阅读说明：本技术 泵滑动轴承的轴向泄压 (Axial pressure relief for pump slide bearings ) 是由 C·韦尔特 U·梅尼格 于 2021-06-23 设计创作，主要内容包括：本发明涉及一种泵,包括：带有转子(4)的驱动轴(10)；第一壳体部件(20)和第二壳体部件(30),在所述第一壳体部件(20)和第二壳体部件(30)之间形成泵室(50),所述转子(4)设置在泵室(50)中；旋转轴承(22),驱动轴(10)通过所述旋转轴承(22)围绕其旋转轴(D)可转动地安装在第一壳体部件(20)上；以及带有第一开口(12)和第二开口(13)的通道(11),其中,所述旋转轴承(22)设置在泵室(50)和第一开口(12)之间,并且带有第二开口(13)的通道(11)通向第二壳体部件(30)的背离泵室(50)的一侧。(The invention relates to a pump comprising: a drive shaft (10) with a rotor (4); a first housing member (20) and a second housing member (30), a pump chamber (50) being formed between the first housing member (20) and the second housing member (30), the rotor (4) being disposed in the pump chamber (50); a rotary bearing (22), by means of which rotary bearing (22) the drive shaft (10) is rotatably mounted on the first housing part (20) about its axis of rotation (D); and a passage (11) with a first opening (12) and a second opening (13), wherein the rotary bearing (22) is arranged between the pump chamber (50) and the first opening (12), and the passage (11) with the second opening (13) opens into a side of the second housing part (30) facing away from the pump chamber (50).)

1. A pump, the pump comprising:

a drive shaft (10), the drive shaft (10) having a rotor (4),

a first housing member (20) and a second housing member (30), a pump chamber (50) being formed between the first housing member (20) and the second housing member (30), the rotor (4) being disposed in the pump chamber (50),

a rotary bearing (22) by means of which the drive shaft (10) is rotatably mounted on the first housing part (20) about its axis of rotation (D), and

a channel (11), the channel (11) having a first opening (12) and a second opening (13),

wherein the swivel bearing (22) is arranged between the pump chamber (50) and the first opening (12), and the passage (11) with the second opening (13) opens into a side of the second housing part (30) facing away from the pump chamber (50).

2. Pump according to claim 1, wherein the second housing part (30) is a mounting plate and/or has a fixing flange (31) for fixing the second housing part (30) to a containment housing (100).

3. The pump according to any one of the preceding claims, wherein the drive shaft (10) has the passage (11), the passage (11) having the first opening (12) and the second opening (13).

4. Pump according to claim 1 or 2, wherein at least one of the first housing part (20), the second housing part (30), a contour ring (2) or a positioning element (6) has the channel (11) or a part of the channel (11), wherein preferably the first housing part (20) has the first opening (12) and the second housing part (30) or the positioning element (6) has the second opening (13).

5. Pump according to any one of the preceding claims, further comprising a cavity (21), said cavity (21) being located between the bottom of the blind hole formed by the first housing part (20) and the first end of a drive shaft (10) provided in the first housing part (20), wherein the first opening (12) of the passage (11) opens into the cavity (21), wherein preferably the first rotational bearing (12) is provided between the pump chamber (50) and the cavity (21).

6. Pump according to any one of the preceding claims, wherein the second opening (13) opens into the surrounding environment of the pump or pump insert (1), in particular outside a receiving cavity (102) of a receiving housing (100) receiving the pump insert (1).

7. Pump according to any of the preceding claims, wherein the drive shaft (10) is located on a side of the second housing part (30) facing away from the pump chamber (50), the drive shaft (10) having a connection structure (15) adapted to be connected with a hub.

8. Pump according to any one of the preceding claims, wherein a peripheral environment or discharge chamber (55) of the pump or of the pump insert part (1) is formed on a side of the second housing part (30) facing away from the pump chamber (50), wherein the peripheral environment or discharge chamber (55) is adapted to accommodate the hub which can be connected with the connecting structure (15), wherein the channel (11) with the second opening (13) opens into the peripheral environment or discharge chamber (55).

9. Pump according to any one of the preceding claims, wherein the discharge chamber (55) is connected to a reserve tank or suction side, in particular a suction chamber (101) of the pump for storing the fluid returning from the discharge chamber (55).

10. The pump according to any one of the preceding claims, wherein the discharge chamber (55) is open to the atmosphere, such that during operation of the pump, atmospheric pressure is present in the discharge chamber (55).

11. Pump according to any of the preceding claims, wherein the pump is a multi-stroke pump, in particular a two-stroke pump and/or a multi-channel pump, in particular a two-channel pump.

12. Pump according to one of the preceding claims, further comprising a first pressure chamber and a second pressure chamber, wherein the pump chamber (50) is connected to the first pressure chamber via a first discharge channel and to the second pressure chamber via a second discharge channel, wherein the first pressure chamber and the second pressure chamber are sealed relative to each other, wherein preferably the first pressure chamber and/or the second pressure chamber are formed between a front wall (103) of the receiving chamber (102) and the first housing part (20), and/or a suction chamber (101) is formed between a peripheral wall (104) of the receiving chamber (102) and the pump insert part (1) or the contour ring (2).

