阅读说明：本技术 用于制冷剂压缩机的润滑剂容纳部 (Lubricant receiving portion for refrigerant compressor ) 是由 H·M·海登博 于 2020-03-11 设计创作，主要内容包括：本发明涉及一种用于借助制冷剂压缩机(3)的曲轴(2)竖直输送润滑剂(15)的润滑剂容纳部(1),该润滑剂容纳部包括：具有净横截面(5)的套筒元件(4)；内部元件(9),其具有外周面(10),外周面沿内部元件(9)的纵轴线(11)从下端部(12)延伸至上端部(13)且在外周面上设置螺旋部(14),该螺旋部从外周面伸出且螺旋状地从外周面下端部的区域延伸至上端部的区域并且局部地限定通道(32),在润滑剂容纳部的运行状态中内部元件以其外周面至少局部地设置在净横截面内。按照本发明,在外周面的上端部的区域中设置至少一个贴靠区段(35),至少一个贴靠区段沿径向伸出超过外周面且其走向不同于螺旋部的螺旋形走向。(The invention relates to a lubricant receiver (1) for vertically conveying lubricant (15) by means of a crankshaft (2) of a refrigerant compressor (3), comprising: a sleeve element (4) having a clear cross-section (5); an inner element (9) having an outer circumferential surface (10) which extends along a longitudinal axis (11) of the inner element (9) from a lower end (12) to an upper end (13) and on which a spiral (14) is arranged which projects from the outer circumferential surface and extends helically from a region of the lower end of the outer circumferential surface to a region of the upper end and which delimits a channel (32) in some regions, the inner element being arranged with its outer circumferential surface at least in some regions in a clear cross section in an operating state of the lubricant reservoir. According to the invention, at least one contact section (35) is provided in the region of the upper end of the outer circumferential surface, which contact section projects radially beyond the outer circumferential surface and has a different course than the spiral course of the spiral.)

1. A lubricant reservoir (1) for the vertical transport of lubricant (15) by means of a crankshaft (2) of a refrigerant compressor (3), comprising a sleeve element (4) having a clear cross section (5) which is delimited by an inner wall (33) and which extends along a longitudinal axis (6) of the sleeve element (4) from an upper end (7) of the sleeve element (4) to a lower end (8) of the sleeve element, the lubricant reservoir (1) further comprising an inner element (9) having an outer circumferential surface (10) which extends along a longitudinal axis (11) of the inner element (9) from a lower end (12) to an upper end (13) and on which a spiral (14) is arranged, which extends from the outer circumferential surface (10) and helically extends from the region of the lower end (12) of the outer circumferential surface (10) to the region of the upper end (13) and delimits the passage (32) locally, wherein, in the operating state of the lubricant container (1)

-the inner element (9) is arranged with its outer circumference (10) at least partially within the clear cross-section (5) of the sleeve element (4) such that a gap (30) is provided between the outer surface (34) and the inner wall (33) of the spiral (14),

-the lower end (12) of the outer circumferential surface (10) is arranged in front of the upper end (13) of the outer circumferential surface, seen in the direction from the lower end (8) to the upper end (7) of the sleeve element (4),

-the inner element (9) and the sleeve element (4) are rotatable relative to one another about the longitudinal axis (6) of the sleeve element (4) and/or the longitudinal axis (11) of the inner element (9), characterized in that at least one abutment section (35) is provided in the region of the upper end (13) of the outer circumferential surface (10), which abutment section projects radially beyond the outer circumferential surface (10) and whose course differs from the helical course of the spiral (14).

2. The lubricant reservoir (1) according to claim 1, characterized in that the at least one contact section (35) is defined by a first boundary surface (40) and a second boundary surface (41) arranged one after the other, as seen along the longitudinal axis (11) of the inner element (9), and the first boundary surface (40) and/or the second boundary surface (41) are perpendicular to the longitudinal axis (11) of the inner element (9).

3. The lubricant reservoir (1) according to one of claims 1 to 2, characterized in that the channel (32) has a reduced channel cross section (42) in the region of the at least one contact section (35).

4. The lubricant reservoir (1) according to any one of claims 1 to 3, characterized in that the spiral (14) is directly connected to the at least one contact section (35).

