EP1066466B1 - High-pressure piston cylinder unit - Google Patents

Abstract

The invention relates to a high-pressure piston cylinder unit, especially an injection pump or an injection valve for an internal combustion engine, and to a method for producing one such high-pressure piston cylinder unit. The high-pressure piston cylinder unit has a piston which is guided inside a cylinder bore and which is coupled to an actuating element. The piston is subjected to a high pressure differential. According to the invention, fine grooves which run very close to one another are configured in at least one part of the guiding surface of the piston. The grooves ensure hydraulic pressure compensation on the periphery of the guiding surface, thus reducing wear, and prevent leakage in a longitudinal guiding direction.

Description

The invention relates to a high-pressure piston-cylinder unit, in particular one Injection pump or an injection valve for an internal combustion engine, in particular for high number of lifting cycles, as provided in the preamble of claim 1.

In such a high-pressure piston-cylinder unit, which has a large number of Lift cycles is exposed, as is particularly the case with an injection pump or a Injector for an internal combustion engine is generally a piston available, which is guided in a cylinder bore, and which a high Pressure difference is exposed. The piston guided in the cylinder bore serves either the delivery of the fuel to be injected into the combustion chamber of the internal combustion engine, as in the case of an injection pump, or in the case of an injection valve, below Exposure to the fuel to be injected under high pressure Open the injector, typically by having the piston coupled or Nozzle needle formed in one piece from the valve seat of a needle valve takes off and thus an injection cross section for injecting the fuel into the Releases the combustion chamber of the internal combustion engine.

With such a high-pressure piston-cylinder unit, there is the fact that ultimately unavoidable manufacturing tolerances a deaxing of the piston in the Cylinder bore occurs, which has the consequence that the pressure distribution over the Piston circumference because of the different setting over the piston circumference Gap widths is not uniform, and this results in a resulting radial force that acts in the direction of deaxing. The resulting one-sided pressure of the Piston in its guide leads to wear in the contact surface.

In the case of a common rail fuel injection system, in which the one to be injected Fuel is stored in a storage tank under high pressure and is kept permanently fuel injected by the high pressure fuel into the Combustion chamber of the internal combustion engine is injected, the risk of wear is special high. With permanently acting high pressures comes namely add to the stress that the resulting from the compressive forces Radial forces act in full during the entire lifting phase, unlike one conventional injection system, in which the stroke is still partially in the Pressure build-up phase, i.e. when the injection pressure is lower than the maximum Pressing takes place. Characterized in that the actuation of the injection valve of a common rail fuel injector serving piston, typically with the valve needle of the Injector coupled or integrally formed with this, the is exposed to the high fuel pressure that arises during deaxing the nozzle needle guide to the nozzle needle seat or the piston in the cylinder bore permanent leakage flow asymmetrical over the piston circumference. Also act due to the high pressures high, the deaxing reinforcing radial forces that during the entire lifting phase are available, in particular also at the beginning of the Lifting phase. These radial forces can start or rub and become too strong Wear of the nozzle needle in the nozzle needle guide or the piston in the Lead cylinder bore.

An injection valve for an internal combustion engine is known from DE 38 24 467 C2, at which the valve needle in two parts by a hollow needle and one in an inner bore the hollow needle guided valve needle is formed. The hollow needle points in the area of Point a number of circumferential grooves, which in Longitudinal direction of the valve needle by a distance of about the order of magnitude Diameter of the valve needle are spaced and have a width and depth that correspond to about one tenth of the valve needle diameter.

Furthermore, from MTZ 55 (1994) 9, page 502, column 3 and page 511, column 1 Use of titanium nitride coatings for the pistons of Fuel injection pumps for large diesel engines are known to "seize" the To prevent piston.

EP 0 565 742 A1 describes methods for the fine machining of workpiece surfaces, in particular of walls of the bores in the cylinder of an internal combustion engine known in which the surface by blasting, in particular by means of a Lasers arranged according to a predetermined pattern are generated, which as Lubricant reservoir should serve.

Finally, EP 0 419 999 B1 describes a method for processing by friction highly stressed surfaces in internal combustion engines, especially the cylinder surfaces known from piston engines, in which the surface is honed and additionally one Laser beam treatment is subjected, the laser treatment for the evaporation of outstanding roughness peaks or scaling is used to make it smoother To reach surface.