13. Pump according to any one of the preceding claims, further comprising a second rotary bearing (32), by means of which second rotary bearing (32) the drive shaft (10) is rotatably mounted on the second housing part (30) about its rotational axis (D), and a shaft seal (33), wherein the second rotary bearing (32) is arranged between the shaft seal (33) and the pump chamber (50).

14. Pump according to any of the preceding claims, wherein the drive shaft (10) with the rotor (4) and the first and second housing parts (20, 30) are integral parts of a pump insert part (1), the pump insert part (1) being placeable or insertable as a unit in a receiving cavity (102) formed by a receiving housing (100).

15. Transmission comprising a transmission housing and a drive shaft which is connected via a drive element to a drive shaft (10) of a pump according to one of the preceding claims in such a way that a rotation of the drive shaft brings about a rotation of the drive shaft (10), wherein the transmission housing encloses a discharge chamber (55) and/or forms a receiving chamber (102), wherein preferably the pump has a pump insert part (1) arranged in the receiving chamber (102), wherein the receiving chamber (102) is sealed off from the surroundings or from the discharge chamber (55).

Technical Field

The invention relates to a pump, in particular an axial pressure relief in a plain bearing of an oil pump, via a channel in the pump housing and/or the pump shaft or the drive shaft, which channel can be designed, for example, as a central bore in the pump shaft or the drive shaft. The invention further relates to a pump, such as a lubricant pump, a coolant pump, a transmission pump or a vacuum pump, having such a pressure relief device. The pump may be a single-or multi-channel pump and/or a single-or multi-stroke pump, in particular a single-or multi-circuit pump. It may be used as a transmission pump for supplying pressurized fluid to a transmission, such as an automatic or steering transmission, a transmission of a vehicle or a wind turbine. It can also be used as a lubricating oil and/or coolant pump for supplying a lubricant and/or coolant, in particular lubricating oil, to an internal combustion engine, for example a drive motor of a vehicle. Combinations thereof for the lubricating oil pump and the transmission pump are also conceivable, in particular in the case of a multi-channel pump. Advantageously, the pump is designed as a cartridge-type structure. Therefore, it may have a pump insertion part that can be placed or inserted as a unit into the accommodation chamber formed by the accommodation case. Furthermore, the pump may be used for lubricating and/or cooling an electric motor, for example constituting a drive motor or an auxiliary drive motor of a motor vehicle.

Background

For oil pumps, in particular double stroke vane pumps, for example mounted in automatic and double clutch transmissions, the pump shaft is usually supported by sliding bearings for space and cost reasons. When using such a sliding bearing, depending on the bearing load to be borne during operation, it is not necessary to additionally support the shaft using bearing bushes made of the same material as the bearing bores, or if the bearing load is high and there is a risk of mixed friction during operation, it is possible to support the shaft using separate bearing bushes made of a bearing material suitable for the present case. In particular, in the case of pumps with high pressure levels, up to several tens of bars, and without the pump shaft protruding from the sides of the pump housing, special requirements are imposed on the pump design, since the end faces of the drive shaft and of the rotor are subjected to different pump operating pressures, which generate a great axial thrust which, according to the chosen axial bearing concept, must be supported by the pump shaft or by the rotor of the pump. The axial thrust generates a friction torque which causes wear of the respective bearing surfaces and increases the driving power of the pump, thereby reducing the working efficiency of the pump. In order to minimize the axial thrust of the end face of the pump shaft which is subjected to the operating pressure, the bearing bore of the pump shaft is usually designed as a blind bore and faces away from the drive side, for example, by connecting the bearing bore of the pump shaft to the intake region of the pump via an inclined pressure relief bore. One disadvantage of such a solution is that the inclined relief holes in the slide bearing result in a burred sipe geometry which can only be removed with considerable effort in mass production, with the risk of the burr folding or forming a new burr. In spite of the relatively complex deburring process, for example by means of ball mills, the burrs turned out or new burrs can disappear during operation of the pump and lead to oil circulation processes, for example, operational disturbances in the control block of the gearbox. Since the radial forces generated by the sliding bearing to be absorbed may change significantly during operation, particularly in the case of a two-circuit pump, the above-mentioned pressure relief opening to the intake region also actually reduces the bearing capacity of the bearing, since in the region of the cylindrical jacket around the groove geometry of the pressure relief opening, it is almost impossible to develop a significant pressure. Furthermore, the freedom of design and machining techniques for determining the optimum physical angular positioning of the relief hole opening in the plain bearing is often limited.

In german patent application 102019132729.6, a pump is known which is equipped with a drive shaft, the end of which facing away from the drive side is fixed in a bearing bore which is designed as a blind bore in a housing part formed by a pressure plate. The drive shaft is mounted on the platen by a slide bearing. A gap is formed between the wall formed by the pressure plate (the bottom of the blind hole) and the end of the drive shaft mounted on the pressure plate. If no pressure relief is provided for this gap, pressure will build up in the gap when the pump is running, thereby exerting an axial thrust on the drive shaft.

Disclosure of Invention

It is an object of the present invention to provide a pump which is easy to manufacture in a low cost, high volume production process to reduce or avoid axial thrust forces generated during operation of the pump.

