• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The hydraulic system comprises a housing (10) in which a hydraulic apparatus (12) is arranged, main ducts (1, 2) for feeding and exhausting the hydraulic apparatus, a shaft (14) engaged in the housing, and a sealing device (16) between the shaft and the housing which comprises two sealing elements (20, 22) disposed on the shaft, providing between them an intermediate chamber (24). The system has a connection (26, 28B) between the intermediate chamber (24) and one (1) of the main pipes, this connection being equipped with a check valve (30) allowing only the flow of fluid in the direction going from the intermediate chamber (24) to said one of the main pipes (1).
    公开号:FR3037354A1
    申请号:FR1555358
    申请日:2015-06-12
    公开日:2016-12-16
    发明作者:Stephane Vidal；Jeremie Mulot；Gery Depierre
    申请人:Poclain Hydraulics Industrie；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a hydraulic system comprising a casing in which is arranged a hydraulic apparatus, main ducts for the supply and exhaust of the hydraulic apparatus, a shaft engaged in the casing, and a sealing device between the shaft and the casing, the sealing device comprising a first and a second sealing element successively arranged on the shaft while providing between them an intermediate chamber. For example, the hydraulic apparatus may comprise a cylinder block, a cam and a distributor, so that, considered with the housing, it forms a hydraulic motor. For the deactivation of this hydraulic motor, the pistons slidably mounted in the cylinders of the cylinder block can be retracted into the cylinder to stop being in contact with the cam, thus operating what is called a motor clutch. This clutch can be aided or caused by the pressurization of the interior space of the housing. However, when you want to reactivate the engine, and thus bring out the pistons of their cylinders to bring them into contact with the cam, thus operating what is called a motor interconnection, the pressure in the interior space can increase suddenly due to the exit of the pistons, thus causing a peak pressure. We know a system of this type by the French patent application FR 2 967 228 in the name of the Applicant. As indicated in FR 2 967 228, the presence of the first sealing element makes it possible to protect the second sealing element against the pressure peaks that can occur in the interior space of the casing. The intermediate chamber serves as a buffer space, in particular to collect the fluid from leaks at the first sealing member, these leaks occurring at such peaks pressure. The first sealing element is composed of a rigid ring and a flexible pushing and sealing member. Thus, the first seal member can not flex under pressure, but may ooze slightly, while the second seal member is a flexible seal designated as a commercial lip seal, which provides a perfect seal on a shaft. turning, but that could flex under the pressure. According to FR 2 967 228, the intermediate chamber is connected to a drain, which makes it possible to avoid pressure increases in this chamber and thus to further improve the protection of the second sealing element. . The assembly of these two joints to seal the connection between a rotating shaft and a casing of a hydraulic apparatus, combined with a drainage of the intermediate chamber provides a perfect seal throughout the 5 use of the hydraulic unit, even if the crankcase pressure becomes high or crankcase pressure peaks occur. Similarly, the French patent application filed under No. 13 62756 (unpublished) relates to a system of the same type in which the intermediate chamber is connected to the internal space of the casing via a calibrated nozzle, in order to organize a leak between the interior of the housing and the discharge chamber, with a given pressure drop between these two enclosures. In known systems, for example by the two aforementioned documents, the intermediate chamber is connected to a drain line, which is a specific pipe, machined in the shaft. Thus, this pipe requires a particular machining of the shaft and, in the case where other pipes are also machined in the shaft (for example the main pipes for the supply and the exhaust of the hydraulic apparatus, or else a pipe used for the supply of the fluid of decrabotage and the evacuation of this fluid), the shaft must be dimensioned, both in terms of size and on that of its mechanical strength, so as to accommodate the pipe (s) to be machined. The invention aims to improve this state of the art, avoiding the need for a specific drain line.
    [0002] This object is achieved by virtue of the fact that the hydraulic system has a connection between the intermediate chamber and one of the main ducts, this connection being equipped with a check valve allowing only the circulation of fluid in the direction from the intermediate chamber. to said one of the main pipes.
