CN102431529A - Hydrodynamic retarder - Google Patents

Hydrodynamic retarder Download PDF

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Publication number
CN102431529A
CN102431529A CN201110268250XA CN201110268250A CN102431529A CN 102431529 A CN102431529 A CN 102431529A CN 201110268250X A CN201110268250X A CN 201110268250XA CN 201110268250 A CN201110268250 A CN 201110268250A CN 102431529 A CN102431529 A CN 102431529A
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CN
China
Prior art keywords
impeller
braking position
stopper section
mobile
spring
Prior art date
Application number
CN201110268250XA
Other languages
Chinese (zh)
Inventor
迪特尔·劳克曼
托马斯·奥赫尔
亚历山大·施雷贝尔
Original Assignee
沃依特专利有限责任公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE102010046374 priority Critical
Priority to DE102010046374.4 priority
Priority to DE102010049704 priority
Priority to DE102010049704.5 priority
Application filed by 沃依特专利有限责任公司 filed Critical 沃依特专利有限责任公司
Publication of CN102431529A publication Critical patent/CN102431529A/en

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60TVEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T10/00Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
    • B60T10/02Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope with hydrodynamic brake
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/007Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders with variable brake geometry, e.g. axially movable rotor or stator
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/04Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders with blades causing a directed flow, e.g. Föttinger type

Abstract

The hydrodynamic retarder comprises a bladed primary wheel (1) and a bladed secondary wheel (2), which together forms a working chamber (3) filled with working medium. One of the two wheels is axially displaceable with its bladed subareas (1.1,2.1) corresponding to the other wheel. A delay unit (4) is provided for damping the striking of the wheel against a stop (6) during the axial displacement of the wheel into the braking position or non-braking position.

Description

Hydraulic brake

Technical field

The present invention relates to that a kind of it has two impellers specifically according to the hydraulic brake as described in the preamble of claim 1, i.e. an elementary impeller and a secondary impeller, at least one in these impellers can move axially with respect to another.

Background technology

The mobility of at least one is used for reducing the loss power of hydraulic brake zero load in two impellers.The for example clear a kind of drg of DE 10219753A1, wherein elementary impeller (rotor) is placed on the hollow shaft by means of screw thread, and when running under braking carries out the transition to non-running under braking, zero load, elementary impeller is away from secondary impeller (stator).In order to change over to once more in the running under braking, therefore rotor can form flow circuit in the epitrochoidal chamber between rotor and stator once more near stator, can torque be transferred on the stator from rotor by means of this flow circuit, therefore makes the rotor braking.

Also known movable impeller each other carries out the fluid power coupling.US 2359930 disclosed that kind for example, it has axle drive shaft that has pump impeller and the driven axle that has turbine, wherein pump impeller is placed on the outside thread of axle drive shaft like this, promptly its can with respect to turbine near with away from.On the end of the end face side of axle drive shaft, be provided with the annular element that has spring, wherein spring axially is applied to power on the pump impeller on the direction of axle drive shaft at actuator.

Near the time, promptly when axle drive shaft rotation was quickened, a masterpiece was used on the pump impeller, it has caused that promptly pump impeller moves on screw thread in contrast to the spring force on the direction of turbine.As long as the load that on this position, is resisted against on the axle drive shaft keeps fixing basically, then this just keeps at normal operation period always.In case yet this load reduces or advance operation when drive spindle changes over to; That is to say if driven shaft rotates with the rotating speed higher than axle drive shaft; Then spring force is excessive and pump impeller is pushed on the position away from turbine, thereby the flow circuit in the epitrochoidal chamber between pump impeller and turbine can not be transferred to torque on the turbine from pump impeller more effectively.

Therefore described fluid power be coupling near the time and fixing in servicely torque is transferred on driven machine from drive machines almost through flow circuit.When the load on drive side reduced, as described, pump impeller was away from turbine, so flow circuit is disturbed and therefore automatic interruption is transferred to torque on driven machine from drive machines.Yet utilize this fluid power coupling not carry out hydraulic brake to driven machine; This is because at first be not provided for the fixedly device of pump impeller; And in this external state of desirably braking; If promptly driven axle is faster than axle drive shaft rotatably, then pump impeller be positioned at respect to turbine away from the position on.