This object is achieved by a pump having the features of claim 1. Advantageous developments are provided in the respective claims, the description and the drawings.

The invention is based on a pump, in particular a vane pump. The pump may be designed as a plug-in pump or as a plug-in pump. The insertion part of the pump can be placed or inserted as a unit in its entirety into a receiving chamber formed by the receiving housing, for example a pot-shaped chamber.

The pump includes a drive shaft with a rotor, which may also be referred to as a pump shaft. The rotor may be formed by the drive shaft or, more preferably, may be non-rotatably connected to the drive shaft about its axis of rotation, for example by means of a hub connection. Thus, rotation of the drive shaft about its axis of rotation causes rotation of the rotor about said axis of rotation.

The pump further comprises a first housing part and a second housing part, between which a pump chamber is formed, in which the rotor is arranged. The first and second housing members restrict the direction of the pump chamber toward the rotation shaft. For example, the first housing part can be designed as a pressure plate which comprises at least one outlet channel or in which at least one outlet channel is formed. For example, the second housing part may be formed as a mounting plate, which may be connected or connected to a receiving housing. The second housing part or mounting plate can be a fixing device, in particular a fixing flange, for fixing the second housing part to the receiving housing. For example, the fastening flange or the second housing part can be fastened or screwed to the receiving housing, usually by means of at least one bolt. For example, the fixing flange may be clamped between the head of the bolt and the accommodating housing.

The pump chamber may be circumferentially surrounded by a contoured ring. In particular, the inner circumferential surface of the profile ring may form an inner profile and circumferentially define the pump chamber. The contour ring may be enclosed as a separate part between the first and second housing parts. Alternatively, the contour ring may be integral with the first housing part or with the second housing part.

The rotor may have a groove, in particular a guide groove, such as a slotted groove or a guide groove, in which a conveying element, such as a vane, a slide valve or a pulley, is accommodated so as to be movable, in particular displaceable, in radial direction relative to the axis of rotation. The conveying elements are received or supported by the rotor such that they rotate with the rotor about its axis of rotation. In particular, each transport element is movably arranged with its guide rail in a single degree of freedom.

The first housing part, the second housing part and the contour ring can therefore enclose or delimit a pump chamber in which the rotor and the conveying element are arranged. At least one delivery chamber can be formed radially between the contour ring and the rotor, which is enclosed between the first housing part and the second housing part and can be rotated, for example, a first delivery chamber and a second delivery chamber of a two-stroke pump or a two-channel pump.

Between adjacent conveying elements, a conveying chamber is formed, which is surrounded by the inner circumferential surface of the contour ring and is bounded in the direction of the axis of rotation by one side of the first housing part and the other side of the second housing part, the volume of which varies depending on the rotational position of the rotor about the axis of rotation. The pump has a plurality of conveying elements and an equal number of conveying units are formed between the conveying elements.

The inner circumference of the profile ring has a profile along which the transport element slides when the rotor rotates. In particular, the design of the profile ensures that, due to the rotation of the rotor, the volume will first become larger with the transport unit, which is moved by the transport chamber, and then subsequently decrease. When the rotor is fully rotated, the transport element is moved away from the axis of rotation and in the direction of the axis of rotation at least once. For example, the pump may have a two-stroke and/or two-channel design, i.e. a first delivery chamber and a second delivery chamber, each passing once by the delivery element or in the delivery unit during a full rotation. This means that during a complete rotation the transport element is alternately moved away from the axis of rotation twice and towards the direction of the axis of rotation twice. During the rotation of the rotor, the volume of the delivery unit increases first and then decreases.

The pump or the pump insert part can have at least one inlet channel to the region of the delivery chamber in which the volume of the delivery unit is increased, and at least one outlet channel to the region of the delivery chamber in which the volume of the delivery unit is reduced. Since the volume of the delivery unit becomes large, at least one inlet passage is required as an intake passage. Due to the reduced volume, at least one discharge channel is required as a pressure channel. For example, a single-stroke pump may be provided with one inlet passage and one discharge passage. For another example, a two-stroke pump or a two-channel pump can be provided with an inlet channel common to the first delivery chamber and the second delivery chamber and a first discharge channel for the first delivery chamber and a separate second discharge channel for the second delivery chamber. Alternatively, the pump insert can be equipped with a first inlet channel for the first delivery chamber and a separate second inlet channel for the second delivery chamber, and a first discharge channel for the first delivery chamber and a separate second discharge channel for the second delivery chamber, or with a common discharge channel for the first delivery chamber and the second delivery chamber. For example, the fluid delivered via the first delivery chamber may be used to supply other consumers or the same consumers as the fluid delivered via the second delivery chamber. When different consumers are supplied, different pressure levels can occur between a first discharge channel, which leads to the first pressure chamber, and a second discharge channel, which leads to the second pressure chamber, or between the first pressure chamber and the second pressure chamber. The conveying element and/or the rotor form a sealed gap with the first housing part and the second housing part, respectively. The at least one inlet passage may be connected or to be connected to a fluid storage reservoir, such as a reservoir, and a transmission in fluid communicating connection. For example, the at least one suction channel may lead to a suction chamber, which may be formed between the receiving housing and the pump insert part, for example between an inner wall of the receiving housing and the pump insert part, such as a contour ring. The at least one discharge channel may be connected to at least one fluid consumer, such as a transmission in fluid communication connection. At least one outlet channel, in particular at least two outlet channels, can open into one opening in each case on the side of the first housing part facing away from the pump chamber.