    [0003] Thus, according to the invention, advantage is taken of the presence of the main pipes, so that one of them is used as a drainage pipe, being connected to the intermediate chamber via the link equipped with a check valve. Since the sealing device of the hydraulic system is located between the shaft and the housing, there is a risk of overpressure in the intermediate chamber, in particular via a leak in the first sealing element, when the pressure in the housing crankcase is high. In the case where the hydraulic apparatus is of the type with reciprocating pistons, these risks of overpressure occur at the moment of the re-engagement of the pistons, when the pistons are taken out of their cylinders, to put them in contact with the cam. Now, at this time, the main pipes are not yet used to operate the hydraulic device, precisely because these pistons are not yet in their interconnected positions. In other words, in this situation, the pressure in the main pipes is maintained at a low value. Thus, if the pressure in the intermediate chamber becomes high, the excess fluid naturally flows to the main pipe to which the intermediate chamber is connected, in the direction of flow permitted by the check valve. Conversely, when the hydraulic apparatus is in operation, the main lines are pressurized to allow this operation. Thus, if the pressure in the main pipe to which the intermediate chamber is connected is greater than the target maximum pressure in this chamber (which is necessarily the case when the main pipe in question is the supply pipe), the fluid does not flow. does not flow from this pipe to the intermediate chamber. On the other hand, if the pressure of the main pipe to which the intermediate chamber is connected is lower than the target maximum pressure in this chamber, the fluid can flow from the intermediate chamber to the main pipe in question. This situation is rather theoretical since, in order to avoid cavitation phenomena, the pressure in the main pipe at the lowest pressure is at least equal to a booster pressure, which is generally quite higher than the atmospheric pressure. It is therefore easy, by a suitable design of the check valve, to avoid a supply of the intermediate chamber from the main pipe to which this chamber is connected even when this main pipe is at the low operating pressure of the hydraulic apparatus. Thus, thanks to the invention, effective drainage of the intermediate chamber is achieved, without requiring a specific drain line. Preferably, the non-return valve forms a restriction, generating a pressure drop between the intermediate chamber and one of the main lines.
    [0004] For example, the passage section of said restriction is of the order of 5 mm 2. Optionally, said at least one of the main lines, or each of the two main lines, comprises a section which passes into the shaft, and the connection comprises a bore of the shaft which extends between the intermediate chamber and said section. The piercing forming the connection may be of small size (short length and small passage section) and, in general, it is inclined with respect to the section of the main duct or ducts passing through the shaft. In particular, the drilling of the shaft can be oriented radially. Thus, this drilling does not affect the dimensioning or the mechanical strength of the shaft. It is also very easy to machine. Optionally, the non-return valve is disposed in the bore of the shaft.
    [0005] Optionally, the hydraulic system comprises a friction ring mounted tightly on the shaft and having an outer track with which at least one of the sealing elements cooperates, and the connection comprises a drilling of the friction ring. The outer race of the friction ring forms a suitable sealing surface for the sealing member (s) with which it cooperates. It is also possible that the friction ring also forms a support ring for a support bearing of the relative rotation between the shaft and the housing. However, in another embodiment, such a friction ring is not provided and the two sealing elements cooperate directly with the shaft, the surface of which forms a sealing surface. Optionally, the non-return valve is disposed in the bore of the friction ring when present. Optionally, said one of the main lines is the exhaust line of the hydraulic apparatus in the preferred direction of operation of said apparatus. Thus, in the operating situation, the pistons being clutched, the check valve is subjected to the exhaust pressure, which is of the order of the force-feeding pressure, which increases its service life compared to a situation in which it would be generally subjected to the supply pressure.
    [0006] It is possible to choose that the check valve be a simple valve, with no set pressure, in which case it opens to allow the circulation of fluid from the intermediate chamber to the main pipe to which this chamber is connected by the aforementioned connection, when the pressure in said chamber is greater than the pressure in said main pipe. However, optionally, the non-return valve is a valve calibrated at a setting pressure which is advantageously of the order of 3 bar. This set pressure means that the valve allows the flow of fluid from the intermediate chamber to the main pipe to which this chamber is connected when the pressure in said chamber exceeds the pressure in said main pipe of at least equal value. at the setting pressure. Calibration of the order of 3 bar makes it possible to use a non-return valve of simple and inexpensive manufacture. Optionally, the hydraulic apparatus comprises a cylinder block, a cam and a fluid distributor. Optionally, the hydraulic system is a drive system of a wheel of a vehicle, and the shaft forms the rocket of the wheel. Optionally, the shaft has only three axial sections of fluid conduit, namely two main sections respectively forming at least a portion of the main supply line and at least a portion of the main exhaust pipe, and a section auxiliary to supply the interior space of the housing with fluid under pressure. In particular, in the case where the hydraulic apparatus comprises retractable pistons, its auxiliary section serves to put the interior space of the crankcase under pressure to favor the declutching of the pistons.
