CN105605024A - Hydraulic machine, in particular a hydraulic pressure exchanger - Google Patents
Hydraulic machine, in particular a hydraulic pressure exchanger Download PDFInfo
- Publication number
- CN105605024A CN105605024A CN201510784206.2A CN201510784206A CN105605024A CN 105605024 A CN105605024 A CN 105605024A CN 201510784206 A CN201510784206 A CN 201510784206A CN 105605024 A CN105605024 A CN 105605024A
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- Prior art keywords
- cylinder
- piston
- opening
- hydraulic machine
- brake chamber
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1404—Characterised by the construction of the motor unit of the straight-cylinder type in clusters, e.g. multiple cylinders in one block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
- F04B9/1172—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions being obtained by a double-acting piston liquid motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F13/00—Pressure exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1409—Characterised by the construction of the motor unit of the straight-cylinder type with two or more independently movable working pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/008—Reduction of noise or vibration
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Hydraulic Motors (AREA)
- Actuator (AREA)
- Reciprocating Pumps (AREA)
Abstract
A hydraulic machine, in particular hydraulic pressure exchanger, is provided comprising a drum having a first end face and a second end face and being rotatable about an axis, said drum comprising at least a cylinder (4), a piston (15) being arranged in said cylinder (4), said piston (15) being moveable in a first moving direction and in a second moving direction opposite to said first moving direction, said piston dividing said cylinder in a first section opening in said first end face and a second section opening in said second end face. Such hydraulic pressure exchanger should be operated with a low noise. To this end braking means are provided for at least of said moving directions, said braking means braking said piston (15) before reaching an end stop.
Description
Technical field
The present invention relates to a kind of machine, especially hydraulic exchanger, this hydraulic exchanger comprises cylinder, this cylinder hasOne end face and the second end face, and can rotate around axis, described cylinder comprise at least one cylinder and be arranged on described inPiston in cylinder, described piston can move on the first moving direction and on the second moving direction contrary with the first moving directionMoving, described piston is divided into described cylinder at the Part I of described the first end face split shed with at described the second end face split shedPart II.
Background technology
Known this kind of hydraulic exchanger from EP1508361A1.
The pressure exchanger of this type can be used in counter-infiltration system. In this kind of system, liquid is pumped into filmIn unit. A part in liquid is through this film. The remainder of liquid must be dropped. But pressure exchanger can be byBe used for the high pressure of this part of recovering fluid. For this reason, hydraulic exchanger comprises the first front plate unit of the first end of cylinderThe second front plate unit with the second end of cylinder. The first front plate unit has high voltage supply mouth and low-voltage return is answered back. SecondFront plate unit comprises high pressure return port and low pressure supply port.
The operation of this kind of pressure exchanger can be summarized as follows simply: in cylinder, be filled with highly pressurised liquid, wherein cylinderThrough the first kidney type opening that is connected to high voltage supply mouth in the first front plate unit. The piston being arranged in this cylinder passes through streamThe liquid entering is moved facing to the direction of the second end face at the first end from cylinder. Before the Part II of cylinder, filled outBe filled with the fresh liquid from low pressure supply port. This fresh liquid is output to the second front plate unit via high pressure return port. WhenWhen cylinder is rotated further, cylinder passes another kidney type opening that is connected to low pressure supply port in the second front plate unit, thereby shouldCylinder is filled with fresh liquid. This fresh liquid promotes this piston in the direction of the first end face towards cylinder and output is treatedThe liquid being dropped.
Fresh liquid can be by amount that hydraulic exchanger pressurizeed according to other including the velocity of rotation of cylinderFactor. Cylinder rotates sooner, and more fluid can be pressurized. But the velocity of rotation of increase has caused the corresponding of noiseIncrease.
Summary of the invention
The object of the invention is to make noise to keep lowlyer.
This object realizes by following brake apparatus, and described brake apparatus is set to for described moving directionAt least one, described brake apparatus was braked described piston before described piston arrives end stop.