The pump may be equipped with a pivot bearing, in particular a slide bearing, by means of which the drive shaft is rotatably arranged on the first housing part about its axis of rotation. Further, the sliding bearing may be the first housing part or a bearing bush inserted into the first housing part. Alternatively, the pump can be equipped with a second rotary bearing, by means of which the drive shaft is rotatably arranged on the second housing part about its axis of rotation. For example, the second rotary bearing as a plain bearing can be a second housing part or a bearing bush inserted into the second housing part.

In an embodiment, the drive shaft may have a particularly long channel extending along the axis of rotation of the drive shaft. For example, the channel can be designed as a bore. The channel has a first opening and a second opening. The first rotary bearing is located between the pump chamber and the first opening. In particular, the first rotary bearing is positioned or disposed in the first housing part between the end of the drive shaft and the pump chamber. This ensures that no pressure builds up in front of the first opening or in front of the end of the drive shaft provided in the first housing part, since the pressure has been reduced by the passage. For example, fluid or so-called leakage fluid can flow from the pump chamber through the first rotary bearing into the region, in particular the cavity or gap, in front of the first opening, possibly creating pressure if the shaft has no passage. The leaking liquid may be drained or the pressure may be released through the channel.

In an alternative embodiment, at least one of the first housing part, the second housing part, the contour ring or the positioning element has said passage or feature, whereby the first and second housing parts and optionally the contour ring can be positioned relative to each other about the rotational axis of the drive shaft. For example, the first housing part can be provided with a first opening and the second housing part or the positioning element with a second opening. The first opening may open into an area, in particular a cavity or a gap, located in the first housing part in front of the end of the drive shaft. For example, fluid or leakage fluid may flow from the pump chamber through the first slew bearing into the region of the cavity or gap, thereby creating pressure without a pressure relief passage. The leaking liquid may be drained or the pressure may be released through the channel.

Preferably, the channel is designed as a bleed channel or a bleed channel. Preferably, the channel with the first opening is connected in a fluid-tight manner with an area in the first housing part in front of the end of the drive shaft, in particular a cavity or a gap. The first opening is formed in the drive shaft, in particular at the end of the drive shaft in the first housing part.

For example, the passage with the second opening may open into a side of the second housing part facing away from the pump chamber. The leakage fluid can thereby be discharged to the side of the second housing part facing away from the pump chamber. Alternatively, the channel with the second opening can open into the discharge chamber or into the surroundings of the pump insert part outside the receiving chamber of the receiving housing. In particular, in the case of a pump designed as a cartridge, the pump insert part can be or is to be arranged in the receiving space. Preferably, the channel and its second opening are connected in fluid connection with the discharge chamber or the surroundings of the pump or the pump insert. The pump shaft or drive shaft preferably projects axially from the second housing part. The second opening is formed in the drive shaft, in particular at the end of the drive shaft that protrudes axially from the second housing part.

Preferably, the channel extends from its first opening to its second opening. Further, the first and/or second rotational bearing is axially distributed between the first and second opening of the passage. The pump chambers can preferably be distributed axially between the first and second openings of the passage.

For example, the pump may comprise a cavity, e.g. gap-shaped, cylindrical or conical, between the bottom of the blind hole formed by the first housing part (also referred to as seat) and the first end of the drive shaft arranged in the first housing part, in particular in the blind hole. The first opening of the channel opens into the cavity. Thus, the first housing part, in particular at least one inner surface of the blind hole, may circumferentially and/or frontally enclose and define a cavity. The first end of the drive shaft may also define a cavity. The bottom of the blind hole can be designed, for example, as a flat or conical surface. The bottom and first end of the drive shaft are opposite each other.

Preferably, the first rotational bearing is disposed between the pump chamber and the cavity. In this way, leakage fluid can flow from the pump chamber to the first rotary bearing and into the cavity, be discharged through the first opening, the passage, in particular the second opening. This prevents axial thrust from being exerted on the drive shaft due to pressure in the cavity.

Thus, the channel is used as a pressure relief channel. As already mentioned, the structural form of the channel can be designed as a bore in the drive shaft, in particular as a centrally distributed bore. For example, the channel may be designed to be stepped one or more times about its diameter from one end to the other.

In other constructional forms, the drive shaft on the side of the second housing part facing away from the pump chamber may be provided with connecting structures, for example distributed in the discharge chamber or in the surroundings of the pump or pump insert part, adapted to be connected to corresponding structures of the hub to form a hub connection. In this connection, the drive element with the respective hub is preferably connected to a discharge chamber or to the surroundings of, for example, a pump or a pump insert. The transmission element may be a gear, pinion, pulley or planetary gear or the like. The transmission element of the planetary gear can be a planet carrier, a sun gear or a ring gear. The hub or the drive element can be connected torsionally to the drive shaft about the axis of rotation of the drive shaft, for example by means of a hub connection. Thus, rotation of the drive element about the axis of rotation causes rotation of the drive shaft about the axis of rotation.