    [0007] According to the invention, the drainage of the intermediate chamber is carried out by one of the main pipes, to which this chamber is connected via a non-return valve. The invention will be better understood and its advantages will appear better on reading the detailed description which follows, of an embodiment shown by way of non-limiting example. The description refers to the accompanying drawings, in which: - Figure 1 is an axial sectional view of a hydraulic system according to the invention in the operating situation of the apparatus, the pistons being in contact with the cam; Figure 2 is a view similar to Figure 1, showing the situation in which the pistons are retracted into the cylinders; and - Figure 3 is a view similar to Figure 1, showing an alternative embodiment. Figure 1 shows a hydraulic system comprising a housing 10 in which is disposed a hydraulic apparatus 12, a shaft 14 10 engaged in the housing and a sealing device 16 between the shaft and the housing. In this case, the hydraulic apparatus 12 comprises a cylinder block 12A, a cam 12B and a fluid distributor 12C. It is therefore, with the housing, a hydraulic motor or a pump. This apparatus can be in particular a hydraulic motor with radial pistons.
    [0008] In a manner known per se, the cylinders of the cylinder block are supplied with fluid from a fluid dispensed by the distributor, via grooves, some of which are shown and designated by the references 13A and 13B. The distributor is itself connected to main lines 1 and 2, respectively for the supply and exhaust of the hydraulic apparatus. In the present case, the hydraulic apparatus may be of the fixed cylinder-block and rotating casing type, and the supply and exhaust ducts 1 and 2 pass through the shaft 14, in which they are oriented axially, that is to say, parallel to the axis A of rotation of the cylinder block, axis in which the shaft 14 is oriented.
    [0009] The distributor comprises distribution ducts 1 'and 2', which are only primed in the figures, and which, on the one hand, open on the radial face of the distributor facing the shaft 14, so as to be opposite with the ends of the pipes 1 and 2 located at this end of the shaft and which, on the other hand, are connected to the distribution grooves such as the grooves 13A and 13B. The communication between the main ducts 1 and 2 and the distribution ducts 1 'and 2' is sealed with respect to the remainder of the system by any appropriate sealing means, for example by annular seals 1 "and 2" disposed between the faces facing the distributor and the shaft.
    [0010] In this case, another pipe 3 is axially pierced in the shaft. This is a fluid supply line, which serves to bring the fluid to the inner space 11 of the housing, in particular to put this space under pressure so as to promote the decoupling of pistons of the hydraulic apparatus, and to evacuate this fluid when re-interconnecting the pistons. The fluid supplied via the pipe 3 reaches between the faces facing the distributor 12C and the shaft 14 and circulates towards the interior space 11 of the casing, for example by a dedicated connection, or by a clearance provided on a part splines between the shaft 14 and the cylinder block 12A. It can thus be seen that the shaft has only three axial sections 10 of fluid conduit, namely two main sections which form all or part of the main supply and exhaust pipes 1 and 2 and an auxiliary section which forms all or part of of the pipe 3 for pressurizing the crankcase. The cam 12B forms part of the housing 10, which also includes a portion 10A located around the distributor 12C, and a portion 10B forming for example a flange for connection with a member driven by the motor, for example the hub of a wheel. On the opposite side to the hydraulic apparatus 12, the housing is extended by a portion 10C, which may for example be engaged in the hub of a wheel.