A part that has been found that noise is caused in the time that this piston stroke finishes by the piston in cylinder. When the rotation speed of cylinderDegree increases, and the linear speed of piston must also be increased. But, there is the piston of fair speed in the time that it clashes into end stopProduce sizable noise. This brake apparatus reduces noise significantly, because before piston arrives end stop, pistonSpeed is reduced by described brake apparatus. In the time of piston arrives end stop, the speed of piston is lower, and noise is less.
In a preferred embodiment, described brake apparatus is hydraulic brake system. Because pressure exchanger utilizes liquidOperation, so this liquid can be used to brake this piston before piston arrives end stop, thereby reduces noise.
Preferably, brake apparatus is set at least one for described moving direction, and described brake chamber has outMouthful, described opening is opened during a part for the movement of described piston, and in end stop described in described piston arrivesPreset distance place before part is closed, and the brake chamber of described closure has throttling outlet. The movement of this piston can be dividedFor Part I, in this Part I, there is not hydraulic braking. In this mobile part, thereby being opened, permits brake chamberThe liquid of being permitted in brake chamber overflows not by throttling in the situation that. In mobile Part II, brake chamber is closed, thus liquidBody can only overflow from brake chamber via throttling outlet. It is in braking side that drive fluid exports needed power by throttlingUpwards act on the power on piston. The kinetic energy of piston is converted into heat energy. But this is not problem, because this heat energy passes through liquidBody is passed away.
Preferably, described throttling outlet comprises hole. Described hole can be prescribed the braking effect that has been of a size of expectation. ThisOutward, preferably, described throttling outlet comprises valve, especially check-valves. This kind of valve can be used to limit fluid and export from throttlingIn flow through. This kind of restriction can be directionality restriction, in the case, uses check-valves.
In another preferred embodiment, described throttling outlet comprises leakage paths. This kind of leakage paths can be formed in workBetween plug and a part for cylinder.
Preferably, at the period of contact of described brake chamber, described piston reduces described opening gradually. Brake apparatus is automatic controlSystem. The restriction characteristic of the mobile flow resistance that increases throttling outlet of piston.
Preferably, described brake chamber is arranged between described piston and the wall of described cylinder. Do not need extra parts withForm the border of described brake chamber.
In a preferred embodiment, the first brake chamber is set to for described the first moving direction, the first brake chamber toolHave the first opening and first throttle outlet, and the second brake chamber is set to for described the second moving direction, described secondBrake chamber has the second opening and second section flow export, and described first throttle outlet and described second section flow export are spaced.Two throttlings outlet can not form short circuit, thereby two brake apparatus can be independent of each other and operated.
In a preferred embodiment, described the first opening is arranged in the described wall of described cylinder. In the case, brakingThe inside that liquid in chamber is moved to the inside of cylinder or holds the housing of cylinder.
In the case, preferably, described first throttle outlet is arranged in the described wall of described cylinder. In principle, existIt is enough in the wall of cylinder, having two holes, has predetermined distance and have different diameters between described multiple holes. ?Macropore is the opening of the first brake chamber, is throttling outlet compared with aperture.
In addition, preferably, sleeve is arranged in described cylinder to reduce the internal diameter of described cylinder, institute on described first directionState piston and comprise the protuberance being inserted in described sleeve, described the first brake chamber by described piston, described sleeve and described inThe described wall of cylinder defines. In this embodiment, two of piston front surfaces have the surface area of different size. Due to surface areaThe difference of size, the fluid in the second chamber can be pressurized to the pressure larger than the pressure in the first chamber. In addition can realize,The simple structure of machine.
Preferably, described the second opening is the opening in the second end face of described cylinder. This makes the simple structure of machine.
In the case, preferably, described second section flow export extends through described piston. Brake chamber is logical via extendingCross the path of piston and be connected to the opening in the second end face of cylinder.
In the case, preferably, described second section flow export leads to the low-pressure side of described cylinder. In the case, do not haveAct on the pressure in outlet via throttling opening.
Preferably, described the second outlet has the area of section less than the area of section of described cylinder, and described piston hasProtuberance, before end stop described in described piston arrives, described protuberance enters described in described the second outlet predeterminedDistance. In the case, in the time that protuberance enters into the second outlet, the second opening is closed by piston self.