5. The lubricant reservoir (1) according to any one of claims 1 to 4, characterized in that the at least one abutment section (35) covers an angular range (36) around the longitudinal axis (11) of the inner element (9), which angular range is at least 15 °, preferably at least 45 °, particularly preferably at least 90 °.

6. The lubricant reservoir (1) according to claim 5, characterized in that the angular range (36) is 360 °.

7. The lubricant reservoir (1) according to claim 6, characterized in that the at least one abutment section (35) comprises at least one closed abutment section (37), wherein each closed abutment section (37) covers the entire angular region (36) in each case.

8. The lubricant reservoir (1) according to one of claims 1 to 7, characterized in that exactly one abutment section (35) is provided.

9. The lubricant reservoir (1) according to any one of claims 1 to 8, characterized in that the inner element (9) has a hollow space (38) which is open, viewed along the longitudinal axis (11) of the inner element (9), towards the upper end (13) of the outer circumferential surface (10).

10. The lubricant reservoir (1) according to claim 9, characterized in that at least one outlet opening (39) is provided in the region of the upper end (13) of the outer circumferential surface (10), wherein the at least one outlet opening (39) connects the channel (32) with the hollow space (38).

11. Refrigerant compressor (3) comprising: a sealably enclosed compressor housing (18); an electric drive unit (19) arranged in a housing interior of the compressor housing (18), the electric drive unit comprising a rotor (20) and a stator (21); a crankshaft (2) connected to the rotor (20) so as to be non-rotatable relative thereto; and a piston-cylinder unit (22) arranged in the housing interior, comprising a piston (23) movably supported in a cylinder (24) of the piston-cylinder unit (22), which piston can be driven for compressing the refrigerant of the crankshaft (2),

the refrigerant compressor (3) has a lubricant receiver (1) according to one of claims 1 to 10 in an operating state in order to convey lubricant (15) from a lubricant groove (26) formed in a bottom region (25) of the compressor housing (18) through the crankshaft (2), wherein the crankshaft (2) has a bore (27) which preferably extends at least in some regions at an angle to a rotational axis (29) of the crankshaft (2) and/or at least one groove which is in fluid connection with a clear cross section (5) of the sleeve element (4).

12. Refrigerant compressor (3) according to claim 11, characterized in that the sleeve element (4) of the lubricant receiver (1) is connected non-rotatably to the crankshaft (2).

Technical Field

The invention relates to a lubricant reservoir for the vertical transport of lubricant by means of a crankshaft of a refrigerant compressor, comprising a sleeve element having a clear cross section which is delimited by an inner wall and extends along a longitudinal axis of the sleeve element from an upper end of the sleeve element to a lower end of the sleeve element, and comprising an inner element having an outer circumferential surface which extends along the longitudinal axis of the inner element from the lower end to the upper end and on which a spiral is arranged which protrudes from the outer circumferential surface and extends helically from a region of the lower end of the outer circumferential surface to a region of the upper end and delimits a channel in some regions, wherein, in an operating state of the lubricant reservoir, the lubricant reservoir comprises a sleeve element having a clear cross section which is delimited by an inner wall and which extends from the upper end to the lower end

The outer circumferential surface of the inner element is arranged at least in some regions in the clear cross section of the sleeve element in such a way that a gap is provided between the outer surface and the inner wall of the spiral,

the lower end of the outer circumferential surface is arranged in front of the upper end thereof, seen in the direction from the lower end to the upper end of the sleeve element,

the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element.

Background

A refrigerant compressor includes: a hermetically sealable compressor housing; an electric drive unit disposed in a shell interior of the compressor shell, the electric drive unit including a rotor and a stator; a crankshaft connected to the rotor so as to be non-rotatable relative thereto; and a piston-cylinder unit disposed in the housing interior (the piston-cylinder unit comprising a piston movably supported in a cylinder of the piston-cylinder unit, the piston being drivable for compressing refrigerant of the crankshaft); in this refrigerant compressor, it is important to ensure sufficient lubrication of all movable components. For this purpose, provision can be made for the lubricant which accumulates in a lubricant sump covering the bottom region of the compressor housing to be conveyed by the crankshaft in the direction of the cylinders.