    [0011] The housing 10 and the shaft 14 are mounted in relative rotation. For this reason, they cooperate with each other via bearings 18A and 18B, housed in this case in part 10C of the housing. In known manner, these bearings can be bearings with tapered bearings. The system can be used to drive a wheel of a vehicle, in which case the shaft may be the rocket of a wheel. In a manner known per se, the bearings 18a and 18b are lined with grease. These bearings may be associated with closure means called cassette seals, not shown, which are intended to physically maintain the grease in the bearings at the time of assembly operations, or to ensure the cleanliness of the bearings during their transport. Such cassette seals are often incorporated into the bearings when delivered already filled with grease. Said bearings are then designated as "sealed bearings". These seals are often placed between the inner and outer rings of the bearings, which constitute the tracks of the bearings.
    [0012] Sometimes these seals consist of a simple metal washer fitted. Sometimes they comprise a rubber part exerting a slight contact pressure on the rotating part and in a usual way have their friction track formed by one of the bearing rings. However, these casing seals are considered as dust protectors or means for maintaining the grease in the bearing, and can not be considered as seals which are impervious to hydraulic fluid or pressure. The shaft 14 is integral in rotation with the cylinder block 12A, via grooves, in a manner known per se. Thus, the shaft and the cylinder block are in this case two stator elements, while the housing is a rotor element. As can be seen better in the enlarged part of FIG. 1, the sealing device 16 comprises a first sealing element 20 and a second sealing element 22 successively arranged on the shaft 14, an intermediate chamber 24 being arranged between them. The first sealing member 20 is closer to the hydraulic apparatus 12 than the second. The intermediate chamber 24 is drained to prevent overpressure in this chamber. It can indeed be supplied with fluid by leaks that may occur at the first sealing member 20, when the pressure in the interior of the housing 11 20 is high. Indeed, the sealing provided by the first sealing element 20 may be voluntarily lower than that provided by the second sealing element 22. Moreover, as seen in the variant of Figure 3, the first element 20 can be provided with a calibrated nozzle 21 for scanning the interior space of the housing, as shown in the French patent application No. 13 62756. Sealing vis-à-vis the hydraulic fluid under The pressure present in the crankcase 12 is provided by the sealing device 16. Between the sealing device 16 and the bearings 18a and 18b there must be a volume of air which has been trapped during assembly, between these bearings and the cassette joint (s) mentioned above. Throughout the life of the machine or machine including the hydraulic system according to the invention, the hydraulic fluid must not flow beyond the sealing device 16, in the direction of the bearings. If such a flow occurs, it means that the machine is destroyed, or badly assembled. In other words, there is no passage of the hydraulic fluid from the housing 12 to the bearings 18a and 18b. The system has a connection between the intermediate chamber 24 and the main pipe 1. In this case, this connection comprises a bore 26 of the shaft 14, this bore being oriented radially and extending between the intermediate chamber 24 and the pipe main 1. In this case, the system comprises a friction ring 28 which is mounted tight on the shaft 14 and which has an outer race with which the sealing elements 20 and 22 cooperate. Thus, part of this outer track 28A delimits the intermediate chamber 24 on the side of the shaft. This ring has a bore 28B which communicates with the bore 26 of the shaft 14. The connection between the intermediate chamber 24 and the pipe 1 therefore comprises in this case the bore 28B and the bore 26. However, it should be noted that the friction ring is present only according to an alternative embodiment. Indeed, if the cylindrical surface of the shaft is of sufficient quality, this surface itself directly acts as a friction track. This link is equipped with a check valve 30 which only allows the flow of fluid in the direction S from the intermediate chamber 24 to the main pipe 1. The check valve 30 comprises a jacket 32 which has a seat surface 32A rotated to the shaft, and a valve stem 34 movable in the sleeve. This rod comprises a sealing head 34A cooperating with the seat surface, and a pressure head 34B, for example formed by a circlip, located opposite the head 34A and a surface facing the intermediate chamber 24, receives the fluid pressure in this chamber. A return spring 36 is disposed between an abutment surface of the liner 32 and an abutment surface of the rod opposite the chamber 24, for example formed by a shoulder of the