In the case, preferably, described protuberance comprises tapered end at least a portion of its circumference. This taperEnd has the effect that the second opening is not closed suddenly, but during the protuberance of piston moves in described the second openingBy little by little closed. This is the other element for reducing noise.
Brief description of the drawings
Below with reference to accompanying drawing, preferred exemplary of the present invention is described in further detail, wherein:
Fig. 1 is the schematic diagram of hydraulic exchanger;
Fig. 2 is the amplification view of cylinder;
Fig. 3 is the part III detail view of Fig. 2;
Fig. 4 is the stereogram of the cylinder of Fig. 2;
Fig. 5 is the cutaway view of cylinder, and it shows the piston in another location;
The detail view of the part VI of Fig. 6 Fig. 5; And
Fig. 7 is the stereogram of the cylinder of Fig. 5.
Detailed description of the invention
Fig. 1 schematically shows the hydraulic machine of hydraulic exchanger 1 form with longitudinal profile.
Pressure exchanger comprises cylinder 2, and cylinder 2 can rotate around axis 3. Term " cylinder " is used to be convenient to explain.Cylinder 2 is cylinder form not necessarily. The main purpose of cylinder 2 is the base portions that are formed for cylinder 4. Cylinder 2 comprises multiple cylinders 4, at Fig. 1Shown in two cylinders 4. Cylinder 2 also can be called as " cylinder support ". Each cylinder 4 is defined in a circumferential direction by wall 5.Term " cylinder " is used to simplified illustration. Cylinder is circular section not necessarily.
The first front plate unit 6 is arranged on the first end of cylinder 2. The second front plate unit 7 is arranged on of cylinder 2Biend place, described the second end face is positioned on the opposition side of the first end face of cylinder 2.
The first front plate unit 6 comprises the first header board 8 and pressure shoe 9. The first header board 8 comprises high voltage supply mouth 10 and low-voltage returnAnswer back 11. High voltage supply mouth 10 is connected to the high-pressure channel 12 of pressure shoe 9 by means of sleeve 13. Cylinder 2 is by rotatable twelve Earthly BranchesSupport is in housing 14. Device for head roll 2 is not shown, thereby keeps view simple. But driving shaft can be through theTwo front plate units 7.
Each cylinder 4 is equipped with piston 15. Cylinder 4 is divided into the first chamber 16 and the second chamber 17 by piston 15. Piston 15 can beFirst end from cylinder 2 on first direction moves facing to the second end face. In addition, piston 15 can be in contrary second directionMove towards the first end face from the second end face of cylinder 2.
The movement of piston 15 is caused by pressure differential. In the example of Fig. 1, upper piston is being present in high voltage supply mouth 10 placesUnder the impact of hydraulic pressure, move in a first direction. During this moves, the liquid being present in the second chamber 17 is moved to secondHigh pressure return port 18 in front plate unit 7. When cylinder 2 further rotates, this cylinder 4 overlaps with low pressure supply port 19. Pressure ratio is lowPress the higher fresh liquid of pressure at return port 11 places to be fed into the second chamber 17, like this in second direction towards the first header boardInstall 6 mobile pistons 15, and liquid is released to low-voltage return from the first chamber 16 and answered back 11.
A kind of mode that increases the capacity of hydraulic exchanger 1 is to increase the velocity of rotation of cylinder 2. In this case, piston15 must move quickly, because they should, in the time short at the half-turn rotation time than cylinder 2, move from the first end faceTo the second end face, or vice versa. The high-speed mobile of piston 15 can cause trouble, because piston 15 touches end at themPortion is stopped when stop part (not shown) suddenly. This kind stops causing the noise that should be avoided to generate.
For this reason, be all provided with brake apparatus for two moving directions of piston 15, this kind of brake apparatus will with reference to figure 2-7Be illustrated.
Fig. 2 to 4 shows the brake apparatus for the first moving direction.
Casing wall 5 is arranged on the keeper 20 of the first end of cylinder 2 and the keeper 21 of the second end of cylinder 2Between. Can be by keeper 20 as end stop.
Sleeve 22 is arranged in cylinder 4 with around the second chamber 17. Piston 15 comprises the part 23 being guided in sleeve 22.The internal diameter of sleeve 22 is corresponding with the external diameter of part 23.
