CN105593081B - hydraulic system for hydraulic machine - Google Patents
hydraulic system for hydraulic machine Download PDFInfo
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- CN105593081B CN105593081B CN201480053992.2A CN201480053992A CN105593081B CN 105593081 B CN105593081 B CN 105593081B CN 201480053992 A CN201480053992 A CN 201480053992A CN 105593081 B CN105593081 B CN 105593081B
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- 230000015654 memory Effects 0.000 claims abstract description 13
- 230000001105 regulatory effect Effects 0.000 claims description 7
- 238000005259 measurement Methods 0.000 claims description 4
- 230000007717 exclusion Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 description 9
- 230000001133 acceleration Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Abstract
The present invention relates to a kind of hydraulic machines for generating braking moment, especially Retarder, it includes the first impeller, especially rotor (1), and the second impeller being disposed concentrically upon with it, especially stator (2), the working chamber (4) of toroid is collectively formed in they, the hydraulic machine carries hydraulic system, the hydraulic system, which has, controls and adjusts unit (22), pump, heat exchanger, valve, working media memory (10) and line system, wherein, the volume flow circulation that working media passes through line system and working chamber can be generated by pump.According to the present invention, it is suggested that, control/adjust braking power or braking moment by pressure-regulating valve.
Description
Technical field
The present invention relates to a kind of hydraulic machines generating braking moment by fluid, especially Retarder.
Background technology
Hydraulic machine or Retarder generally include shell, are disposed with the first impeller, especially rotor wherein, with
And concentric with it the second impeller arranged, especially stator, they together form the working chamber of toroid and they are surrounded
Common pivot center in groups.
Either hydraulic brake can be arranged in motor-side or transmission device side to retarder in power train.Use workflow
Body, such as oil or the degree decision " rotor-braking moment " that retarder is filled with or without the water of additive.It is slow in operation
When fast device, such as send oil pump in working chamber.In running under braking, rotor driven makes oily acceleration, and in working chamber
Overall diameter at oil handed into stator.Make oily deceleration there, and is returned in rotor via the interior diameter of working chamber.It is logical
The interaction crossed between commonly known rotor and stator generates braking moment.
It is caused by hydraulic system：Under non-brake operation and/or under running under braking, with corresponding working media volume come
Supply or filling working chamber.It is with particular meaning herein：By working media generating under two kinds of methods of operation
Heat is drawn from working chamber and is delivered to for carrying out cooling cooling circuit in cooler.Especially needed in non-brake operation
It guides minimum volume and passes through working chamber, to cool down retarder under non-operating state.
Working chamber couples via fluid entrance and fluid discharge unit with operating fluid loop, and the operating fluid loop is basic
On by working fluid memory, cooler, pump and multiple valve groups at.Control and the such phase of component for adjusting unit and hydraulic system
Even, that is, braking moment and/or working media stream can be controlled or regulated.
Such hydraulic system is for example as known to 10 2,006 030 791 A1 of document DE.The hydraulic system essentially relates to：
Working media is guided under all methods of operation by cooler, to realize that ideal temperature is adjusted.Wherein, working media is
Oil, simultaneously for the lubrication of transmission device.It is provided that adjust volume flow：The pump of hydraulic system is adjusted.
Invention content
Task of the invention lies in, it is proposed that a kind of improved hydraulic system for hydraulic machine.Purpose particularly in,
Electro-hydraulic system is improved in terms of the adjustability of braking power.
Task according to the present invention is solved by following for generating the hydraulic machine of braking moment, the fluid power
Machinery includes the first impeller, and the second impeller being disposed concentrically upon with it, and first impeller and second impeller are common
Formed toroid working chamber, the hydraulic machine also carry hydraulic system, the hydraulic system have control and adjust unit,
Pump, heat exchanger, valve, working media memory and line system, wherein can generate working media by the pump and pass through
The volume flow circulation of the line system and the working chamber, wherein the valve is pressure-regulating valve, is adjusted by the pressure
Valve can control/adjust braking power or braking moment, wherein the pressure-regulating valve is controlled by pressure difference regulating device
System/adjusting.
The present invention includes hydraulic machine or retarder, especially Retarder comprising the first impeller especially turns
Son, and the second impeller for being disposed concentrically upon with it, especially stator, they together form the working chamber of toroid.In addition
The hydraulic machine has electro-hydraulic system, which, which has, controls and adjust unit, pump, heat exchanger, valve, work
Make medium storage and line system, wherein can generate the body that working media passes through line system and working chamber by pump
Product stream circulation.Electro-hydraulic system is characterized in that valve is pressure-regulating valve, by its can control/adjust braking power or
Person's braking moment.