pressure head 34B opposite the chamber 24. In FIG. In this case, the non-return valve 30 is disposed in the bore 26 of the shaft 14. This valve could, however, be disposed in the bore 28B of the friction ring 28. The spring 36 can be defined so that the valve 30 is calibrated at a pressure of the order of 3 bar, so that it opens only when the pressure in the intermediate chamber 24 is at least 3 bar higher than the pressure in the pipe 1. For example the first sealing element 20 may be designed to leak from a pressure difference of 1 bar between the intermediate chamber 24 and the interior space of the housing 11. In the particular case where the hydraulic apparatus is of the type with declivable pistons, it is possible to a pressure of about 3 to 5 bar prevails in the interior space of the casing 11 to disengage the pistons, by supplying fluid through line 3. In this situation of inactivity of the hydraulic apparatus, and in particular also during the short time when the deactivated situation is changed to the activated situation, while the pressure in the inner space of the casing increases when the pistons are retracted, the first sealing element 20 leaks so that the pressure In the intermediate chamber 24. When this pressure reaches 3 bar, the check valve 30 opens to unload this chamber. If the device is in a deactivated situation, line 1 is at low pressure. At the moment (which is a short time) when going from the deactivated situation to the activated situation, the supply pressure is established in line 2, but has not yet established in line 1. Thus it is still possible to obtain the opening of the check valve 30, at the very moment when the pistons, pushed by the pressure established in the pipe 1, come out of the cylinders to come into contact with the cam, which creates a decrease in the volume. contained in the interior space of the housing 11, and can create a temporary peak pressure in said interior space. Thus, the second sealing member 22 is protected against excess pressure and fully plays its role of sealing between the inner space 11 of the housing and the bearings 18A and 18B. When the apparatus is in operation, the pistons being clutched, the pressure in the main pipe 1 is normally at least of the order of the boost pressure. The pipe 1 is preferably the main exhaust pipe, that is to say it serves for the exhaust in the preferred direction of operation of the hydraulic apparatus (forward). The pressure in the interior space of the casing 11 remains otherwise low, being generally less than the pressure of 3 to 5 bar used for the declutching of the pistons, the fluid does not enter the intermediate chamber 20 from the pipe 1. It is also noted that when the hydraulic apparatus is in operation, line 1 may serve to drain the interior space of the housing, so that the fluid pressure in this interior space is low. Line 1 can in this operating mode be connected to a tank at atmospheric pressure or at a similar pressure. However, it may be chosen that the pipe 1 which is connected to the chamber 24 via the link 26, 28 is the feed pipe of the hydraulic apparatus, in which case, when the hydraulic apparatus is of the radial piston hydraulic motor type, the pressure in this pipe can reach 450 bar. This being so, as indicated above, it is advantageous for this line 1 to be the pipe which, in the preferred direction of operation of the apparatus, serves the exhaust. Even if it is the exhaust pipe, the pressure in this pipe during operation of the hydraulic apparatus is generally of the order of 20 bar, and remains greater than the pressure in the interior space 11 of the so that, even in this case, the fluid does not penetrate the main pipe to the intermediate chamber 24. Thus, when the hydraulic apparatus is two-way operation, the pipes 1 and 2 alternately playing the role main supply line and main exhaust pipe, the pressure in the intermediate chamber remains low enough that the second sealing member 22 plays its role. When the hydraulic apparatus is activated after a deactivation phase, it is possible to connect the pipe 3 to a tank at atmospheric pressure or to a similar pressure in order to drain the interior space of the housing and to reduce the pressure in this case. space, before putting the pipes 1 and 2 under pressure, this to avoid any overpressure in the chamber 24. FIG. 1 shows the circulation of fluid in the operating situation of the apparatus, the pistons being in contact with the cam and the apparatus functioning in its preferential sense. The bold arrows in lines 1 and 2 show that these lines serve respectively for exhaust and for feeding. Figure 2 shows the situation while the pistons are declutched, that is to say that they are retracted into the cylinders, without being in contact with the cam. It can be seen that the pipe 3 then serves to hold the inner space of the casing 11 under pressure. Under the effect of the increase of this pressure which occurs during the re-interconnection of the pistons (their exit for their implementation). contact with the cam), leakage may occur at the first sealing member, as indicated by the arrow f1 in the enlarged portion of the figure. In this case, the pressure in the intermediate chamber 24 becoming greater than the pressure in the pipe 1, the valve stem 34 comes off its seat and the fluid flows towards the pipe 1, as indicated by the arrows f2. The system shown in FIG. 3 is similar to that of FIGS. 1 and 2, except that the first sealing element 22 comprises a calibrated nozzle 21 which organizes a permanent leak between the interior of the housing and the intermediate chamber. 