What in hydraulic brake, be worth expectation is, it is in service as far as possible promptly to carry out the transition to work from zero load, promptly or rather after chaufeur provides brake request, is carried out the transition in the running under braking by non-running under braking.Two impellers must as far as possible promptly be brought on its braking position thus; Two paddle shafts are to being adjacent in the face of arranging on this position; Thereby in epitrochoidal chamber, can be formed in desired working cycle between two impellers, and carry out torque transfer by means of this working medium.

The path that moves axially for restrict rotor and stator is known that the stopper section is set.Therefore rotor is being resisted against when reaching braking position on the stopper section when on stator, moving, and the adjacent component of hydraulic brake gets in the oscillatory regime thus, and therefore produces noise.This noise becomes big then to be felt bad and has interference for design has the passenger in the vehicle of this drg, thereby has room for improvement at this.

Summary of the invention

The objective of the invention is to, propose a kind of at least one axially hydraulic brake of the impeller of ability displacement that has, wherein avoided the shortcoming when the work that carries out the transition to from zero load is in service with respect to known embodiment.Especially, should when impeller being brought on braking position and/or the non-braking position, avoid noise to become big.

Realize according to the described hydraulic brake of independent claims through a kind of according to the object of the invention.Dependent claims has been explained favourable and particularly suitable embodiment of the present invention.

Hydraulic brake according to the present invention comprises elementary impeller that blade is housed and the secondary impeller that blade is housed; These impellers constitute the epitrochoidal chamber that can fill working medium each other; Wherein at least one in two impellers can be utilized at least it that part of vane zone is housed to move axially like this with respect to another impeller; Promptly this impeller can switch between braking position and non-braking position; This paddle shaft is to being adjacent to arrange that in the face of another impeller this impeller is to arrange to the bigger axial spacing of another impeller with respect to braking position on non-braking position on braking position.

If with one in latter two impeller, for example elementary impeller is driven in rotation; Then the working medium in the epitrochoidal chamber that part of vane zone formation is housed through two outwards quickens through the blade radial of driven impeller; Flow into being equipped with in the part of vane zone in the face of the secondary impeller that is provided with; And radially inwardly slow down there, therefore regulate the circulation of the working medium in the epitrochoidal chamber.

On second farther position; Impeller that promptly therein can longitudinal travel the part of vane zone is housed by being equipped with on the position of moving in the part of vane zone with respect to another impeller; Be based on two between the zone that blade is housed distance and can not regulate the flow circuit in the epitrochoidal chamber, therefore do not transmit torque or between impeller, do not transmit torque basically.Avoid the loss that in no-load run, is not supposed to thus as much as possible or fully.

In order to realize moving axially; In two impellers at least one, be that elementary impeller or secondary impeller are assigned a control apparatus; This control apparatus applies displacing force to mobile impeller, thereby makes the impeller can be near another impeller or can be away from another impeller on the direction of non-braking position.

Hydraulic brake also comprise be used to limit mobile impeller or its stopper section of the mobile route in part of vane zone is housed.

Be provided with speed reduction gearing according to the present invention; Forever at paddle shaft when moving to braking position and/or non-braking position; The bump of impeller on the stopper section cushioned; Wherein design speed reduction gearing like this, promptly the speed reduction gearing power that will react on displacing force is applied on the mobile impeller, and speed reduction gearing only mobile route, in the last subregion before the stopper section, work.Replacedly; Speed reduction gearing also can be described as being used at paddle shaft when moving to braking position and/or non-braking position, slow down speed, or the speed reduction gearing of the acceleration/accel of the impeller that is used to slow down of impeller; This be because the speed that makes impeller through speed reduction gearing when it moves axially with respect to not reducing according to the embodiment of speed reduction gearing of the present invention; Perhaps when the speed of impeller increases, the speed recruitment is reduced at least, and and then reduce to slow down in other words acceleration/accel.