Optionally, one or more passages, in particular bores, extending transversely or radially into the axis of rotation or into the longitudinal direction of the axis of rotation, extending along the axis of rotation into the drive shaft, provide pressure relief and/or lubrication of the hub connection.

For example, the pump, and in particular the design of the drive shaft, should ensure that the fluid discharged via the passage is led to the hub connection, through which the hub of the drive element and the drive shaft are connected or about to be connected, on the drive side. This allows the hub connection to be lubricated to prevent wear and/or frictional rusting thereat. For example, the drive shaft may be designed such that fluid discharged via the channel may be transferred to the connecting structure, in particular between the connecting structure and the hub, during operation of the pump. The drive shaft may have one or more bores, which are transverse to the axis of rotation or distributed in the longitudinal direction of the channel, leading to the channel and the connecting structure, so that fluid may flow out of the channel to the connecting structure via the at least one transverse bore.

In other constructions, the design of the drive shaft should ensure that the fluid discharged via the channel or the leakage fluid is led to the hub connection between the drive shaft and the rotor. For example, the drive shaft can have one or more bores transverse to the axis of rotation or distributed in the longitudinal direction of the passage, through which the fluid discharged from the passage is conducted into the hub connection. For example, at least one bore may lead to the passageway and hub connection. Thereby, the shaft hub connection can be lubricated and the occurrence of wear or friction rusting can be prevented.

In other embodiments, the drive shaft can have one or more bores running transversely to the axis of rotation or in the longitudinal direction of the channel and opening out into the outer periphery of the drive shaft and the channel. For example, the at least one bore may open into a region on the outer circumference of the drive shaft, which is located between the pump chamber and the shaft seal, in particular between the radial shaft seal, or between the rotor and the shaft seal. For example, a second rotary bearing may be provided between the shaft seal and the pump chamber, in particular between the radial shaft seal ring and the pump chamber. For example, the shaft seal may be disposed between the second rotary bearing or pump chamber on one side and the ambient environment or discharge chamber or connection structure on the other side. Such a design seals the pump chamber or the second rotational bearing from the surroundings or the discharge chamber. Further, the bore may open into an outer circumferential region of the drive shaft, said region being located between the shaft seal and the second rotary bearing. The bore opening to the area between the rotor or pump chamber and the shaft seal may be vented to relieve the pressure on the radial shaft seal ring, thereby reducing wear on the radial shaft seal ring. In order not to impair or eliminate the sealing effect of the shaft seal caused by such a bore, it is possible to resort to devices such as siphons, siphons or the like. The shaft seal is in particular arranged axially between the first and second openings of the channel and axially between the second rotary bearing and the second opening of the channel.

For example, the discharge chamber should be distributed on the side of the second housing part facing away from the pump chamber, or may be distributed in the surroundings of the pump or pump insert part, wherein the discharge chamber or surroundings are adapted to accommodate the drive element or its hub, which may be connected with the connecting structure.

For example, the aperture to the connecting structure may be a second opening. However, it is preferred to lead the second opening to a second end of the drive shaft, i.e. a second end at the front side of the drive shaft. In addition to the second opening, at least one cross-hole may be provided.

In an embodiment, the discharge chamber or the peripheral area may be connected to a storage container or a suction side, in particular a suction chamber of a pump, to accommodate fluid returning from the discharge chamber or the peripheral area. For example, a passage can be provided from the discharge chamber or the surroundings to the reservoir or the intake chamber. Furthermore, it is preferred that the venting chamber or the surrounding environment is in pressure-balanced communication with the atmosphere during operation of the pump, ensuring that atmospheric pressure or substantially atmospheric pressure prevails in the venting chamber or the surrounding environment during operation of the pump.

For example, the pump can be equipped with a pump insert part which comprises at least the drive shaft with the rotor, the first housing part and the second housing part, preferably also the contour ring. The pump insert can be inserted as a unit into a receptacle, for example, in the form of a pot.

For example, a transmission may be equipped with a pump according to the invention. The transmission may be equipped with a transmission housing and/or a receiving housing. For example, the transmission housing may form a containment housing. The transmission housing may form or enclose a discharge chamber or ambient environment of the pump or pump insert. Thus, the exhaust cavity or ambient environment may be enclosed by the transmission housing. The pressure of the cavity can be relieved through a passage of the cavity surrounded by the transmission, i.e. a vent cavity or a passage of the surrounding environment. A reservoir, in particular an oil sump, can be provided on or in the transmission housing, into which the fluid discharged through the channel can be discharged. For example, the transmission or transmission housing may have a ventilation device, which may allow pressure equalization between the atmosphere and a chamber enclosed by the transmission housing. For example, the transmission may be provided with a drive shaft which is connected to the drive shaft of the pump via a drive element, such that rotation of the drive shaft causes rotation of the drive shaft.

For example, the pump can be equipped with a sealing element which is arranged between the pump insert part, in particular between the second housing part and the receiving housing and seals the receiving chamber, in particular the intake chamber of the pump, from the surroundings or the discharge chamber. Further, the sealing element is axially disposed between the first opening and the second opening of the passage.