For this purpose, a lubricant receptacle is often provided, which is sleeve-shaped or has a sleeve element, is connected to the crankshaft in a rotationally fixed manner and is arranged coaxially to the crankshaft and projects with an end section into the lubricant groove. The lubricant which enters the cylindrical receiving section of the lubricant receiver from the lubricant groove via the inlet opening is forced into a parabolic shape on account of the rotation of the lubricant receiver as a result of the rotation of the crankshaft, wherein the parabolic shape is formed along an inner wall of the lubricant receiver or sleeve element which delimits the receiving section and along an inner wall of the crankshaft which is hollow or provided with a bore. Such a lubricant receptacle is known, for example, from AT 15828U 1.

The maximum rise height to which the lubricant in the receptacle section of the lubricant receptacle can be raised in this way is achieved in the region of the net inner diameter of the crankshaft or bore and depends on the square of the rotational speed of the lubricant receptacle and the square of the net inner radius of the crankshaft or lubricant receptacle. The lubricant can then be discharged from the crankshaft through at least one outlet opening to the location to be lubricated.

Thus, with a corresponding selection of production parameters (e.g. the clear inner radius of the crankshaft, the height of the outlet openings) and process parameters (e.g. the rotational speed of the crankshaft, the viscosity of the lubricant), it is possible to transport lubricant from the bottom of the compressor housing by means of the lubricant receiver through the crankshaft of the compressor to the bearing locations of the main bearings of the crankshaft, the crank pin and the connecting rod of the refrigerant compressor.

In practice, compressors with variable speed are increasingly used compared to conventional compressors with fixed speed, which have only two states, namely zero speed and typically 3000min^-1The operating rotational speed of (c). In compressors with variable rotational speed, depending on the required cooling capacity, in practice, it is usual to achieve not only high rotational speeds but also low rotational speeds (typically a minimum of 800 min)^-1). In order to achieve a sufficiently large power transmission even at low rotational speeds, it is known from the prior art to provide a cylindrical receiving section in which an inner element, which is open at the bottom and likewise cylindrical, is arranged, so that a gap is produced between the outer circumferential surface of the inner element and the inner wall of the receiving section. The inner element typically has a helical spiral extending from bottom to top on its outer circumferential surface, which spiral can be configured, for example, as a web projecting from the outer circumferential surface. This considerably facilitates the transport of the lubricant, since the lubricant is thus transported not only through the gap but also through the channel formed or delimited by the spiral.

At high rotational speeds, however, this has the disadvantageous effect that, as a result, too much lubricant or oil is then conveyed through the channel, so that more oil is introduced into the gaseous refrigerant, in particular through the suction muffler. However, oil is undesirable in the refrigerant circuit because it limits heat transfer in the condenser and evaporator.

In the solutions described in the prior art, the inner element is basically fixed, typically by being connected to the stator, in such a way that the inner element does not rotate with the crankshaft. It is possible, however, to tilt the longitudinal axis of the sleeve element and the longitudinal axis of the inner element no longer parallel to one another. The inclination is limited by the abutment of the spiral against the inner wall of the sleeve element which defines the receiving section or clear cross section.

An increasingly important requirement of refrigerant compressors is a space-saving design which is as compact as possible. This results in the lubricant receiving portion of such a compact compressor becoming shorter and shorter. The spiral of such a lubricant receiver also fails correspondingly shorter. The latter lubricant receiver, in the case of an unfavorable inclination of the spiral, in turn leads to only a small or no surface being available for the spiral to rest against the inner wall of the upper and lower part of the sleeve element when the inner element is inclined. This, and an excessive clearance between the spiral and the sleeve element, can therefore cause the inclination to fail to such an extent that jamming of the inner element and the sleeve element occurs. Lubricant transport is interrupted by this seizing, which can lead to damage and even to total damage to the refrigerant compressor.

Disclosure of Invention

The object of the present invention is therefore to provide a lubricant reservoir which avoids the above-mentioned disadvantages. In particular, jamming of the inner element and the sleeve element and/or excessive lubricant transport at high rotational speeds should be avoided.