In service in order especially promptly to realize carrying out the transition to work from zero load, must make one mutual quickening in two impellers near process near process or two impellers.Must make the displacing force of control apparatus big like this to this, if when promptly impeller for example should move on the braking position by non-braking position, it is higher relatively to make mobile impeller or its that acceleration/accel (on axial direction) of the subregion of impeller is housed.Produce noise on the stopper section for fear of being resisted against owing to impeller; Through speed reduction gearing make higher, reduce through moving axially the axial acceleration that causes or the speed of impeller, this speed reduction gearing only mobile route, in the last subregion before the stopper section, particularly on braking position, work.Can significantly improve the comfort level that has the passenger in the vehicle of this hydraulic brake in design thus.

Advantageously; Mobile impeller by means of hub spindle to being placed in movably on the axle; Its axis has outside thread, particularly steep screw thread and wheel hub has complementary negative thread, makes the impeller can be with respect to axial translation on axial direction thereby drive through rotation axle or impeller; Wherein wheel hub utilize profile, the end face towards the stopper section is resisted against on the stopper section on braking position and/or non-braking position.

Preferably, speed reduction gearing comprises at least one electricity, machinery, hydraulic pressure and/or compressed-air controlled shock absorber part, wherein shock absorber part be positioned on the axial direction can displacement impeller, particularly wheel hub and stopper section between, and particularly be fixed on the stopper section.At this, the shock absorber part of machinery can for example have friction face, by means of this friction face mobile impeller is slowed down, and in contrast, electric shock absorber part for example is meant the drg according to the type of work of eddy-current brake.Hydraulic pressure and/or the compressed-air controlled shock absorber part for example be known as the piston-cylinder-unit of filling oil and/or air.

Particularly preferably, shock absorber part be designed to elastic element, particularly be designed to the cup spring of spring-for example-, perhaps be designed to comprise the spring leaf group of a plurality of springs, the spring rigidity of its medi-spring/a plurality of springs has the tendency of progression.The tendency of progression means that at this spring force is particularly crossed ratio ground and risen with rising on the spring path that increases.That is to say that along with displacement path increases, speed and/or the acceleration/accel of impeller in last subregion reduces with respect to displacement path with crossing ratio.

Advantageously, shock absorber part is processed by vibration-absorptive material, particularly polymer at least in part, perhaps is coated with vibration-absorptive material.Certainly replace polymer also can consider to use other vibration-absorptive material, for example use rubber or rubber, and it for example is connected with stopper section and/or wheel hub as interchangeable embolus form fit and/or power with transmitting.

According to an embodiment, the stopper section is additionally partly or entirely processed by vibration-absorptive material, or is furnished with this material, so shock absorber part at first makes the speed/acceleration of mobile impeller reduce, and through vibration-absorptive material collision is weakened.Parallel connection of a plurality of acting in succession shock absorber part or advantageous particularly ground are connected in order.

According to one preferred embodiment; Stopper section and wheel hub constitute shock absorber part jointly and design like this; It is that stopper section and wheel hub constitute hydraulic pressure and/or compressed-air controlled piston-cylinder-unit or be connected at least indirectly on this piston-cylinder-unit; Wherein particularly piston be arranged in wheel hub, on the end face side of stopper section, and be designed on axial direction from the form of the annular arrangement convex shoulder of wheel hub protrusion.Cylinder has complementary recess; And constitute by the stopper section, thereby impeller is slowed down at the piston of piston-cylinder-unit and the damping medium between the cylinder through discharging in last subregion mobile route, before the stopper section when it moves axially on braking position or the non-braking position.Therefore with in the hydraulic brake, particularly the medium in its epitrochoidal chamber (air and/or working medium) is considered as the damping medium that is used for piston-cylinder-unit.

Advantageously, hydraulic brake is assigned the fill system that is used to fill epitrochoidal chamber, and wherein speed reduction gearing is integrated in the fill system, and the acceleration/accel that at least one can axially movable impeller slows down and utilizes working medium to fill epitrochoidal chamber through temporarily slowing down to realize.In that mobile impeller is filled epitrochoidal chamber by means of control apparatus lentamente when non-braking position is brought braking position into, this means that the little work medium arrives in the epitrochoidal chamber in each time quantum.Realize mobile impeller hydraulically and/or is pneumatically cushioned thus and through the flow process that in epitrochoidal chamber, in driven rotor, forms.Therefore in this case, the epitrochoidal chamber self that is made up of two impellers is used as shock absorber part.