As mentioned above, the pump may be a two-stroke pump, in particular a two-channel pump. The first working fluid is supplied by a first pressure chamber and the second working fluid is supplied by a second pressure chamber. For this purpose, the pump chamber, in particular the first delivery chamber, can be connected to a first pressure chamber via a first discharge channel, and the second delivery chamber can be connected to a second pressure chamber via a second discharge channel, the first and second pressure chambers being sealed off from one another. For example, a seal may be provided to seal the first pressure chamber and the second pressure chamber relative to each other. The seal can be arranged between a front wall of a pot-shaped receiving space, which is formed by the receiving housing, for example, and the first housing part. For example, a first seal surrounding the first pressure chamber and a second seal surrounding the second pressure chamber may be provided. The containment housing may be equipped with a discharge slot for a first workflow and a discharge slot for a second workflow. The first discharge groove opens into the first pressure chamber and the second discharge groove opens into the second pressure chamber.

In a further embodiment, the first pressure chamber and/or the second pressure chamber may be located between the front wall of the receiving chamber and the first housing part. Alternatively, the suction chamber may be located between the inner circumferential wall of the receiving chamber and the pump insert part or the profiled ring of the pump insert part.

For example, the pump can be equipped with a sealing element which is arranged in particular between the pump insert part (in particular between the first housing part and the receiving housing) and seals off from the suction chamber of the pressure chamber. Preferably, the sealing element is axially arranged between the first opening and the second opening of the passage.

Drawings

The invention has been described based on embodiments and examples. The structural form will now be described with reference to the accompanying drawings. In this case, the features disclosed each individually and in combination constitute the subject matter of the claims. The drawing shows a cross section of the pump insertion part 1 inserted into the accommodation case 100 along the rotation axis D of the drive shaft 10.

Description of the reference numerals

1-Pump insert

2-profile ring

3-conveying element/impeller

4-rotor

5-spring

6-positioning element

7- (first) sealing element/sealing ring

8- (second) sealing element/sealing ring

9-fixing element

10-drive shaft

11-channel/hole/pressure relief channel

12- (first) opening

13- (second) opening

14-shaft hub connection

15-connecting structure

16-locking element

20-first housing part/pressure plate

21-cavity

22-first rotary bearing

23-Pin

24-Blind hole bottom (bottom)

30-second housing part/mounting plate

31-mounting flange

32-second swivel bearing

33-shaft seal

40-sealing element/flanging seal

50-Pump Chamber

55-exhaust Chamber/ambient Environment

100-containment case

101-suction chamber

102-containing chamber

103-front wall

104-inner peripheral wall

D-axis of rotation

Detailed Description

The pump insert 1 is equipped with a first housing part 20 designed as a pressure plate and a second housing part 30 designed as a mounting structure or mounting plate. The pump chamber 50 is located between the first and second housing parts 20, 30 and is circumferentially surrounded or defined by an inner circumferential surface forming the inner contour of the contour ring 2. The first housing part 20, the second housing part 30 and the contour ring 2 are positioned relative to one another in an angular position about the axis of rotation D by means of pin-shaped positioning elements 6. At least one pin-shaped positioning element 6 is fixed in a hole of the second housing part 30. For example, the positioning element 6 can be pressed, screwed, welded or glued into the second housing part 30. The contour ring 2 and the first housing part 20 each have a passage through which the positioning element 6 extends. Thereby, the first and second housing parts 20, 30 and the contour ring 2 can be positioned or angularly positioned relative to each other about the rotational axis D. Furthermore, the housing parts 2, 20 and 30 can be fixed together by means of the positioning element 6 in order to be able to operate as a unit or as a pump insert part 1.

The front wall 103 delimits the receiving space to the front, and a spring 5 is arranged between the receiving space 102 of the receiving housing 100 and the first housing part 20, so that when the pump insert part 1 is inserted, for example, into the receiving housing 100 in the receiving space 102, the first housing part 20 is preferably pressed against the contour ring 2 and the contour ring 2 is again pressed against the second housing part 30. The spring 5 is supported on the front wall 103 and the first housing part 20 and exerts a force on the first housing part 20, which force is directed away from the front wall 103 along the longitudinal direction of the axis of rotation D or the positioning element 6.

For example, when the pump insertion part 1 is inserted into the accommodation chamber 102, the spring 5 may be inserted as a separate part between the front wall 103 and the pump insertion part 1. However, in the example shown, the spring 5 is fixed on the pump insertion part 1, so that the spring 5 can operate with the pump insertion part 1 as a whole. The spring is thus part of the pump insert 1. As described in german patent application No. 102020116731.8, the spring 5 can be fixed to the pump insert 1.

In the example shown, a first pressure chamber and a second pressure chamber (not shown in the figures) are formed between the front wall 103 of the receiving chamber 102 and the first housing part 20. The pump chamber 50 is connected to the first pressure chamber through a first discharge passage (not shown in the drawings), and is connected to the second pressure chamber through a second discharge passage (not shown in the drawings). The pump shown is thus a two-channel pump, i.e. it generates a first working fluid which is discharged from the pump chamber 50 into the first pressure chamber and a second working fluid which is discharged from the pump chamber 50 into the second pressure chamber. The first pressure chamber and the second pressure chamber are sealed with respect to each other. Thus, it is possible to supply fluid to different fluid consumers or to different supply branches of a common fluid consumer. Furthermore, this may optionally allow different pressure levels to be generated in the first and second pressure chambers.