An injection valve for an internal combustion engine is known from US Pat. No. 3,398,936 emerge, in which the nozzle needle in the guide surface with annular or in the form of a Threaded grooves is executed. The groove spacing will be obvious the natural frequency of the nozzle needle oriented to vibrations of the nozzle needle To cushion the impact in their seat and to prevent injections. In addition, should friction and wear can also be avoided and centering of the nozzle needle can be achieved to wear through friction and seizure of the nozzle needle avoid. The grooves can also be arranged in the guide bore. In one Embodiment are a number of five annular grooves along the longitudinal axis of the guide pin. The centering and wear reduction should Obviously be achieved by the fact that fuel present in the grooves Exerts lubricating effect. The grooves also serve as metallic abrasion particles record and thereby avoid further abrasion.

WO 89/10479 describes a high-pressure piston-cylinder unit, in particular for one High pressure pump shown as an injection pump of a diesel engine. To the danger of To prevent the piston from seizing up, the boundary gap between the piston surface area and expanded cylinder area. In one exemplary embodiment, this is done in that one or more spaced circumferential grooves in the lateral surface of the Piston and / or in the cylinder surface. If the piston during the Operating in an eccentric position, it will be on the enlarged side Limit gap building pressure through the circumferential grooves on the entire circumference of the Limit gap distributed, whereby eccentric forces are avoided. In one Exemplary embodiments are three in the region of the lateral surface of the printing edge spaced circumferential grooves or less. The grooves are obviously far apart. The disadvantage is that wear and tear and seizure are not prevented, since in the predominantly sliding surface areas of the piston no lubricating film is built up.

A high pressure fuel injection device is described in DE 41 39 907 A1, at which is a labyrinth seal in the form of ring grooves in the outer surface of a piston or is arranged in the inner wall surface of the cylinder bore associated with the piston. With a gap flow of this seal is to be reduced, it being disadvantageous that due to the seal, the access of fuel to the guide surfaces is reduced.

The object of the invention is to provide a high-pressure piston-cylinder unit, in particular for to specify an injection pump or an injection valve for an internal combustion engine, at which has a lower risk of wear on a guided in a cylinder bore Piston exists by deaxing.

Furthermore, the invention is intended to provide a method for producing such High pressure unit can be specified.

This object is achieved by the high-pressure piston-cylinder unit specified in the claims or by the method specified in the claims for Manufacture of such a solution, the respective advantageous embodiments in the Subclaims are specified.

The invention provides a high-pressure piston-cylinder unit, in particular a Injection pump or an injection valve for an internal combustion engine, in particular for created a high number of lifting cycles, in which a guided in a cylinder bore Piston on one side a high pressure and thus a high pressure difference is exposed, according to the invention at least in a part of the guide surface of the Piston or the cylinder bore at a short distance from each other fine grooves are formed. The grooves formed in the guide surface have a Width b from 5 to 100 µm. The distance between the grooves is 0.05 up to 1 mm.

An advantage of the guide surface of the piston designed according to the invention is that that there is a hydraulic pressure equalization on the circumference of the guide through the grooves and so that the one-sided contact of the piston in the cylinder bore is prevented or at least the contact forces are reduced. Another advantage is that the Leakage flow after central alignment of the piston in the longitudinal direction of the Guide surface of the piston is reduced and thus the hydraulic efficiency of the Unity is improved. A reduction in the leakage flow is also coming only because the grooves running transverse to the direction of the leakage flow act like a labyrinth seal. Another advantage is that this is in the grooves fluid present wets the contact surfaces, whereby a lubrication effect is achieved.

The width b of the grooves is preferably between 10 and 40 μm. The depth t of the grooves is advantageously between 3 to 50 microns, preferably between 10 to 30 microns.

The distance a between the grooves is preferably between 0.1 and 0.3 mm.

According to an advantageous embodiment, the width b corresponds to a groove in the essentially their depth t.

It is also advantageous if the ratio of the depth t of the groove to Nominal diameter D of the guide surface is between 1/200 and 1/1000.

According to one embodiment of the invention, the grooves in the circumferential direction are Guide surface designed to run.

According to a further development thereof, the grooves can also be provided in the longitudinal direction Guide surface varying distance a be formed.

According to another embodiment of the invention, it is provided that the grooves in Longitudinal direction of the guide surface are formed.