By using pressure-regulating valve, can in an advantageous manner with torque or braking moment proportionally regulating system
Pressure.Here, pressure-regulating valve can be 3/3 reversal valve or 3/2 reversal valve.
In addition, including pressure difference regulating device for controlling/adjusting the electro-hydraulic system of pressure-regulating valve.In the present invention
In the sense that, which includes at least one proportioning valve and control and adjusting unit.
In addition, the sensor for torque measurement is coupled with controlling and adjusting unit, to use torque measurement
Value carries out pressure difference adjusting.
In addition, pump is linked into hydraulic systems as follows, that is, pump can switch in two kinds of operating statuses,
First operating status, i.e., non-brake operation and the second operating status, i.e. running under braking, wherein the line system is designed to
So that can carry out volume pumped stream circulation by pump under two kinds of operating statuses passes through working chamber.
By with switching valve it is combined using pump to ensure under all operating conditions to working chamber supply work be situated between
Matter can reduce the complexity of line system or hydraulic system.The flowed friction being thus reduced, and in system safety
Advantage in terms of property, maintenance and economy.
Pump can be coupled with rotor or (drehfest) is connected in anti-relative rotation gerotor pump (Gerotor-
pumpe)。
In addition, in the first embodiment, for switchover operation state, switching valve is arranged in the exclusion side of pump, wherein other
Logical circuit setting around valve opening with pump for returning in working medium container.It carries out in this arrangement：It is special in the exclusion side of pump
It is that basic adjusting carries out working media volume by the hydraulic pressure or line system of postposition.Non-essential working media valve it
It is preceding and/or be introduced back into later in working media memory.
In this second embodiment, for switchover operation state, switching valve is arranged in the suction side of pump, wherein in the reality
It applies in mode, bypass line is arranged for around valve opening, working media can be taken by pumping across the bypass line.
In order in this embodiment by working media or partial volume stream in the first operating status i.e. non-brake fortune
It is pumped into working chamber in row, is provided with the second bypass line.Working media filter can be set wherein.
In addition in this embodiment, proportioning valve can advantageously after working media filter with bypass line coupling
Connection, by the proportional valve control/adjusting pressure-regulating valve.There are two advantages for this tool.On the one hand it only needs to a small amount of working media
It is filtered, the cost for " filtering " function is thus greatly decreased.In addition, proportioning valve is due to being coupled with bypass line and always
Preparation operating status is remained, this is because being applied with certain working medium pressure always.
The other feature and Ben Fa of equipment according to the present invention with reference to attached drawing are obtained by the following explanation of preferred embodiment
Bright other advantages.
Description of the drawings
In the following, by attached drawing, the present invention is furture elucidated.In attached drawing：
Fig. 1 shows in cross section retarder,
Fig. 2 shows the first embodiment of the structure of hydraulic system,
Fig. 3 shows the second embodiment of the structure of hydraulic system.
Specific implementation mode
Fig. 1 illustratively shows in cross section retarder, especially in bus and commercial car.
Retarder includes：Shell, rotor 1 and the stator 2 being made of multiple housing parts, they form toroid each other
Annular chamber working chamber 4 in other words.
Retarder working fluid, the especially oil are run, which pumps by pump 11 via line system
Into input channel 6 in other words helical duct.Oil passes through separation seam 3 to arrive in working chamber 4 from input channel 6.In running under braking
Period forms in working chamber 4 and circulates.Driven rotor 1 makes oily acceleration, and oil is handed at overall diameter
Stator.Here, oil is encountered static stator vane and is decelerated.Oil flows to rotor 2 again at interior diameter.The system generated
Energy is converted primarily into heat, to need constantly to be cooled down to a part for oil by heat exchanger 19.Via fluid
Output section in other words output channel 7 by this part of oil from circulating middle export.The oil being exported is then across heat exchange
It device 19 and is pumped back into working chamber 4 then according to depending on operating status, is circulated to generate.In non-brake fortune
Under row state, oil is pumped back into working media memory 10.