Have so extra effect, that is, piston 15 has difference in areas between multiple end faces, thus the stream in interchangerBody can be expanded, and can for example avoid booster pump in counter-infiltration system. But, the face between multiple end faces of pistonThe embodiment that product moment can otherwise be realized and be not limited to illustrate.
Piston 15 comprises another part 24, and this part 24 has larger diameter. The diameter of this part 24 is relative with the internal diameter of cylinder 4Should.
In addition, piston 15 comprises the protuberance 25 of directed the first keeper 20.
Brake chamber 26 is by periphery, the end face of sleeve 22 and the Part II 24 of piston 15 of casing wall 5, Part I 23Front surface limits.
This brake chamber 26 is connected with the inside of housing 14 via the first opening 27. At the First of the movement of piston 15 by stagesBetween, this first opening 27 allows fluid flow out and flow into the inside of housing 14, this housing from brake chamber 26 limitedly hardly14 inside is filled with low pressure liquid, the answer back pressure at 11 places of the pressure at described low pressure and low pressure supply port 19 places and low-voltage returnBetween pressure corresponding.
But the first opening 27 is only just opened during the Part I of piston 15 movement in a first direction. ChangeYan Zhi, this first opening is opened until the Part II 24 of piston 15 starts with the first opening 27 overlapping. Piston 15During being moved further in one direction, the first opening 27 is closed gradually, until arrive position as shown in Figures 2 to 4.
When the first opening 27 is closed, as in Figure 2-4, brake chamber 26 is only connected by means of first throttle outlet 28To the inside of housing 14. This first throttle outlet 28 allows liquid to flow out from brake chamber 26, but restriction is from brake chamber 26Flow out. The kinetic energy of piston 15 is converted to heat energy by this restriction.
In principle, the first opening 27 can be manufactured to the hole with the first diameter, and first throttle outlet 28 can be madeAs the hole with Second bobbin diameter, Second bobbin diameter is little more a lot of than the first diameter.
In a not shown manner, brake chamber 26 can be by means of the check-valves quilt of the direction upper shed towards brake chamber 26Be connected to the inside of housing 14. When piston 15 is in the time that second party moves up, this kind of check-valves contributes to refill brake chamber26。
Alternatively or additionally can otherwise realize the first throttle outlet of brake chamber 26. Fig. 3 showsLeakage paths 29 between sleeve 22 and the Part I 23 of piston 15. This leakage paths 29 can only pass through sleeve 22 HesRealize in gap between the Part I 23 of piston 15. This leakage paths 29 can also be by the Part I along piston 1523 groove extending longitudinally is realized.
In the time that piston 15 moves in a first direction, liquid overflows from brake chamber 26 via the first opening 27, until liveThe Part II 24 of plug 15 starts closed the first opening 27. Being moved further of piston 15 causes the first opening 27 more and more less,Increase gradually thus the flow resistance that liquid overflows from brake chamber 26. In the time of the complete closure of the first opening 27 quilt, liquid energyEnough only exporting 28 by first throttle overflows or overflows by leakage paths 29. Finally, only arrive end at piston 15Before block piece, the movement of piston 15 stops, and current in the situation that, this end stop can be formed by sleeve 22.
Fig. 5 to 7 shows the brake apparatus at the other end place that is positioned at cylinder 4. Identical element is with identical Reference numeral tableShow.
The second brake chamber 30 is formed on wall 5, the protuberance 25 of piston 15 and front surface and the guarantor of Part II 24 of cylinderBetween the front surface of gripping member 20.
As long as when piston 15 protuberance 25 in the time that second party moves up is not also inserted into the passage in keeper 20In 31, this second brake chamber 30 is open. Passage 31 is connected to low-voltage return and answers back 11. In this way, as long as the second systemMoving chamber is not closed, and the second brake chamber 30 can unrestrictedly output to low pressure by the liquid in the first chamber 16 of cylinder 4 and returnsIn mouth 11.
Protuberance 25 comprises tapering point 32. In Fig. 6, tapering point 32 is shown as the whole circumference that covers protuberance 25.But in some cases, enough, this tapering point only extends in the part of circumference.