In order to solve the object, in a lubricant receiver for the vertical transport of lubricant by means of a crankshaft of a refrigerant compressor, comprising a sleeve element having a clear cross section which is delimited by an inner wall and extends along a longitudinal axis of the sleeve element from an upper end of the sleeve element to a lower end of the sleeve element, the lubricant receiver further comprises an inner element having an outer circumferential surface which extends along the longitudinal axis of the inner element from the lower end to the upper end and on which a spiral is arranged which protrudes from the outer circumferential surface and extends helically from the region of the lower end to the region of the upper end of the outer circumferential surface and delimits the passage in some regions, wherein, in an operating state of the lubricant receiver, the lubricant receiver comprises a first lubricant channel which is arranged in the inner circumferential surface of the sleeve element and a second lubricant channel which

The outer circumferential surface of the inner element is arranged at least in some regions in the clear cross section of the sleeve element in such a way that a gap is provided between the outer surface and the inner wall of the spiral,

the lower end of the outer circumferential surface is arranged in front of the upper end thereof, seen in the direction from the lower end to the upper end of the sleeve element,

the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element,

according to the invention, at least one contact section is provided in the region of the upper end of the outer circumferential surface, which contact section projects radially beyond the outer circumferential surface and has a different course than the spiral course of the spiral.

A spiral portion "protruding" from the outer circumferential surface may be understood as "protruding radially outward". That is to say that the spiral extends at each point along its course in a direction perpendicular to the outer circumferential surface or longitudinal axis of the inner element, which direction points away from the longitudinal axis.

The spiral course of the spiral can be provided with a constant slope or a varying slope.

In particular, the spiral portion may extend from a lower end portion to an upper end portion of the outer peripheral surface.

The channel or the channel cross section is at least partially delimited on two mutually opposite sides by a spiral and on the side arranged between the sides by an outer circumferential surface, wherein the channel has no delimiting surface on the side opposite the outer circumferential surface and is open. In other words, the channel or the channel cross section is closed only on three of the four sides, and the outer circumferential surface constitutes the bottom of the channel.

In accordance with the above, the sleeve element and the inner element are designed such that, in the operating state, the outer circumferential surface of the inner element is arranged at least partially in the clear cross section of the sleeve element such that a gap is provided between the outer surface and the inner wall of the spiral.

It is to be noted that the outer circumferential surface typically corresponds to the circumferential surface of the rotating cylinder. However, other shapes are also conceivable, for example tapered, in particular conical shapes which narrow along the longitudinal axis of the inner element. The clear cross section of the sleeve element corresponds to the shape of the inner element or the outer circumferential surface and typically has a cylindrical shape. Similar to the outer circumferential surface, other shapes of the clear cross section are also conceivable, for example a shape which narrows, in particular tapers, along the longitudinal axis of the sleeve element.

In accordance with the above, the sleeve element and the inner element are designed such that, in the operating state, the lower end of the outer circumferential surface is arranged in front of the upper end thereof, viewed in the direction from the lower end to the upper end of the sleeve element. That is to say that the sleeve element and the inner element are oriented at least approximately identically. In practice, when used in an operating refrigerant compressor, it follows that the lower end of the sleeve element and the outer circumferential surface is arranged vertically below the upper end of the sleeve element and the outer circumferential surface.

Since only a relative rotation of the sleeve element and the inner element with respect to one another is relied upon, the inner element can be connected to the crankshaft in a rotationally fixed manner and the sleeve element is fixed in rotation (except for a negligible slight angle of rotation). When the compressor is running, the crankshaft rotates and accordingly the inner element also rotates, while the sleeve element does not rotate.

Or the sleeve element can be connected to the crankshaft in a rotationally fixed manner and the inner element can be fixed in rotation (except for a negligible slight torsion angle).

The rotationally fixed connection between the inner element or the sleeve element and the crankshaft can in principle take place directly or indirectly, that is to say with the interposition of at least one further element, for example a seal, a fastening element or the like.

The sleeve element can be connected to the crankshaft, in particular in the region of its upper end. For example, it is conceivable for the sleeve element to be pushed with its clear cross section onto the crankshaft in the region of the upper end and to be held on the crankshaft, for example by means of a press fit. For this purpose, it can be provided that the clear cross section in the press-fit region is configured differently than the clear cross section in the region in which the inner element is at least partially arranged in the operating state.