Fig. 2 shows the first embodiments of the structure of hydraulic system.One of essential characteristics of the embodiment are：Pump 11
It is arranged in before valve 9.The valve is in non-brake running position herein.As long as driving the pump, oil will be from working media memory
In be pumped into bypass line 27,28 via valve.Throttle valve 14 is enclosed in bypass line 27, may be adjusted so that one
Fraction working media is pumped into working chamber 4.Volume flow is selected as following size, that is, ensures fully to draw from working chamber
Go out heat.In addition, the volume flow does not allow greatly to the idle resistance for generating raising.Oil passes through heat exchanger 19 from working chamber 4
In ground pumped back working media memory 10.Thus, it is cooled down always by heat exchanger 19 under non-brake operation a small amount of
Oil.
The guiding of second bypass line 28 remaining, the volume flow of substantially bigger be returned directly to working media memory 10
In.Pump 11 thus almost with free-runing operation, it is possible thereby to the minimization of loss under non-brake operation, without being adjusted to pump
Section.The gerotor pump directly driven by armature spindle may be used herein as pump.
For running under braking (position is not shown), valve 9,16 and 20 is switched over.As long as switched arrangement is in pump 11
Squeeze the switching valve 9 of side, working media will be arrived at via working line 30,31 and valve 16 in working chamber 4.
Valve 16 is pressure compensator, the pressure by being measured in working chamber 4 and previously given by proportioning valve 21
Pressure switches to corresponding switching position.Pressure compensator is differential valve or pressure-regulating valve, can be adjusted external defeated
The pressure difference of the measurement position sent and the pressure applied on valve.Valve 16 may be embodied as 3/3 reversal valve (just as shown herein)
Or 2/3 reversal valve.By pressure compensator, work can be proportionally adjusted with the desired braking moment on armature spindle
Make the system pressure in chamber 4.Torque sensor can be for example set on armature spindle thus.Only when switching to application position
When, just in the handover to 21 feed system pressure of proportioning valve.In order to protect proportioning valve 21 to be provided with filter 13, to all right
Necessary working media is filtered for running under braking.
By being formed in the closed circuit between working chamber 4 and cooler 19 to the switching of valve 20, wherein pressed by adjusting
Force compensating device carrys out regulating system pressure.
Fig. 3 shows the second embodiment of the structure of hydraulic system.It is substantially different from the first embodiment, wherein
In this embodiment, the working media of certain volume also is pumped into working chamber 4 by pump 11 in non-brake operation.
In the structure, valve 9 is arranged in the suction side of pump 11.
Under non-brake operation, by pump 11 via the bypass line 26 to throttle by suction throttle valve 17 from working media
Working media is constantly drawn in memory 10, and is pumped into working chamber 4 via bypass line 27.Here, bypass line
27 terminate at as follows in input channel 6, that is, working media is pumped into output channel 7 essentially through 4 ground of working chamber
In.
In bypass line 27, another throttle valve 14 is installed, and before the throttle valve, for adjusting by valve 25
The proportioning valve 21 of pressure compensator be connected on bypass line 27.It is ensured that being applied with foot always at proportioning valve 21
Enough system pressures, and thus realize quick, the no-delay adjusting to braking effect.In addition, filter 13, especially
Fine filter is mounted in bypass line 27 before proportioning valve 21, thus only to being used for non-brake operation and for driving
Relatively small volume needed for control proportioning valve 21 is filtered.
For running under braking (its position is not shown), valve 9,20 and 25 is switched over.Oil is via working line 30,31 and
Valve 25 arrives at working chamber 4.Valve 25 is pressure compensator, in advance according to the pressure measured in working chamber 4 and by proportioning valve 21
Given pressure is switched to corresponding switching position.Valve 25 may be embodied as 2/3 reversal valve (as described herein) or also implement
For 3/3 reversal valve.By pressure compensator, can on armature spindle desired braking moment proportionally adjust working chamber
System pressure in 4.For this purpose, torque sensor can for example be arranged on armature spindle.
It is set as pumping with the gerotor pump 11 that armature spindle is connected in anti-relative rotation.It is ensured that in both embodiments,
Pump resistance is very small under non-brake operation and is acted on being supported braking under running under braking.
Usually it is also noted that filter shown in figure, the circuit being back in working media memory 10 and
Although the throttle valve or check-valves installed in circuit are necessary for entire function, but by those skilled in the art
It applies by the numbers.