Passage 31 forms the second opening, when piston is in the time that second party moves up, liquid can be through the second opening thus andSpill into outside the first chamber 16. In the time that protuberance 25 enters into passage 31, the size of this opening is reduced. Due to tapering point32, thereby the size of this opening reduces gradually.
In the time that protuberance 25 has arrived position as shown in Figure 6, in this position, it is complete that passage 31 is highlighted portion 25Closure, making unique path that liquid flows out the second brake chamber 30 is via second section flow export 33, this second section flow export 33Extend through piston 15. Second section flow export 33 comprises hole 34, by means of this hole 34, and the restriction effect energy of second section flow export 33Enough adjusted.
Usually, between the part of piston 15 and peripheral part of cylinder 4, always there is leakage paths. This leakage paths canTo be used as throttling outlet, thereby particular bore or valve are always unnecessary.
Claims (17)
1. a hydraulic machine, especially hydraulic exchanger (1), it comprises,
Cylinder (2), described cylinder (2) has the first end face and the second end face and can rotate around axis,
Described cylinder (2) comprising:
At least one cylinder (4), and
Be arranged on the piston (15) in described cylinder (4),
Described piston (15) can be on the first moving direction and at second moving direction contrary with described the first moving directionUpper movement,
Described piston (15) is divided into described cylinder at the Part I (16) of described the first end face split shed with described secondThe Part II (17) of end face split shed,
It is characterized in that,
Brake apparatus is set at least one for described moving direction, and described brake apparatus arrives at described piston (15)Before reaching end stop, brake described piston (15).
2. hydraulic machine according to claim 1, is characterized in that,
Described brake apparatus is hydraulic brake system.
3. hydraulic machine according to claim 2, is characterized in that,
Brake chamber (26,30) is set at least one for described moving direction, and described brake chamber (26,30) has outMouth (27,31), described opening (27,31) is opened during a part for the movement of described piston (15), and in described workThe preset distance place that plug arrives before described end stop is closed, and closed described brake chamber (26,30) has at least oneIndividual throttling outlet (28,29; 33,34; 5,24).
4. hydraulic machine according to claim 3, is characterized in that,
Described throttling outlet (33) comprises hole (34).
5. according to the hydraulic machine described in claim 3 or 4, it is characterized in that,
Described throttling outlet (28) comprises valve, especially check-valves.
6. according to the hydraulic machine described in any one in claim 3 to 5, it is characterized in that,
Described throttling outlet comprises leakage paths (29; 5,24).
7. according to the hydraulic machine described in any one in claim 3 to 6, it is characterized in that,
At the period of contact of described brake chamber, described piston (15) reduces described opening (27,31) gradually.
8. according to the hydraulic machine described in any one in claim 3 to 7, it is characterized in that,
Described brake chamber (26,30) is arranged between the wall (5) and described piston (15) of described cylinder (4).
9. according to the hydraulic machine described in any one in claim 3 to 8, it is characterized in that,
The first brake chamber (26) is set to for described the first moving direction, and the first brake chamber (26) has the first opening (27)With first throttle outlet (28,29), and the second brake chamber (30) is set to for described the second moving direction, the second brakingChamber (30) has the second opening (31) and second section flow export (33,34), described first throttle outlet (28,29) and described secondThrottling outlet (33,34) is spaced.
10. hydraulic machine according to claim 9, is characterized in that,
Described the first opening (27) is arranged in the described wall (5) of described cylinder (4).
11. hydraulic machines according to claim 10, is characterized in that,
Described first throttle outlet (28) is arranged in the described wall (5) of described cylinder (4).
12. 1 kinds according to the pressure exchanger described in claim 10 or 11, it is characterized in that,
Sleeve (22) is arranged in described cylinder (4) to reduce the internal diameter in described Part II (17) of described cylinder (4), instituteState piston (15) and comprise the part (23) being inserted in described sleeve (22), described the first brake chamber (26) is by described piston(15), the described wall (5) of described sleeve (22) and described cylinder defines.
13. 1 kinds according to the pressure exchanger described in any one in claim 9 to 12, it is characterized in that,
Described the second opening (31) is the opening of described cylinder (4) in end face.