According to another embodiment of the invention, it is provided that the grooves under are formed at an angle to the longitudinal direction of the guide surface.

According to a further development, the grooves can be arranged in the longitudinal direction of the Guide surface have varying slope.

According to another embodiment of the embodiment which is very advantageous in terms of production technology Invention it is provided that the grooves are formed by a helix.

This can be further developed in that the helix is multi-start.

The helix can have a gradient varying in the longitudinal direction of the guide surface to have.

According to yet another embodiment of the invention, it is provided that the grooves' at different angles to the longitudinal direction of the guide surface crosswise are progressive.

This can be further developed in that the grooves in the longitudinal direction of the Guide surface of varying slope are formed.

In the aforementioned embodiments, it may be advantageous to set the distance a Grooves in the longitudinal direction of the guide surface so that it is essentially the Operating stroke of the piston in the cylinder bore corresponds.

According to a further embodiment of the invention, several of the aforementioned can Patterns can be combined to form the grooves.

According to one embodiment of the invention it is provided that the grooves in one the high pressure side of the piston adjoining area of the guide surface are trained.

Alternatively, the grooves can extend over the entire area of the guide surface be trained.

The invention is of particular value in the case of a high-pressure piston-cylinder unit which Part of a fuel injector of a common rail injection system, in which the Piston is used to actuate the injector of the fuel injector, and wherein the Pressure difference permanently applied to the piston. With such a permanent from The component subjected to fuel pressure can undergo constant deaxing, i.e. from the beginning the movement of the piston in the cylinder bore occur, which is why Invention here achieved a significant reduction in wear with particular advantage can be.

In such a, serving as part of a common rail injection system High pressure unit, the piston is advantageously made of one piece of material on the nozzle needle of the injection valve, wherein the piston has a shoulder that is permanent is acted upon by the fuel pressure of the common rail injection system.

According to the invention, the grooves on which the fuel pressure is advantageous are advantageous acted shoulder adjoining, serving as a guide surface jacket surface of the Pistons trained.

The inventive method for manufacturing a high pressure unit of the invention it provides that the grooves are produced by machining, for example fine turning become.

An alternative method, which is particularly advantageous, provides for the grooves to generate by beam processing.

Such beam processing is advantageously carried out in particular by laser engraving.

An advantageous development of the method according to the invention provides that after the grooves have been created, lapping or fine grinding the Guide surface is made. One can also create the grooves Fine machining of the guide surface must be upstream.

Figur 1

eine teilweise geschnittene Seitenansicht des Einspritzventils eines Kraftstoffinjektors eines Common-Rail-Einspritzsystems, welches gemäß einem Ausführungsbeispiel der Erfindung ausgebildet ist, wobei der Ausschnitt A vergrößert die in der Führungsfläche eines Kolbens des Einspritzventils vorgesehenen feinen Rillen zeigt;

Figur 2

eine vergrößerte Ansicht der Düsennadel des Einspritzventils des in Figur 1 gezeigten Kraftstoffinjektors;

Figur 3

einen stark vergrößerten Querschnitt durch die an der Führungsfläche des Kolbens der in Figur 2 gezeigten Düsennadel ausgebildeten feinen Rillen; und

Figur 4

eine Figur 2 entsprechende Ansicht der Düsennadel des Einspritzventils mit vier Ausführungsbeispielen a) bis d) der Anordnung der Rillen an der als Führungsfläche dienenden Mantelfläche des Düsennadelkolbens.

Figur 5

eine stark vergrößerte Ansicht der Führungsfläche des Kolbens mit als Schraubengewinde ausgebildeten Rillen.

Exemplary embodiments of the invention are explained below with reference to the drawing.
Show it:

Figure 1

a partially sectioned side view of the injection valve of a fuel injector of a common rail injection system, which is designed according to an embodiment of the invention, wherein the cutout A shows the fine grooves provided in the guide surface of a piston of the injection valve;

Figure 2

an enlarged view of the nozzle needle of the injection valve of the fuel injector shown in Figure 1;

Figure 3

a greatly enlarged cross section through the fine grooves formed on the guide surface of the piston of the nozzle needle shown in Figure 2; and

Figure 4

a view corresponding to Figure 2 of the nozzle needle of the injection valve with four embodiments a) to d) the arrangement of the grooves on the surface of the nozzle needle piston serving as a guide surface.