It has been established for good specifications that it is not excluded that the sleeve element itself is a part or a section of a larger element. But in any case the clear section extends over the portion or section, i.e. over the sleeve element.

In accordance with the above, the sleeve element and the inner element are designed such that, in the operating state, the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element. Correspondingly, if the sleeve element and preferably also the inner element project at least partially into the lubricant groove, lubricant can pass from the lubricant groove into the gap (and thus also at least subsequently into the channel) of the refrigerant compressor.

The lubricant may be an oil, which is common in particular when used in refrigerant compressors.

The sleeve element and the inner element are caused to rotate relative to one another by rotation of the crankshaft, in particular when the sleeve element is connected to the crankshaft in a rotationally fixed manner. Preferably, the inner element is not rotated or is rotated only over a limited angular range relative to the stator, while the sleeve element is rotated completely. However, as already stated above, a reverse design is also possible, in which the inner element is rotated completely and the sleeve element is not rotated or is rotated only over a limited angular range relative to the stator.

The lubricant is set in rotation by the viscosity of the lubricant or the friction between the lubricant and the sleeve element or the inner element, and therefore a corresponding centrifugal force acts on the lubricant. The centrifugal force presses the lubricant into the gap and (due to the presence of the spiral) mainly into the channel in the direction of the crankshaft.

Tilting of the inner element relative to the sleeve element can occur during operation. In conventional lubricant receptacles, the angle of inclination which occurs between the longitudinal axis of the sleeve element and the longitudinal axis of the inner element during tilting is limited by the outer surface of the spiral abutting against the inner wall of the sleeve element.

By the following means: the at least one contact section projects beyond the outer circumferential surface in a radial direction, i.e. in a direction perpendicular to the longitudinal or outer circumferential surface, in a direction pointing away from the longitudinal or outer circumferential surface, and the contact section can contact the inner wall during tilting and thus limit the tilting angle in such a way that no jamming occurs. In this case, the at least one contact section can be designed to project so far that only the contact section contacts the inner wall and that the outer surface, which is not, for example, a spiral, also contacts the inner wall.

In this case, it is possible to realize that the course of the at least one contact section differs from the course of the spiral, on the one hand, the arrangement of the at least one contact section can be kept concentrated in the region of the upper end of the outer circumferential surface and, on the other hand, at the same time, a sufficiently large angular region about the longitudinal axis of the inner element is covered by the at least one contact section in order to ensure a secure contact against the inner wall when tilting occurs.

In this case, the at least one contact portion does not necessarily have to project from the outer circumferential surface itself, but a distance can also exist between the outer circumferential surface and the contact portion, for example, as viewed along the longitudinal axis.

Of course, a plurality of, for example, two, three or more abutment sections can also be provided in the region of the upper end of the outer circumferential surface. In particular, it is therefore not necessary to provide a continuous or uninterrupted contact portion, but rather a plurality of contact portions can extend, for example, along a circular line (in particular when the line is in a plane perpendicular to the longitudinal axis of the inner element) or an elliptical line (in particular when the line is in a plane not perpendicular to the longitudinal axis of the inner element) around the longitudinal axis of the inner element.

The arrangement of the at least one contact portion in the region of the upper end of the outer circumferential surface also ensures that the at least one contact portion does not hinder the lubricant from entering the channel. The latter channels are important for reliable lubrication, in particular at low rotational speeds, wherein the lubricant typically does not completely fill the channels or the channel cross sections when the lubricant is fed in the direction of the crankshaft.

At the same time, however, the restriction of the lubricant flow at high rotational speeds can be achieved by the limitation of the channel or the channel cross section by means of the at least one contact section in the region of the upper end of the outer circumferential surface. In this case, the channel is usually completely filled with lubricant and a narrowing of the channel can be achieved (apart from the limitation by the spiral) by locally limiting the channel by means of the at least one contact section. This in turn causes an accumulation of lubricant and thus limits lubricant delivery at high rotational speeds.

Accordingly, in a preferred embodiment of the lubricant receiver according to the invention, it is provided that the channel has a reduced channel cross section in the region of the at least one contact section. That is to say the channel cross-section is reduced compared to at least one section of the channel outside said region. Preferably, the channel cross section in the region of the abutting section is reduced compared to the channel cross section outside said region, i.e. all sections of the channel outside said region have a larger channel cross section. Here, a reduced channel cross section is achieved in that: the at least one abutment section at least partially defines a channel.