24.The system according to the invention operates in combination with a feed / exhaust system using the three lines 1, 2 and 3 in a particular way: in the activated mode, the lines 1 and 2 are the main lines of escape and supplying the hydraulic apparatus while pipe 3 is a drain line connected to a tank at atmospheric pressure or at a nearby pressure; on the other hand, in a deactivated mode, the pipes 1 and 2 are connected to a tank at atmospheric pressure or at a similar pressure, whereas the pipe 3 is connected to a releasing pressure of the order of 3 to 5 bar. in the interior space of the housing 11 for disengaging the pistons, by supply of fluid through the pipe 3. During the interconnection of the pistons, that is to say during the short time when the supply pipe 1 rises in pressure and When the pistons come out of the cylinders to come into contact with the cam, the peak of crankcase pressure can be discharged towards the pipe 1 which does not rise to a significant pressure, until all the pistons have come out and rest on the cam 12B .. In non-activated mode, the pistons being declutched, the low permanent pressure in the housing 11 creates a leak either by the first sealing member 20, or by the calibrated nozzle 21 (Figure 30 3 ). This leak is evacuated via the chamber 24 to the pipe 1. The fact that the pipe 1 is not pressurized in this operating mode allows to evacuate this flow without adding additional drain line in the shaft, and thus avoids weakening the tree. This leakage allows a sweep of the oil contained in the housing and in the sealing device 16. This sweeping allows the rinsing and cooling of the hydraulic components and the sealing device 16. This sweeping is useful when the The system is deactivated and the shaft rotates at high speed, or the proximity of an external member such as a brake sends a heat flux to the system. This is particularly the case when the hydraulic apparatus is a hydraulic assist motor for driving a wheel of a vehicle, this motor being active in a work situation and being inactive in road traffic situation. The clutch pressure can be used for safety in parallel with other means for returning pistons in a declutched mode, such as return springs or magnets.
    [0013] It should be noted that the valves necessary for connecting the various lines to the hydraulic power supply are not shown in the figures which have just been described.
    权利要求:
    Claims (12)
    [0001]
    REVENDICATIONS1. Hydraulic system comprising a housing (10) in which a hydraulic apparatus (12) is arranged, main ducts (1,
    [0002]
    2) for feeding and exhausting the hydraulic apparatus, a shaft (14) engaged in the housing, and a sealing device (16) between the shaft and the housing, the sealing device (16) ) comprising a first and a second sealing element (20, 22) successively arranged on the shaft while providing between them an intermediate chamber (24), characterized in that it has a connection (26, 28B) between the chamber intermediate (24) and one (1) of the main lines, this link being equipped with a check valve (30) allowing only the flow of fluid in the direction from the intermediate chamber (24) to said one of the main pipes (1). 2. System according to claim 1, characterized in that said at least one of the main ducts (1, 2), optionally each of the two main ducts, comprises a section which passes into the shaft (14), and the connection comprises a drilling (26) of the shaft (14) extending between the intermediate chamber (24) and said section (1).
    [0003]
    3. System according to claim 2, characterized in that the bore (26) of the shaft (14) is oriented radially.
    [0004]
    4. System according to claim 2 or 3, characterized in that the non-return valve (30) is disposed in the bore (26) of the shaft (14).
    [0005]
    5. System according to any one of claims 1 to 4, characterized in that it comprises a friction ring (28) mounted tightly on the shaft and having an outer race with which cooperates at least one of the elements d sealing (20, 22), and in that the connection comprises a bore (28B) of the friction ring (28).
    [0006]
    6. System according to claim 5, taken in combination with any one of claims 1 to 3, characterized in that the non-return valve (30) is disposed in the bore of the friction ring (28).