14. pressure exchangers according to claim 13, is characterized in that,
Described second section flow export (33,34) extends through described piston (15).
15. pressure exchangers according to claim 14, is characterized in that,
The low-pressure side that described second section flow export (33,34) leads to described cylinder (4).
16. according to claim 13 to the pressure exchanger described in any one in 15, it is characterized in that,
Described the second opening (31) has the little area of section of area of section than described cylinder (4), and described piston has protuberance(25),, before described piston (15) arrives described end stop, described protuberance (25) enters described the second opening (31)Described in preset distance.
17. pressure exchangers according to claim 16, is characterized in that,
Described protuberance (25) comprises end (32), and described end is cone at least a portion of the circumference of described protuberanceShape.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP14193210 | 2014-11-14 | ||
| EP14193210.3A EP3020968B1 (en) | 2014-11-14 | 2014-11-14 | Hydraulic machine, in particular a hydraulic pressure exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105605024A true CN105605024A (en) | 2016-05-25 |
Family
ID=51904768
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510784206.2A Pending CN105605024A (en) | 2014-11-14 | 2015-11-16 | Hydraulic machine, in particular a hydraulic pressure exchanger |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP3020968B1 (en) |
| CN (1) | CN105605024A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810684A (en) * | 2021-01-28 | 2022-07-29 | 丹佛斯有限公司 | Pressure exchanger |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20230020630A1 (en) * | 2021-07-08 | 2023-01-19 | Energy Recovery, Inc. | Reduced mixing pressure exchanger |
| EP4130492A1 (en) * | 2021-08-04 | 2023-02-08 | Danfoss A/S | Pressure exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5316451A (en) * | 1990-06-05 | 1994-05-31 | Abb Mineral Slurry Transportation Pty. Ltd. | Valve porting for rotating barrel ram pump |
| EP1508361A1 (en) * | 2003-08-22 | 2005-02-23 | Danfoss A/S | A pressure exchanger |
| CN201099279Y (en) * | 2007-08-28 | 2008-08-13 | 张保兴 | Hydraulic exchanger for controlling standby booster pump |
| CN101545506A (en) * | 2008-03-26 | 2009-09-30 | 通用汽车环球科技运作公司 | Hydraulic actuator for transmissions having reduced noise |
| CN101907113A (en) * | 2009-06-03 | 2010-12-08 | Smc株式会社 | The air cushion mechanism of pneumatic of cylinder |
| CN103958893A (en) * | 2011-10-27 | 2014-07-30 | 罗伯特·博世有限公司 | Hydrostatic piston machine |
-
2014
- 2014-11-14 EP EP14193210.3A patent/EP3020968B1/en not_active Not-in-force
-
2015
- 2015-11-16 CN CN201510784206.2A patent/CN105605024A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5316451A (en) * | 1990-06-05 | 1994-05-31 | Abb Mineral Slurry Transportation Pty. Ltd. | Valve porting for rotating barrel ram pump |
| EP1508361A1 (en) * | 2003-08-22 | 2005-02-23 | Danfoss A/S | A pressure exchanger |
| CN201099279Y (en) * | 2007-08-28 | 2008-08-13 | 张保兴 | Hydraulic exchanger for controlling standby booster pump |
| CN101545506A (en) * | 2008-03-26 | 2009-09-30 | 通用汽车环球科技运作公司 | Hydraulic actuator for transmissions having reduced noise |
| CN101907113A (en) * | 2009-06-03 | 2010-12-08 | Smc株式会社 | The air cushion mechanism of pneumatic of cylinder |
| CN103958893A (en) * | 2011-10-27 | 2014-07-30 | 罗伯特·博世有限公司 | Hydrostatic piston machine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810684A (en) * | 2021-01-28 | 2022-07-29 | 丹佛斯有限公司 | Pressure exchanger |
| US11920573B2 (en) | 2021-01-28 | 2024-03-05 | Danfoss A/S | Pressure exchanger |
| CN114810684B (en) * | 2021-01-28 | 2024-05-03 | 丹佛斯有限公司 | Pressure exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3020968B1 (en) | 2016-08-24 |
| EP3020968A1 (en) | 2016-05-18 |
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