Figure 5

a greatly enlarged view of the guide surface of the piston with grooves formed as a screw thread.

Figure 1 shows a view, partially in cross section, of the injector Fuel injector for a common rail fuel injection system. The one with the Injection nozzle designated 1 has a needle housing 2, in which a cylinder bore 3 is provided. A piston 5 is located in this cylinder bore 3 performed, which is integrally formed with a nozzle needle 4. The nozzle needle 4 has a needle tip 8 which interacts with a valve seat 9. In the area of the valve seat 9 is an injection cross section 11 in the form of injection openings educated. At the transition from the piston 5 to the nozzle needle 4 there is a shoulder 6 formed, which lies in the region of an annular space 12 formed in the needle housing, in which a fuel channel 7 opens. The fuel channel 7 leads to a High-pressure accumulator of the common rail system, in which fuel is to be injected is held under high pressure. To control the injector 1, the Fuel injector via an actuating element, not shown in FIG. 1 electromechanical or hydraulic, as is well known, by which the piston 5 is released in the sense of an upward movement, so that in the Annulus 12 acting on the shoulder 6 of the piston 5 fuel pressure raising the Nozzle needle 4 and thus the needle tip 8 from the valve seat 9 and thus a release of the injection cross section 11.

As can be seen in the enlarged section labeled A, in the The outer surface of the piston 5 is a fine distance apart Grooves 10 formed. On the one hand, these grooves 10 effect a hydraulic one Pressure equalization over the circumference of the piston 5 in the through the cylinder bore 3rd formed guide and thus prevent one-sided contact of the piston 5 due of the annular space 12 forth in the gap between the outer surface of the piston 5 and the high pressure fuel entering the cylinder bore 3 Deaxization of the nozzle needle guide. At the same time it becomes asymmetrical and therefore increased leakage flow in the longitudinal direction of the guide between the lateral surface of the Piston 5 and the cylinder bore 3 reduced and thus the hydraulic efficiency of the fuel injector improved.

In FIG. 2, the nozzle needle 4 is provided in one piece with the piston 5 shown enlarged. The piston 5 has a nominal diameter D, which at the illustrated embodiment is 6.8 millimeters. From shoulder 6 and so from the fuel under high pressure in the annulus 12 acted side of the piston 5 ago over a length 1, the grooves 10 in Formed circumferentially on the lateral surface of the piston 5. In which In the illustrated embodiment, this length is 1, over which the grooves 10 approximately 22 mm are provided.

In Figure 3 is a greatly enlarged cross section through the surface of the jacket of the Piston 5 shown, which shows two grooves 10. The cross section of the grooves 10 has the illustrated embodiment has a substantially triangular shape. The width b a groove is, for example, 5 to 100 microns, preferably between 10 to 40 microns. at the illustrated embodiment, the groove width b is 30 microns. The groove depth t can be 3 to 50 microns, preferably between 10 to 30 microns. In the illustrated Embodiment is the depth t 15 microns. The distance a between two grooves can between 0.05 to 1 mm, preferably between 0.1 to 0.5 mm, preferably between 0.1 to 0.3 mm. In the illustrated embodiment, the distance is a 0.2 mm.

The ratio of the depth t of the groove 10 to the nominal diameter D of the guide surface or of the piston 5 is advantageously between 1/200 and 1/1000. at the illustrated embodiment, the said ratio is around 1/450, which turns out to be has proven particularly advantageous.

The cross section of the grooves 10 can also have other shapes instead of a triangular shape assume, for example, a semicircular shape.

FIG. 4 again shows a representation corresponding to FIG. 2 and examples a) to d) of the Structuring the outer surface of the piston 5.

According to the example in FIG. 4 a), the grooves 10 are in the circumferential direction of the piston 5 formed, as shown in the side view above and also in Figure 2. In which Embodiment are the grooves in the longitudinal direction with an equal distance a formed, alternatively, the grooves 10 can also with a in the longitudinal direction Guide surface varying distance a be formed.

According to the embodiment of Figure b), the grooves 10 are in the longitudinal direction Guide surface designed to run.

According to the exemplary embodiment in FIG. 4c), the grooves 10 are closed at an angle Longitudinal direction of the guide surface. In the illustrated In the embodiment, the grooves 10 all have the same pitch. Alternatively the grooves 10 can also vary with a lengthways direction of the guide surface Slope should be provided.