Description of drawings

Should the present invention be described according to the embodiment that schematically shows in the accompanying drawings now,

Shown in the figure:

Fig. 1 a is design-calculated according to the present invention, has first embodiment of the drg of the rotor on its non-braking position, on the axial cross section of the rotating shaft of passing drg, observes;

Fig. 1 b is the drg among Fig. 1 a, and it has the rotor on its braking position;

Fig. 2 is second embodiment of the design-calculated drg according to the present invention, on the axial cross section of the rotating shaft of passing drg, this second embodiment is observed;

Fig. 3 is the 3rd embodiment of the design-calculated drg according to the present invention, on the axial cross section of the rotating shaft of passing drg, observes;

Fig. 4 is another embodiment of the design-calculated drg according to the present invention, observes passing on the axial cross section of rotating shaft, and this drg has and is used for piston-cylinder-unit that bump is cushioned.

The specific embodiment

Hydraulic brake with elementary impeller 1 and secondary impeller 2 has been shown in Fig. 1 a.Rotor that elementary impeller 1 is a drg and secondary impeller 2 are stators of drg.Two impellers 1,2 have the part of vane of being equipped with zone, and promptly rotor has subregion 1.1 and stator has subregion 2.1.

Stator, be that secondary impeller 2 can be by unshowned housings support, this housing for example surrounds elementary impeller 1 with stator together.The subregion that impeller is housed 1.1,2.1 of current two impellers 1,2 has constituted the planar epitrochoidal chamber 3 of annulus.

Impeller is supported in the subregion 1.1 of elementary impeller 1, and this subregion is current can move on the axial direction of hydraulic brake, as representing through double-head arrow.Realize that thus this axially-displaceable moves property, promptly elementary impeller 1 is placed on the axle 5 by means of wheel hub 7, and this wheel hub is current to have interior the gear teeth or negative thread, for example be steep screw thread, and axle has the outside thread of complementation.Axle 5 is fixed on the axial direction in the case; In contrast; Wheel hub 7 can move with elementary impeller 1; Therefore the rotation through axle 5 drives elementary impeller 1 can moved between its braking position and non-braking position on the axial direction with respect to axle 5, and and then elementary impeller 1 can carry out its desired function.

For the diagram that illustrates replacedly or additionally, secondary impeller 2 can certainly axially can be arranged movably.

Be provided with stopper section 6 for the mobile route that limits elementary impeller 1, its current design is annular arrangement and is locating to be connected with axle 5 towards the end of secondary impeller 2 antitorquely.Current stopper section 6 is fixed on the end of axle 5 end face side by means of screw 11.At this, stopper section 6 sees on cross-sectional plane and is designed to L shapedly that wherein its leg that on axial direction, extends can not be placed in the recess of the complementation of axle in 5 movably.(toward the leg of radial direction) of stopper section 6, towards the end face of axle 5 and axle 5, on axial direction, surround speed reduction gearing 4 with it in the face of the end face that is provided with.Speed reduction gearing is designed to spring 8 and is specifically designed to cup spring at this.Because wheel hub 7 is centering on axle 5 in the radial direction under present case, so wheel hub 7 can utilize its end face towards spring 8 when elementary impeller 1 is brought on the braking position, to be resisted against on the spring 8.

Therefore on the position shown in Fig. 1 a, elementary impeller 1 is away from secondary impeller 2 (non-braking position), and two impellers 1,2 are separated from each other through gap clearly, therefore do not carry out the power delivery from elementary impeller 1 to secondary impeller 2.This state is called light condition, and this is because 1 rotation of elementary impeller still is not braked owing to forming working medium stream.The space between elementary impeller 1 and the secondary impeller 2 or through elementary impeller and secondary impeller be equipped with part of vane zone 1.1 and 2.1 be positioned in the middle of endplay common that constitute, advantageously be emptied completely in the space that is called epitrochoidal chamber 3 under this state equally or except the working medium of being scheduled to surplus, be drained and correspondingly fill air.

Now in order to change in the running under braking rapidly as much as possible; The subregion 1.1 of elementary impeller 1 must switch to apace on the position shown in Fig. 1 b (braking position), thus epitrochoidal chamber 3 through elementary impeller, that part of vane zone 1.1 and secondary impeller are housed, part of vane zone 2.1 be housed constitute.