In order to achieve a substantially steeply oriented course of the at least one contact section, in contrast to the course of the steeply angled spiral, in a preferred embodiment of the lubricant receiver according to the invention it is provided that the at least one contact section is delimited, as seen along the longitudinal axis of the inner element, by a first boundary surface and a second boundary surface which are arranged one after the other, and the first boundary surface and/or the second boundary surface is perpendicular to the longitudinal axis of the inner element. This increases the throttling effect on the lubricant supply at high rotational speeds. Furthermore, such a design of the at least one contact portion proves to be advantageous from a manufacturing point of view.

In a preferred embodiment of the lubricant receiver according to the invention, it is provided that the spiral is connected directly to the at least one contact portion. This ensures a favorable flow of lubricant in the region of the at least one contact portion. Furthermore, this embodiment also proves to be advantageous in terms of manufacturing technology.

As already mentioned, by the course of the at least one contact section, it is possible to cover a sufficiently large angular region around the longitudinal axis of the inner element with the at least one contact section in order to ensure a secure contact against the inner wall when tilting occurs. Accordingly, in a preferred embodiment of the lubricant receiver according to the invention, it is provided that the at least one contact section covers an angular range around the longitudinal axis of the inner element of at least 15 °, preferably at least 45 °, particularly preferably at least 90 °.

It is thus conceivable, for example, to provide one continuous contact portion which covers a specific angular range (for example 60 °), or to provide three contact portions, each of which covers a part of the specific angular range (for example 20 ° in each case in the example), wherein the contact portions are arranged such that they do not overlap and therefore cover the specific angular range as a whole.

By means of the flexible positioning of the contact portions, a relatively small angular range of coverage is already sufficient for stable operation. In practice, achieving stable operation is often an optimization problem, wherein the desired stability, the free passage cross section, the rotational speed of the crankshaft, the oil viscosity, the course of the spiral and the friction between the at least one contact section and the inner wall of the sleeve element are taken into account. For example, applications are conceivable in which four abutment portions are provided for stable operation, each of which covers an angular range of only 5 °, so that the abutment portions as a whole cover an angular range of 20 ° about the longitudinal axis of the inner element.

In a particularly preferred embodiment of the lubricant receiver according to the invention, it is provided that the angular range is 360 °. That is to say the entire angular range about the longitudinal axis of the inner element is covered by the at least one contact portion.

In principle, it is conceivable to provide a plurality of abutment sections for this purpose, which are arranged one behind the other, at least in regions, as viewed along the longitudinal axis of the inner element. For example, it is conceivable to provide three abutment sections, each of which covers 120 ° and is arranged without overlapping, so that they cover the entire angular range of 360 ° overall. However, it is also conceivable to provide three contact portions, each of which covers more than 120 ° and is arranged one above the other such that they cover the entire angular range of 360 ° overall.

In a particularly preferred embodiment of the lubricant receiver according to the invention, it is provided that the at least one bearing section comprises at least one closed bearing section, wherein each closed bearing section covers the entire angular region. In principle, one or more closed contact sections can be provided, wherein in the case of a plurality of closed contact sections, the contact sections are arranged one after the other, as seen along the longitudinal axis of the inner element. This makes it possible to define the angle of inclination optimally and reliably and thus to protect it optimally against jamming.

In a preferred embodiment of the lubricant receiver according to the invention, it is provided that, in particular for reasons of manufacturing engineering or economy, exactly one contact section is provided. In particular, when the contact portion is designed as a closed contact portion in this case, a particularly good compromise can be achieved between the simplicity of the production technology and the reliable limitation of the angle of inclination.

In a preferred embodiment of the lubricant receiver according to the invention, it is provided that the inner element has a hollow space which is open, viewed along the longitudinal axis of the inner element, toward the upper end of the outer circumferential surface. This allows, in particular, a simple, material-saving and cost-effective production.

In a preferred embodiment of the lubricant receiver according to the invention, it is provided that at least one outlet opening is provided in the region of the upper end of the outer circumferential surface, wherein the at least one outlet opening connects the channel to the hollow space.