As a limit case of the arrangement of the grooves 10 in the circumferential direction as in Figure 4a) and Arrangement of the grooves at an angle to the longitudinal direction as in Figure 4c), the Grooves 10 may be formed by a helix. A section of the guide surface with Grooves formed as a screw thread 22 are shown in FIG. The Guide surface is a cylindrical piston surface, which of the threads of the Screw thread 22 is divided. The pitch of the screw thread 22 is s specified. The screw thread or the screw line can be catchy or also be multi-course. The helix can be one in the longitudinal direction of the Guide surface constant slope or alternatively one in the longitudinal direction of the Guide surface have a varying slope. The formation of the grooves as a helix is particularly advantageous in terms of manufacturing technology.

According to FIG. 4d), the grooves 10 can be at different angles to the longitudinal direction the guide surface may be designed to run crosswise, the angles opposite, but the same amount or different amount can. While in the illustrated embodiment the slope of the grooves 10 in In the longitudinal direction of the guide surface is the same, the grooves 10 can alternatively also with be designed in the longitudinal direction of the guide surface varying slope.

The structuring patterns according to FIGS. 4a) to 4d) are basic patterns, different ones However, patterns are also possible. Furthermore, several patterns according to the under Combined with reference to Figures 4a) to 4d) described type.

According to a special embodiment of the invention, the distance a is the grooves 10 chosen in the longitudinal direction of the guide surface so that it is essentially the Operating stroke of the piston 5 in the cylinder bore 3 corresponds. This has the beneficial Effect that the remaining guide surface on the jacket of the piston 5 between the grooves 10 is constantly moving on the wetted surfaces of the guide and thus Running dry the guide is made largely impossible. With a catchy Thread corresponds to the distance a between the grooves 10 then the thread pitch.

In the exemplary embodiments illustrated with reference to FIGS. 1 to 4, the grooves 10 formed in the outer surface of the piston 5 in its function as a guide surface. Alternatively or optionally in addition, the grooves 10 can also be in the Cylinder bore 3 can be formed as a guide surface.

In the application shown in Figure 1, an injection valve for a common rail fuel injector is the one held by the pre-memory Fuel pressure via the fuel channel 7 and the annulus 12 permanently on the Shoulder 6 of the piston 5, so that the piston 5 permanently one-sided Pressure difference is exposed. This has the advantage of that caused by the grooves 10 hydraulic pressure compensation and the reduction of leakage flow especially for Wear. However, also in the case of other high-pressure piston-cylinder units in which one Piston is exposed to a high pressure difference on one side, as is particularly the case with other injectors and in the case of injection pumps for internal combustion engines, the invention leads to a corresponding advantage.

The grooves 10 in the guide surface of the piston, that is to say in the lateral surface of the piston 5 or in the surface of the cylinder bore 3 by machining, for example by turning, fine turning, grinding or milling. alternative for this purpose, the grooves can pass through, in particular on the lateral surface of the piston 5 Beam processing are generated, in particular the method of laser engraving is advantageous. The grooves 10 are produced after the finishing (grinding) of the Guide surface. After the creation of the grooves 10, a lapping or Fine grinding the guide surface made to the final surface of the Manufacture guide surface. Finishing the guide surface before creating it the grooves can also be omitted if there is adequate dimensional accuracy through suitable Manufacturing measures can be guaranteed.

LIST OF REFERENCE NUMBERS

1

injection

2

needle housing

3

bore

4

nozzle needle

5

piston

6

shoulder

7

Fuel channel

8th

pinpoint

9

valve seat

10

groove

11

Injection cross section

12

annulus

22

screw thread

Claims (28)