    [0007]
    7. System according to any one of claims 1 to 6, characterized in that said one (1) of the main ducts is the exhaust duct of the hydraulic apparatus (12) in the preferred direction of operation of said apparatus. 3037354 15
    [0008]
    8. System according to any one of claims 1 to 7, characterized in that the non-return valve (30) is a valve calibrated at a setting pressure which is advantageously of the order of 3 bar.
    [0009]
    9. System according to any one of claims 1 to 8, characterized in that the hydraulic apparatus (12) comprises a cylinder block (12A), a cam (12B) and a fluid distributor (12C).
    [0010]
    10. System according to any one of claims 1 to 9, characterized in that it forms a drive system of a wheel of a vehicle and in that the shaft (14) forms the rocket of the wheel . 10
    [0011]
    11. System according to any one of claims 1 to 10, characterized in that the shaft (14) has only three axial sections of fluid lines, namely two main sections (1, 2) respectively forming at least a part the main supply line and at least a part of the main exhaust pipe, and an auxiliary section (3) for supplying the interior space of the housing with fluid under pressure.
    [0012]
    12. System according to any one of claims 1 to 11, characterized in that the first sealing element (20) is provided with a calibrated nozzle (21) for scanning the internal space of the housing 20 (11). ).
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    同族专利:
    公开号 | 公开日
    WO2016198793A1|2016-12-15|
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    EP3308026B1|2020-10-07|
    EP3308026A1|2018-04-18|
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    FR2967228A1|2011-12-21|2012-05-11|Poclain Hydraulics Ind|Lubricating fluid e.g. oil, evacuation system for e.g. vehicle's hydraulic motor, has discharge chamber coupled to drain via conduit placed on shaft surface to evacuate fluid in chamber so that chamber is not subjected to pressure in casing|WO2019058058A1|2017-09-22|2019-03-28|Poclain Hydraulics Industrie|Supply unit for at least one hydraulic machine|US2481754A|1946-07-27|1949-09-13|Caterpillar Tractor Co|Pump|
    FR1362756A|1962-05-18|1964-06-05|Thomson Houston Comp Francaise|Current limiting circuit breaker|
    DE1528416C3|1965-12-08|1975-07-31|Fuerstlich Hohenzollernsche Huettenverwaltung Laucherthal, 7481 Laucherthal|Radial piston machine with pistons arranged in a star shape|
    WO1983002482A1|1982-01-19|1983-07-21|Christian Helmut Thoma|Hydraulic radial piston machines|
    DE68905659T2|1988-05-19|1993-09-23|Bruno Giamello|HYDRAULIC RADIAL PISTON ENGINE WITH CHANGEABLE LIFT VOLUME.|
    US5769611A|1996-09-06|1998-06-23|Stanadyne Automotive Corp.|Hydraulic pressure supply pump with multiple sequential plungers|
    FR3014940B1|2013-12-17|2016-01-15|Poclain Hydraulics Ind|HYDRAULIC SYSTEM WITH DRAIN CARTER|EP3376033B1|2017-03-14|2020-11-25|Leybold GmbH|Lubricant-sealed vacuum pump|
    FR3066789B1|2017-05-24|2020-12-04|Poclain Hydraulics Ind|HYDRAULIC UNIT INCLUDING AN IMPROVED DISTRIBUTOR|
    法律状态:
    2016-06-27| PLFP| Fee payment|Year of fee payment: 2 |
    2016-12-16| PLSC| Search report ready|Effective date: 20161216 |
    2017-06-28| PLFP| Fee payment|Year of fee payment: 3 |
    2018-06-25| PLFP| Fee payment|Year of fee payment: 4 |
    2020-06-25| PLFP| Fee payment|Year of fee payment: 6 |
    2021-06-23| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1555358A|FR3037354B1|2015-06-12|2015-06-12|HYDRAULIC SYSTEM WITH DRAINED CHAMBER|
    FR1555358|2015-06-12|FR1555358A| FR3037354B1|2015-06-12|2015-06-12|HYDRAULIC SYSTEM WITH DRAINED CHAMBER|
    PCT/FR2016/051385| WO2016198793A1|2015-06-12|2016-06-09|Drained-chamber hydraulic system|
    EP16734436.5A| EP3308026B1|2015-06-12|2016-06-09|Drained-chamber hydraulic system|
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