Reference numerals list
1 rotor
2 stators
3 separation seams
4 working chambers
5 pivot centers
6 input channels
7 output channels
8 electro-hydraulic systems
9 valves
10 working media memories
11 pumps
12 excess pressure valves
13a/b oil screens/filter
14 throttle valves
15 check-valves
16 pressure difference limen, 3/3 reversal valve
17 suction throttle valves
18 excess pressure valves
19 heat exchangers
20 switching valves
21 proportioning valves
22 controls and adjusting unit
23 control circuits
24 control circuits
25 pressure difference limens
26-29 bypass lines
30-31 working lines
32 arrive the circuit of cooler
Claims (13)
1. a kind of hydraulic machine for generating braking moment, the hydraulic machine includes the first impeller, and concentrically with it
The working chamber (4) of toroid, the hydraulic machine is collectively formed in second impeller of arrangement, first impeller and second impeller
Tool also carry hydraulic system, the hydraulic system have control and adjust unit (22), pump (11), heat exchanger, valve (16,
25), working media memory (10) and line system, wherein working media can be generated by the pump (11) and pass through institute
The volume flow circulation of line system and the working chamber is stated,
It is characterized in that,
The valve (16,25) is pressure-regulating valve, and braking power or brake force can be controlled/adjust by the pressure-regulating valve
Square, wherein the pressure-regulating valve is controlled/adjusted by pressure difference regulating device, and the pressure difference regulating device includes extremely
A few proportioning valve (21) and the control and adjusting unit (22), wherein the pressure-regulating valve passes through in the work
The pressure that is measured in chamber (4) and corresponding switching position is switched to by the previously given pressure of the proportioning valve (21).
2. hydraulic machine according to claim 1,
It is characterized in that,
The pressure-regulating valve is 3/3 reversal valve (16) or 3/2 reversal valve (25).
3. hydraulic machine according to claim 1 or 2,
It is characterized in that,
The hydraulic machine is Retarder.
4. hydraulic machine according to claim 3,
It is characterized in that,
Sensor for torque measurement is coupled with the control and adjusting unit (22), and measured torque is used for
Pressure difference is adjusted.
5. hydraulic machine according to claim 1 or 2,
It is characterized in that,
The pump (11) is linked into hydraulic systems as follows, that is, the pump (11) can in two kinds of operating statuses into
Row switching, the first operating status i.e. non-brake operation and the second operating status i.e. running under braking, wherein described
Described in line system is designed so that under two kinds of operating statuses, can carry out volume pumped stream circulation by the pump (11) passes through
Working chamber (4).
6. hydraulic machine according to claim 1,
It is characterized in that,
First impeller is rotor (1) and the pump (11) is the gerotor pump coupled with the rotor (1).
7. hydraulic machine according to claim 1 or 2,
It is characterized in that,
For switchover operation state, it is disposed with valve (9) in the exclusion side of the pump (11), and third bypass line (28) setting is used
It is returned in the working media memory (10) in getting around the valve and the pump (11).
8. hydraulic machine according to claim 1 or 2,
It is characterized in that,
For switchover operation state, it is disposed with valve (9) in the suction side of the pump (11), and the first bypass line (26) setting is used
In the bypass valve (9).
9. hydraulic machine according to claim 1 or 2,
It is characterized in that,
It is provided with the second bypass line (27), it can be in the first operating status i.e. non-brake by second bypass line
Partial volume stream is pumped into the working chamber (4) under operation.
10. hydraulic machine according to claim 9,
It is characterized in that,
It is provided with working media filter (13) in second bypass line (27).
11. hydraulic machine according to claim 10,
It is characterized in that,
By proportioning valve (21) control/adjusting pressure-regulating valve (25), the proportioning valve is in the working media filter
(13) it is coupled with second bypass line (27) after.
12. hydraulic machine according to claim 1 or 2,
It is characterized in that,
First impeller is rotor (1).
13. hydraulic machine according to claim 1 or 2,
It is characterized in that,
Second impeller is stator (2).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013219792.6 | 2013-09-30 | ||
| DE201310219792 DE102013219792A1 (en) | 2013-09-30 | 2013-09-30 | Hydraulic system for a hydrodynamic machine |
| PCT/EP2014/070590 WO2015044328A2 (en) | 2013-09-30 | 2014-09-26 | Hydraulic system for a hydrodynamic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105593081A CN105593081A (en) | 2016-05-18 |
| CN105593081B true CN105593081B (en) | 2018-08-31 |
Family
ID=
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2496497A (en) * | 1946-08-16 | 1950-02-07 | Robert C Russell | Brake |
| US6817455B1 (en) * | 1999-10-27 | 2004-11-16 | Zf Friedrichshafen Ag | Retarder system |
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2496497A (en) * | 1946-08-16 | 1950-02-07 | Robert C Russell | Brake |
| US6817455B1 (en) * | 1999-10-27 | 2004-11-16 | Zf Friedrichshafen Ag | Retarder system |
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| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180831 |