In other words, the at least one discharge opening provides a fluid connection between the channel and the hollow space. Accordingly, lubricant can pass from the channel through the at least one outlet opening into the hollow space and from there (since the hollow space opens upward, i.e. in the direction of the upper end of the outer circumferential surface) into the clear cross section of the sleeve element or to the crankshaft. This facilitates improved lubricant delivery.

If a closed contact section is provided, which at least partially delimits the channel, it may also prove necessary for the at least one outlet opening to interact with the hollow space in order to achieve a sufficient supply of lubricant from the channel in the direction of the crankshaft.

In particular, if the passage is completely closed by the closed contact section in the direction of the upper end of the outer circumferential surface, the lubricant can only be transported further through the gap in the direction of the crankshaft without flow openings, which can lead to an excessively low transport of lubricant, which is dependent in particular on the rotational speed and the gap width.

Similarly to the above, in a refrigerant compressor, the refrigerant compressor includes: a hermetically sealable compressor housing; an electric drive unit disposed in a shell interior of the compressor shell, the electric drive unit including a rotor and a stator; a crankshaft connected to the rotor so as to be non-rotatable relative thereto; according to the invention, the refrigerant compressor has a lubricant receiver according to the invention in an operating state in order to convey lubricant from a lubricant groove formed in a bottom region of the compressor housing through (or onto) the crankshaft, wherein the crankshaft has a bore and/or at least one groove which preferably extends at least in some regions at an angle to a rotational axis of the crankshaft, said at least one groove being in fluid connection with a clear cross section of the sleeve element.

For good specification, it should be noted that the lubricant receiver according to the invention can of course also be used in compressors in which no bore is present in the crankshaft, but the crankshaft has, for example, at least one groove for the further supply of lubricant, which groove is in fluid connection with the clear cross section of the sleeve element.

As also explained above, the inner element or the sleeve element can be connected to the crankshaft in a rotationally fixed manner. In a preferred embodiment of the refrigerant compressor according to the invention, it is correspondingly provided that the sleeve element of the lubricant receiver is connected to the crankshaft in a rotationally fixed manner.

Correspondingly, the inner element may be connected substantially non-rotatably with respect to the stator or other component of the refrigerant compressor, relative to which the crankshaft rotates.

Correspondingly, the inner element can preferably have a fastening element in the region of the lower end of the outer circumferential surface, which fastening element can cooperate with the fixing means in order to establish the rotationally fixed connection. The fastening element may be, for example, an ear stemThe fastening means can be, for example, a bow which can engage with the lug.

Drawings

The invention will now be explained in more detail with the aid of examples. The drawings are exemplary and, while the inventive concepts are to be construed, they are not intended to be limiting or even exhaustive.

Shown here are:

figure 1a shows the inner elements of an embodiment of the lubricant reservoir according to the invention in a side view,

figure 1b shows the internal elements of figure 1a in a front view,

figure 1c shows the inner element of figure 1a in cross section according to the section line I-I in figure 1a,

figure 2a shows the inner elements of a further embodiment of the lubricant reservoir according to the invention in a side view,

figure 2b shows the internal elements of figure 2a in a front view,

figure 2c shows the inner element of figure 2a in cross section according to the section line II-II in figure 2b,

fig. 3 shows a sectional view of an embodiment of the lubricant receiver according to the invention with the internal components in fig. 1a or 1c, wherein the lubricant receiver is mounted on a crankshaft of a refrigerant compressor according to the invention,

fig. 4 shows a sectional view of a refrigerant compressor according to the invention with the lubricant receiver in fig. 3.

Detailed Description

Fig. 1a shows a side view of an inner element 9 of an embodiment of a lubricant reservoir 1 according to the invention. The latter lubricant receiver is fixed in the operating state and is shown in fig. 3 in a sectional view on the crankshaft 2 of the refrigerant compressor 3 according to the invention.

The lubricant receiver 1 serves for the vertical transport of lubricant, in particular oil 15, from a lubricant groove 26 formed in a bottom region 25 of the compressor housing 18 of the refrigerant compressor 3 via the crankshaft 2, see the sectional view in fig. 4. For this purpose, the crankshaft 2 has a bore 27, which is well visible in fig. 3, and from which oil 15 can be discharged via a discharge opening 28 to the location to be lubricated. The bore 27 may be embodied to extend obliquely to the rotational axis 29 of the crankshaft 2 in order to optimally convey the oil 15.