Be provided with unshowned control apparatus in addition, it is assigned to elementary impeller 1 and displacing force is applied on the elementary impeller at this, and therefore elementary impeller can be near secondary impeller 2.Can comprise at least one spring (not shown) to this control apparatus, arrange this spring like this, promptly the spring force of this spring corresponding to elementary impeller 1 near secondary impeller 2 and on total mobile route, work especially.Except spring 8, also be provided with this spring, wherein the spring force of this spring reacts on spring 8.Naturally also can consider, utilize other devices, for example electrical motor to realize the moving movement of control apparatus.Also possible is that control apparatus is applied to power on the elementary impeller 1 away from secondary impeller 2 corresponding to elementary impeller 1, and makes elementary impeller 1 near secondary impeller 2 through filling working medium for epitrochoidal chamber 3.

When non-braking position moves to braking position, confirm the zone beginning at elementary impeller 1 from of mobile route, wheel hub 7, be resisted against on the spring 8 towards the end face of spring 8, and wheel hub 7 slows down through spring force.When arriving braking position, cup spring utilizes stopper section and wheel hub 7 " locking " (Fig. 1 b).Since spring 8 only wheel hub 7 and and then in the last subregion mobile route of elementary impeller 1, before stopper section 6, work, therefore realize that through control apparatus the elementary impeller 1 that quickens is slowed down in the last subregion of mobile route.Thus, when being resisted against 6 last times of stopper section, wheel hub 7 suppressed the noise increase.

Alternative cup spring also can be considered other spring, particularly coil spring, its for example maybe and wheel hub 7 be disposed axially in concentrically between stopper section 6 and the wheel hub 7.

In order between two impellers, to carry out torque transfer working medium is filled in the epitrochoidal chamber 3; This working medium at first radially outward quickens through the blade (subregion 1.1) in the elementary impeller 1; And radially inwardly slow down through the blade (subregion 2.1) in the secondary impeller 2; Thereby regulated the working medium stream of torque transfer, referring to arrow 10.

Second embodiment according to drg of the present invention has been shown in Fig. 2.It is to a great extent corresponding at the embodiment shown in Fig. 1 a and the 1b, and different is not shown two impellers 1,2 and its subregion 1.1,2.1.Under present case, wheel hub 7 has convex shoulder 7.1 that on axial direction, protrude, annular arrangement at it on the end face of stopper section 6.Stopper section 6 has complementary annular arrangement recess 6.1, and convex shoulder 7.1 submerges in the last subregion of mobile route in this recess.At this, measure the size of convex shoulder 7.1 and recess 6.1 like this, promptly there is the gap in the surface that convex shoulder 7.1 and recess 6.1 face with each other.Therefore stopper section 6 constitutes piston-cylinder-unit 9 with wheel hub 7, thereby convex shoulder 7.1 and recess 6.1 are worked with cylinder 9.2 as the piston 9.1 of piston-cylinder-unit 9 respectively.

When elementary impeller 1 moves axially on braking position; The surplus of working medium that is contained in medium, the for example air in the cylinder 9.2 and/or comes from epitrochoidal chamber 3 is discharged through the gap that diminishes between piston 9.1 and cylinder 9.2 in the last subregion of mobile route, thus the medium of discharge is worked as the damping medium and therefore make wheel hub 7 (with so elementary impeller 1) in this zone, slow down at braking position.

Certainly can consider that replacedly piston-cylinder-unit is set to independent parts.

The 3rd embodiment of drg has been shown in Fig. 3.It is equally to a great extent corresponding to the embodiment among Fig. 2, yet in contrast, wheel hub 7 is as designing shown in Fig. 1 a and the 1b.Current, between stopper section 6 and wheel hub 7, be furnished with equally at the spring 8 shown in Fig. 1 a and the 1b, it is surrounding axle 5 in the radial direction.Additionally, between spring 8 and stopper section 6, in recess 6.1, inserted the shock absorber part of processing by vibration-absorptive material, for example polymer.Current this shock absorber part is designed to O shape ring 12.Therefore spring 8 is that O shape ring 12 is seen in order on force direction and is connected at this with vibration-absorptive material, at this, and its medi-spring 8 and O shape are encircled the longitudinal rigidity that 12 spring rigidity mutual superposition becomes two shock absorber parts.O shape ring 12 and spring 8 are the same only to work in last subregion, and the acceleration/accel of elementary impeller 1 is reduced.