1. High-pressure piston/cylinder unit, in particular of an injection pump or of an injection valve for an internal combustion engine, in particular for high numbers of stroke cycles, with a piston (5) which is guided in a cylinder bore (3) and is coupled to an actuating element and which is exposed to a high pressure difference, grooves (10) being formed at least in part of a guide surface of the piston (5), to be precise in the outer surface of the piston (5) or the cylinder bore (3), characterized in that the grooves (10) have a width b of between 5 and 100 µm and run at a distance a of between 0.05 and 1 mm from one another.
2. High-pressure unit according to Claim 1, characterized in that the grooves (10) have a width b of between 10 and 40 µm
3. High-pressure unit according to Claim 1 or 2, characterized in that the grooves (10) have a depth t of between 3 and 50 µm, preferably of between 10 and 30 µm.
4. High-pressure unit according to Claim 1, 2 or 3, characterized in that the grooves (10) are at a distance a from one another of between 0.1 and 0.5 mm, preferably of between 0.1 and 0.3 mm.
5. High-pressure unit according to one of Claims 1 to 4, characterized in that the width b of a groove (10) corresponds essentially to its depth t.
6. High-pressure unit according to one of Claims 1 to 5, characterized in that the ratio of the depth t of the groove (10) to the nominal diameter D of the guide surface is between 1/200 and 1/1000.
7. High-pressure unit according to one of Claims 1 to 6, characterized in that the grooves (10) are designed to run in the circumferential direction of the guide surface.
8. High-pressure unit according to Claim 7, characterized in that the grooves (10) are designed with a distance a from one another which varies in the longitudinal direction of the guide surface.
9. High-pressure unit according to one of Claims 1 to 6, characterized in that the grooves (10) are designed to run in the longitudinal direction of the guide surface.
10. High-pressure unit according to one of Claims 1 to 6, characterized in that the grooves (10) are designed to run at an angle to the longitudinal direction of the guide surface.
11. High-pressure unit according to Claim 10, characterized in that the grooves (10) have a pitch varying in the longitudinal direction of the guide surface.
12. High-pressure unit according to one of Claims 1 to 6, characterized in that the grooves (10) are formed by a counter-clockwise or clockwise helical line.
13. High-pressure unit according to Claim 12, characterized in that the helical line is multi-flight.
14. High-pressure unit according to Claim 12 or 13, characterized in that the helical line has a pitch varying in the longitudinal direction of the guide surface.
15. High-pressure unit according to one of Claims 1 to 6, characterized in that grooves (10) are designed to run crosswise at different angles to the longitudinal direction of the guide surface.
16. High-pressure unit according to Claim 15, characterized in that the grooves (10) are designed with a pitch varying in the longitudinal direction of the guide surface.
17. High-pressure unit according to one of Claims 7 to 16, characterized in that the distance a of the grooves (10) from one another in the longitudinal direction of the guide surface corresponds essentially to the operating stroke of the piston (5) in the cylinder bore (3).
18. High-pressure unit according to one of Claims 1 to 6, characterized in that the grooves (10) are designed in a combination of a plurality of patterns according to Claims 7 to 16.
19. High-pressure unit according to one of Claims 1 to 18, characterized in that the grooves (10) are formed in a region of the guide surface which adjoins the high-pressure side of the piston (5).
20. High-pressure unit according to one of Claims 1 to 18, characterized in that the grooves (10) are formed over the entire region of the guide surface.
21. High-pressure unit according to one of Claims 1 to 20, characterized in that the high-pressure piston/cylinder unit is an integral part of a fuel injector of a common-rail injection system, in which the piston (5) serves for actuating the injection valve of the fuel injector, the pressure difference bearing permanently on the piston (5).
22. High-pressure unit according to Claim 21, characterized in that the piston (5) is formed materially in one piece on the nozzle needle (4) of the injection valve, the piston (5) having a shoulder (6) which is acted upon permanently by the fuel pressure of the common-rail injection system.
23. High-pressure unit according to Claim 22, characterized in that the grooves (10) are formed on the outer surface of the piston (5), the said outer surface serving as a guide surface and adjoining the shoulder (6) acted upon by the fuel pressure.
24. Method for producing a high-pressure unit according to one of Claims 1 to 23, characterized in that the grooves (10) are made by cutting machining, in particular turning, fine turning, grinding or milling.
25. Method for producing a high-pressure unit according to one of Claims 1 to 23, characterized in that the grooves (10) are made by beam machining, in particular laser beam or electron beam.
26. Method according to Claim 25, characterized in that the grooves (10) are made by laser engraving.
27. Method according to Claim 24, 25 or 26, characterized in that, after the grooves (10) have been made, lapping or precision grinding of the guide surface is carried out.
28. Method according to Claim 27, characterized in that the making of the grooves (10) is preceded by a fine machining of the guide surface.

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