 | 1989-11-28 | Hydraulic motor with constant-stress rolling track and radial spherical pistons |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1052172A true CN1052172A (en) | 1991-06-12 |
| CN1018277B CN1018277B (en) | 1992-09-16 |
Family
ID=4857837
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 89109027 Expired CN1018277B (en) | 1989-11-28 | 1989-11-28 | Hydraulic motor with constant-stress rolling track and radial spherical pistons |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1018277B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1049721C (en) * | 1994-03-26 | 2000-02-23 | 齐茂林 | Limiting protection structure for radial plunger type hydraulic motor and pump |
| CN101832245A (en) * | 2010-04-28 | 2010-09-15 | 北京航空航天大学 | Double-plunger pulse-free flow combining method and direct-drive plunger pump |
| CN103562544A (en) * | 2011-05-23 | 2014-02-05 | 罗伯特·博世有限公司 | Hydrostatic radial piston machine and piston for a hydrostatic radial piston machine |
| CN106194571A (en) * | 2016-09-14 | 2016-12-07 | 杨健 | A kind of rotary casing type hydraulic motor |
| CN106536925A (en) * | 2014-04-25 | 2017-03-22 | 波克兰液压工业设备公司 | Hydraulic machine with radial pistons comprising a casing not exhibiting symmetry of revolution |
| CN109882350A (en) * | 2019-03-03 | 2019-06-14 | 宁波精润机械有限公司 | A kind of hydraulic motor plunger lid |
| CN107806391B (en) * | 2017-11-08 | 2023-10-31 | 南昌大学 | Radial hydraulic plunger motor |
-
1989
- 1989-11-28 CN CN 89109027 patent/CN1018277B/en not_active Expired
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1049721C (en) * | 1994-03-26 | 2000-02-23 | 齐茂林 | Limiting protection structure for radial plunger type hydraulic motor and pump |
| CN101832245A (en) * | 2010-04-28 | 2010-09-15 | 北京航空航天大学 | Double-plunger pulse-free flow combining method and direct-drive plunger pump |
| CN101832245B (en) * | 2010-04-28 | 2013-09-18 | 北京航空航天大学 | Double-plunger pulse-free flow combining method and direct-drive plunger pump |
| CN103562544A (en) * | 2011-05-23 | 2014-02-05 | 罗伯特·博世有限公司 | Hydrostatic radial piston machine and piston for a hydrostatic radial piston machine |
| CN103562544B (en) * | 2011-05-23 | 2016-04-13 | 罗伯特·博世有限公司 | Hydrostatic radial piston machine and the piston for hydrostatic radial piston machine |
| CN106536925A (en) * | 2014-04-25 | 2017-03-22 | 波克兰液压工业设备公司 | Hydraulic machine with radial pistons comprising a casing not exhibiting symmetry of revolution |
| CN106536925B (en) * | 2014-04-25 | 2019-06-04 | 波克兰液压工业设备公司 | Hydraulic press with the radial piston for including non-rotationally-symmetric shell |
| CN106194571A (en) * | 2016-09-14 | 2016-12-07 | 杨健 | A kind of rotary casing type hydraulic motor |
| CN106194571B (en) * | 2016-09-14 | 2018-01-09 | 杨健 | A kind of rotary casing type hydraulic motor |
| CN107806391B (en) * | 2017-11-08 | 2023-10-31 | 南昌大学 | Radial hydraulic plunger motor |
| CN109882350A (en) * | 2019-03-03 | 2019-06-14 | 宁波精润机械有限公司 | A kind of hydraulic motor plunger lid |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1018277B (en) | 1992-09-16 |
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