Another embodiment that has piston-cylinder-unit 9 has been shown in Fig. 4.Piston 9.1 moves together with elementary impeller 1 and it is supported by wheel hub 7 in the illustrated embodiment; This piston is in the amount of this increase of moving to secondary impeller 2 with elementary impeller 1 and stretch into more in the cylinder 9.2, its on the one hand through secondary impeller 2 (stator) and on the other hand through elementary impeller 1, be that the wheel hub 7 of elementary impeller limits at this.Seal ring, particularly piston ring 14 are set for cylinder 9.2 is sealed, and it remains on the wheel hub 7 and along secondary impeller 2 at this and slides.

Spring 13 is as control apparatus, be used for making with respect to elementary impeller 1, or rather on total mobile route away from.For this reason in the illustrated embodiment, spring 13 is supported on the wheel hub 7 on the one hand and is supported on the other hand on the convex shoulder of axle 5.Replacedly, spring also possibly be supported on the secondary impeller 2.Axle 5 supports elementary impeller 1.

In Fig. 4, be provided with and fill pipeline 15, fill pipeline through this and fill working medium for cylinder 9.2.Advantageously, be arranged in this filling pipeline 15 for single hole or porous form like this, the inlet of promptly filling pipeline 15 is opposite with the stream of the working medium in the epitrochoidal chamber 3 to be provided with.Therefore cylinder 9.2 also or is filled in light condition when filling working medium for epitrochoidal chamber 3, and epitrochoidal chamber 3 has only been filled the working medium of surplus in light condition.If present elementary impeller 1 moves or especially by means of moving in this unshowned screw thread rotation to secondary impeller 2; Then the working medium in cylinder 9.2 through at this be the gap 16 of circular clearance form between the wall of piston 9.1 and cylinder 9.2 by cylinder 9.2 in discharge, referring to small arrow.Gap 16 also possibly seal by means of the sealing member that can realize suitable amount of leakage, and wherein sealing member for example is installed on the piston 9.1 and slides along the wall of cylinder 9.2.

In the embodiment shown in this external Fig. 4, fill pipeline 15 and locate with the mode that passes to like this in the cylinder 9.2, promptly elementary impeller 1 and and then piston 9.1 when beginning to move, working medium is also discharged through filling pipeline 15 by cylinder 9.2.On the contrary, if elementary impeller 1 further continues to move with respect to secondary impeller 2, then piston 9.1 has covered and has filled the inlet of pipeline 15 in cylinder 9.2, thereby working medium only can be discharged through gap 16 by cylinder 9.2.Correspondingly, piston 9.1 is submerged in the cylinder 9.2 relatively more shallowly, and thisly submerge the mobile route that increases with elementary impeller 1 and suppressed more significantly.

The filling pipeline 15 that illustrates correspondingly has double effects: it can be filled into working medium in the cylinder 9.2 reliably on the one hand, so that realize desired damping effect fully.If during piston 9.1 submerges cylinder 9.2 on the other hand, then fill pipeline and be used at initial emptying cylinder 9.2.

The moving velocity of elementary impeller 1 is big more, and counteractive power is just big more, and this power forms through working medium is discharged from cylinder 9.2.

Be contemplated that in addition embodiment illustrated in the accompanying drawings can be bonded to each other.

Certainly also possible is that illustrated shock absorber part also is arranged in the zone of unshowned non-braking position, so that when introducing drg in the light condition, equally elementary impeller 1 is cushioned.