The first pressure chamber is surrounded or enclosed by a sealing element arranged between the front wall 103 of the receiving chamber 102 and the first housing part 20. The sealing element is pressed in a sealing manner against the first housing part 20 and the front wall 103.

The second pressure chamber is surrounded or enclosed by a sealing element arranged between the front wall 103 and the first housing part 20. The sealing element is pressed in a sealing manner against the first housing part 20 and the front wall 103.

In the example shown, the first pressure chamber and the second pressure chamber are sealed by a common sealing element 40, preferably a so-called flange seal. In principle, however, separate sealing elements may also be provided for the first pressure chamber and the second pressure chamber, or sealing may be performed in another manner.

Preferably, the sealing element 40 can be firmly fixed to the positioning element 6 or the pump insert part 1, for example by means of bolts screwed into internal threads of the positioning element 6. The sealing element 40 can be designed, for example, as described in german patent applications 102019132729.6 and 102020116731.8.

Between the inner circumferential wall 104 of the receiving chamber 102 and the housing insert part 1, preferably the contour ring 2, a suction chamber 101 is formed, which suction chamber 101 extends annularly around the pump insert part 1 or the contour ring 2. The pump is adapted to deliver fluid from the suction chamber (first working flow) via a first suction channel (not shown in the figures), via the pump chamber 50, preferably a first delivery chamber formed therein, and then through a first discharge channel in the first pressure chamber. Furthermore, the pump is adapted to deliver fluid from the suction chamber 101 via a second suction channel (not shown in the figures), via the pump chamber 50, preferably a second delivery chamber formed in the pump chamber 50, and then through a second discharge channel in the second pressure chamber (second working flow).

The suction chamber 101 is distributed between the first sealing ring 8 and the second sealing ring 7. The sealing ring 8 is located between the peripheral wall 104 of the receiving chamber 102 and the first housing part 20. The first housing part 20 is provided with an annular groove extending around the periphery of the first housing part 20, in which annular groove the sealing ring 8 is arranged. The sealing ring 8 is tightly connected to the inner circumferential wall 104 and the first housing part 20, in particular to the groove bottom of the annular groove. The sealing ring 7 is disposed between the inner peripheral wall 104 and the second housing component 30. The sealing ring 7 is located in an annular groove extending around the outer circumference of the second housing part 30. The sealing ring 7 is tightly connected to the inner circumferential wall 104 and the second housing part 30, in particular to the groove bottom of the annular groove.

The drive shaft 10 (pump shaft) is rotatably arranged on the first housing part 20 about its rotational axis D by means of a first rotary bearing 22. The first rotary bearing is designed as a sliding bearing, for example in a blind hole or a bottom hole, and is arranged on the second housing part 30 by means of a second rotary bearing 32, which is designed as a sliding bearing and is rotatable about the axis of rotation D. The rotor 4 with the conveying element 3 in the pump chamber 50 is torsionally connected or engaged to the drive shaft 10 about the axis of rotation D by means of the hub connection 14, ensuring that in operation the rotor 4 rotates jointly with the drive shaft 10. The rotor 4 has a guide channel in which the conveying elements 3 designed as impellers are distributed. During operation, the conveying element 3 slides along the inner contour or inner circumferential surface of the contour ring 2. Since the pump has a double-flow or double-stroke design, the design of the inner contour should ensure that the impeller 3 moves out of the groove-shaped guide twice and into the groove-shaped recess twice when the rotor 4 is fully rotated.

The drive shaft 10 has a channel 11, which can be used, in particular, as a pressure relief channel. As an alternative to the embodiment shown in the figures, the channel serving as a pressure relief channel can be designed differently, for example, the first housing part 20, the contour ring 2 and/or the positioning element 6 and the second housing part 30 form a channel. The channel 11 has a first opening 12 at a first end of the drive shaft 10, said first opening 12 being located in the first housing part 20, for example in a blind hole, and a second opening 13 at a second end of the drive shaft 10. The first rotational bearing 22 is distributed between the pump chamber 50 and the first opening 12 or the cavity 21. A cavity 21 is formed between the bottom of the blind bore opposite the first end of the drive shaft 10 and the first end of the drive shaft 10. The channel 11 opens into the cavity 21 through its first opening 12. Furthermore, the channel 11 with the second opening 13 opens into a side of the second housing part 30 facing away from the pump chamber 50. This design ensures that pressure fluid, for example so-called leakage fluid, from the pump chamber 50 flows through the first rotary bearing 22 into the cavity 21 and is discharged through the passage 11, for example into the discharge chamber 55, indicated in the figure by the double-dashed line, for example surrounded by a transmission housing which also constitutes the receiving housing 100. In this way, it is achieved that no pressure is generated in the cavity 21, which pressure would exert an axial thrust on the drive shaft 10. Without the passage 11, it is possible to build up pressure in the cavity 21, thereby exerting an axial thrust on the drive shaft 10, resulting in increased friction, increased wear and reduced pump efficiency. By means of the channel 11, wear and friction can be reduced and efficiency increased. The second end of the drive shaft 10 is located in the discharge chamber 55. The drive shaft 10 is provided with a connecting structure 15 on the side of the second housing part 30 facing away from the pump chamber 50. The connection structure 15 is adapted to be connected to a hub (not shown in the figures) of a drive element. The drive member may be a gear, a pinion, a pulley or a gear member such as a planet gear, e.g. a planet carrier. The hub forms a hub connection with the connecting structure 15. The drive element may be connected with a drive shaft of the transmission such that rotation of the drive shaft causes rotation of a drive shaft of the pump.