REFERENCE NUMBER LIST

1 elementary impeller

1.1 subregion

2 level impellers

2.1 subregion

3 epitrochoidal chambers

4 speed reduction gearings

5

6 stopper sections

6.1 recess

7 wheel hubs

7.1 convex shoulder

8 springs

9 piston-cylinders-unit

9.1 piston

9.2 cylinder

10 arrows

11 screws

12 O shapes ring

13 springs

14 piston rings

15 fill pipeline

16 gaps

Claims (11)

1. hydraulic brake,
1.1 have elementary impeller (1) that blade is housed and the secondary impeller (2) that blade is housed, said impeller constitutes the epitrochoidal chamber (3) that can fill working medium each other;
1.2 two said impellers (1; What at least one 2) can be utilized said at least impeller is equipped with part of vane zone (1.1; 2.1) move axially like this with respect to another said impeller (1,2), promptly said impeller can switch between braking position and non-braking position; At the above paddle shaft of said braking position to being adjacent in the face of another said impeller (1; 2) arrange, arrange to arrive the bigger axial spacing of another said impeller (1,2) with respect to said braking position at the above impeller of said non-braking position;
1.3 two said impellers (1; 2) at least one in is assigned a control apparatus, and said control apparatus applies displacing force to said mobile impeller (1,2); Thereby make the said impeller can be near another said impeller (1,2) and/or can be away from another said impeller;
1.4 have the stopper section (6) of the mobile route that is used to limit said mobile impeller (1,2);
It is characterized in that:
1.5 have speed reduction gearing (4), be used for when said impeller (1,2) moves axially said braking position and/or non-braking position, the bump of said impeller (1,2) on said stopper section (6) cushioned; Wherein
1.6 design said speed reduction gearing (4) like this; Be that the power that said speed reduction gearing will react on said displacing force is applied to said mobile impeller (1; 2) on, and said speed reduction gearing (4) only said mobile route, in said stopper section (6) last subregion before, work.
2. hydraulic brake according to claim 1; It is characterized in that; In two said impellers (1,2) at least one settled with respect to said axle (5) between said braking position and non-braking position on the axial direction in order to realize said impeller on axle (5), to carry out longitudinal travel movingly; And
2.2 said stopper section (6) and said axle (5) design, thereby said impeller (1,2) is being resisted against on said braking position or the non-braking position on the said stopper section (6) antitorquely.
3. hydraulic brake according to claim 1 and 2; It is characterized in that said mobile impeller (1,2) axially is placed on the said axle (5) by means of wheel hub (7) movingly; Wherein said axle (5) has outside thread, particularly steep screw thread and said wheel hub (7) has complementary negative thread; Thereby said impeller (1,2) can be moved on axial direction with respect to said axle (5) through the rotation driving (5) or said impeller (1,2) of said axle; Wherein
3.1 said wheel hub (7) utilize said wheel hub, the end face towards said stopper section (6) is being resisted against on said braking position and/or the non-braking position on the said stopper section (6).
4. according to each described hydraulic brake in the claim 1 to 3; It is characterized in that; Said speed reduction gearing (4) comprises at least one electricity, machinery, hydraulic pressure and/or compressed-air controlled shock absorber part; And said shock absorber part is positioned on axial direction between said impeller (1,2), particularly said wheel hub (7) and said stopper section (6), and particularly is fixed on the said stopper section (6).
5. hydraulic brake according to claim 4 is characterized in that, in said stopper section (6) and/or two the said impellers (1,2) any, particularly said wheel hub (7) constitutes said shock absorber part, perhaps be connected at least indirectly on the said shock absorber part.
6. according to claim 4 or 5 described hydraulic brakes; It is characterized in that; Said shock absorber part is designed to elastic element, particularly like the spring (8) of cup spring; Perhaps be designed to comprise the spring leaf group of a plurality of springs (8), and the spring rigidity of said spring/a plurality of springs (8) has the tendency of progression.
7. according to each described hydraulic brake in the claim 4 to 6, it is characterized in that said shock absorber part is processed by vibration-absorptive material, particularly polymer at least in part, perhaps be coated with said vibration-absorptive material.
8. according to each described hydraulic brake in the claim 1 to 7; It is characterized in that; That said speed reduction gearing (4) comprises hydraulic pressure and/or compressed-air controlled piston-cylinder-unit (9); The piston of said piston-cylinder-unit (9.1) through said movably impeller (1,2) near and move in the said cylinder (9.2) and discharge the damping medium between said piston (9.1) and said cylinder (9.2), particularly be accompanied by the increase of restriction effect of the said damping medium of discharge.
9. according to each described hydraulic brake in the claim 1 to 8; It is characterized in that said stopper section (6) and said mobile impeller (1,2); Particularly the said wheel hub (7) by means of said impeller constitutes said shock absorber part jointly; And that design like this, promptly said stopper section and said mobile impeller constitute hydraulic pressure and/or compressed-air controlled piston-cylinder-unit (9) perhaps are connected on said piston-cylinder-unit at least indirectly; Wherein especially
9.1 said piston (9.1) is arranged in said mobile impeller (1; 2) towards on the end face of said stopper section (6), particularly on the said wheel hub (7) of said mobile impeller; And be designed on axial direction from the annular arrangement convex shoulder (7.1) of said wheel hub (7) protrusion of said mobile impeller (1,2), particularly said mobile impeller; With
9.2 said cylinder (9.2) has complementary recess; And constitute by said stopper section (6); Thereby make said impeller (1,2) when said paddle shaft is on moving to said braking position or non-braking position said mobile route, in said stopper section (6) last subregion before, slow down at the said piston (9.1) of said piston-cylinder-unit (9) and the said damping medium between the said cylinder (9.2) through discharging.
10. according to each described hydraulic brake in the claim 1 to 9; It is characterized in that; Said hydraulic brake is assigned the fill system that is used to fill said epitrochoidal chamber (3); Said speed reduction gearing (4) is integrated in the said fill system, and utilizes said working medium to fill said epitrochoidal chamber (3) through temporarily slowing down and realize the buffering to the bump of said impeller (1,2).
11. according to each described hydraulic brake in the claim 1 to 10; It is characterized in that; Said control apparatus comprises at least one spring (13); Said spring designs like this, promptly the spring force of said spring corresponding to said mobile impeller (1,2) on total mobile route near and/or away from working.
CN201110268250XA 2010-09-24 2011-09-09 Hydrodynamic retarder CN102431529A (en)