The hub, and in particular the drive element, may be located or mounted in the discharge chamber 55. The discharge chamber 55 is located on the side of the second housing part 30 facing away from the pump chamber 50. For example, the discharge chamber 55 may be connected by a passage to one or more reservoirs or containers, or to the suction side of a pump, in particular the suction chamber 101 of a pump, to return fluid from the discharge chamber 55. Alternatively, the fluid discharged into the discharge chamber may be discharged into the storage container by gravity, for example, may be lower than the second opening in the gravity direction by the storage container (e.g., a fuel tank), and the second opening 13 and the storage container are connected in fluid communication.

In the exhaust chamber 55, in particular in the chamber enclosed by the transmission housing, preferably atmospheric pressure is used. The passage 11 further allows the pressure in the gap 21 to be the same, or at least substantially the same, as the pressure in the discharge chamber 55, i.e. preferably atmospheric pressure.

A shaft seal 33, in particular a radial shaft seal, is located in the second housing part 30 or on the second housing part 30, sealingly abutting against the drive shaft 10. A shaft seal 33 is located between the second rotary bearing 32 and the connecting structure 15. Alternatively, the second rotary bearing 32 is provided between the pump chamber 50 and the shaft seal 33.

In other embodiments of the embodiment shown in the figures, one or more cross-shaped bores, i.e. bores running transversely to the longitudinal direction of the channel 11 or transversely with respect to the axis of rotation D, can be provided in the drive shaft 10. For example, a cross-hole may be provided in the region of the hub connection 14. The cross bore leads to the hub connection 14 and the passageway 11. Depending on the pressure conditions, leakage fluid flows from the pump chamber 50 into the passage 11 via the hub connection 14 and the cross bore, and from the passage 11 into the discharge chamber 55, so that fretting and wear in the shaft-hub connection can be reduced or prevented. Alternatively, depending on the pressure conditions, leakage fluid can pass from the gap 21 via the passage 11 and the cross bore to the shaft-hub connection 14 via the cross bore.

Alternatively, a cross-bore may be provided between the pump chamber 50 and the shaft seal 33, said cross-bore opening out into the outer circumference of the drive shaft 10 and into the passage 11. For example, the cross-bore may open out into a region on the outer circumference between the position where the second rotary bearing 32 and the shaft seal 33 bear in a sealing manner against the drive shaft 10. This serves both to relieve the pressure on the shaft seal 33 and to increase the flow of leakage fluid from the pump chamber 50 through the second rotary bearing 32, thereby providing better lubrication or cooling of the second rotary bearing 32. The fluid containing the leaked fluid passing through the first slew bearing 22 may also lubricate or cool the first slew bearing 22.

Alternatively, a cross-hole can be provided in the region of the connecting structure 15, said cross-hole leading to the connecting structure 15 and the channel 11. This may result in that leakage liquid discharged through the channel 11 is brought to the connection structure 15 through the transverse bore and thus to the hub connection between the hub of the drive element and the connection structure 15. Thus, wear or fretting rust on the connection structure or hub connection is reduced or even prevented.

The design of the second housing part 30 should ensure that the pump insert part 1 is fastened to the receiving housing 100. The second housing part 30 is provided with a fixing flange 31, said fixing flange 31 having one or more holes so that the second housing part 30 can be fastened to the accommodating housing 100 by means of bolts. In the example shown, the longitudinal direction of the hole in the fixing flange 31 is parallel to the axis of rotation D. The fixing flange 31 is clamped between the head of the bolt screwed into the accommodating case 100 and the accommodating case 100.

The first housing part 20 can optionally be fitted with pins 23 which project from the end face of the first housing part 20 facing away from the pump chamber 50 or the end face facing the front wall 103. The pin 23 may center the sealing element 40. Alternatively, the pin 23 may be used to center the pump insert part 1 or the first housing part 20 in the receiving housing 100. The receiving case 100 may have a hole with an inner circumferential surface on which an outer circumferential surface of the pin 23 is centered.

The receiving housing 100 can be provided with a channel which opens into the first pressure space and through which the first working fluid can flow to the consumer. Furthermore, the receiving housing can also be provided with a passage to the second pressure chamber, through which a second working fluid can flow to the respective fluid consumer.

The rotor 4 and the connecting structure 15 are connected to each other along the axis of rotation D to prevent displacement, for example by means of a locking element 16 designed to be inserted into an axial shaft retaining ring of the drive shaft. The rotor 4 can be distributed or enclosed between the stages of the drive shaft 10 and a locking element 16 fixed on the drive shaft 10.