Priority Applications (4)

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DE102010046374 2010-09-24
DE102010046374.4 2010-09-24
DE102010049704 2010-10-28
DE102010049704.5 2010-10-28

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106090073A (en) * 2015-04-29 2016-11-09 Zf腓德烈斯哈芬股份公司 Hydraulic retarder

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3284543A1 (en) * 2016-08-17 2018-02-21 Nelson Irrigation Corporation Viscous rotational speed control device with fluid circuit
US9995352B2 (en) * 2015-01-14 2018-06-12 Nelson Irrigation Corporation Viscous rotational speed control device
US9657790B2 (en) 2015-01-14 2017-05-23 Nelson Irrigation Corporation Viscous rotational speed control device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3467225A (en) * 1967-01-18 1969-09-16 Teves Gmbh Alfred Hydrodynamic brake with axially shiftable stator
EP0507745A2 (en) * 1991-03-13 1992-10-07 IVECO FIAT S.p.A. A control system for a hydraulic retarder for commercial vehicles and a vehicle with the system
WO2000052352A1 (en) * 1999-03-03 2000-09-08 Voith Turbo Gmbh & Co. Kg Hydrodynamic retarder with axially sliding rotor and restoring mechanism
CN1650118A (en) * 2002-05-02 2005-08-03 沃伊思特博两合公司 Hydrodynamic brake

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2359930A (en) 1941-04-14 1944-10-10 Hydraulic Brake Co Fluid coupling

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3467225A (en) * 1967-01-18 1969-09-16 Teves Gmbh Alfred Hydrodynamic brake with axially shiftable stator
EP0507745A2 (en) * 1991-03-13 1992-10-07 IVECO FIAT S.p.A. A control system for a hydraulic retarder for commercial vehicles and a vehicle with the system
WO2000052352A1 (en) * 1999-03-03 2000-09-08 Voith Turbo Gmbh & Co. Kg Hydrodynamic retarder with axially sliding rotor and restoring mechanism
CN1650118A (en) * 2002-05-02 2005-08-03 沃伊思特博两合公司 Hydrodynamic brake

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106090073A (en) * 2015-04-29 2016-11-09 Zf腓德烈斯哈芬股份公司 Hydraulic retarder
CN106090073B (en) * 2015-04-29 2019-08-06 Zf腓德烈斯哈芬股份公司 Hydraulic retarder

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KR20120031438A (en) 2012-04-03

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