Furthermore, an electric drive unit 19 having a rotor 20 and a stator 21 is arranged in the compressor housing 18, wherein the crankshaft 2 is connected to the rotor 20 in a rotationally fixed manner. In the compressor housing 18, there is furthermore a piston-cylinder unit 22, which comprises a piston 23, which is mounted movably in a cylinder 24 of the piston-cylinder unit 22 and which can be driven for compressing the refrigerant of the crankshaft 2.

The lubricant reservoir 1 comprises a sleeve element 4 having a clear cross section 5 defined by an inner wall 33, which extends along a longitudinal axis 6 of the sleeve element 4 from an upper end 7 to a lower end 8 of the sleeve element 4. As can be seen in fig. 3, the clear cross section 5 at the upper end 7 can be used to accommodate the crankshaft 2 in order to establish a rotationally fixed connection between the sleeve element 4 and thus the lubricant receiver 1 and the crankshaft 2, for example by means of a press fit.

Furthermore, the lubricant reservoir 1 comprises an inner element 9 having an outer circumferential surface 10 which extends along a longitudinal axis 11 of the inner element 9 from a lower end 12 to an upper end 13. On the outer circumferential surface 10, a spiral 14 is provided which projects radially outward from the outer circumferential surface 10 and extends helically from the region of the lower end 12 of the outer circumferential surface 10 to the region of the upper end 13 (in the exemplary embodiment shown, from the lower end 12 of the outer circumferential surface 10 to the upper end 13). For reasons of manufacturing technology, the spiral 14 may have a short interruption, which is visible in fig. 1a and 2 a. The channel 32 with the channel cross section 42 is formed or defined by the spiral 14 and the outer circumferential surface 10. The channel 32 or the channel cross section 42 is at least partially delimited by the spiral 14 on two sides lying opposite one another and by the outer circumferential surface 10 on the side lying between these sides, the channel 32 not defining a surface on the side lying opposite the outer circumferential surface 10 but being open. In other words, the channel 32 or the channel cross section 42 is closed on only three of the four sides, and the outer circumferential surface 10 forms the bottom of the channel 32.

In the operating state of the lubricant reservoir 1, the inner element 9 is arranged with its outer circumferential surface 10 at least partially (in the illustrated exemplary embodiment substantially completely) in the clear cross section 5 of the sleeve element 4. Here, the lower end 12 of the outer circumferential surface 10 is arranged in front of the upper end 13 of the outer circumferential surface, as seen in the direction of the lower end 8 to the upper end 7 of the sleeve element 4, that is to say the sleeve element 4 and the inner element 9 are oriented or oriented to some extent identically.

In the embodiment shown, the outer circumferential surface 10 corresponds to the circumferential surface of a rotating cylinder. The clear cross section 5 of the sleeve element 4 is adapted to the shape of the inner element 9 or the outer circumferential surface 10 and has a corresponding cylindrical shape in the region in which the inner element 9 is accommodated in the sleeve element 4 or is arranged in the clear cross section 5 in the operating state.

Furthermore, the sleeve element 4 and the inner element 9 are designed such that the inner element 9 and the sleeve element 4 can be rotated relative to one another about the longitudinal axis 6 of the sleeve element 4 and/or the longitudinal axis 11 of the inner element 9. During operation of the refrigerant compressor 3, this rotation is transmitted or generated by the rotationally fixed connection of the lubricant receiver 1 to the crankshaft 2. In principle, only a relative rotation between the sleeve element 4 and the inner element 9 is important, i.e. it is also conceivable for the inner element 9 to be driven in rotation and for the sleeve element 4 to be substantially rotationally fixed. In the embodiment shown, when the crankshaft 2 is rotating, while the inner element 9 is not rotating, the sleeve element 4 is driven in rotation due to the rotationally fixed connection of the sleeve element 4 to the crankshaft 2.

In order to largely prevent rotational movements of the inner element 9, it can be connected to the stator 21, for example, by means of a fastening means. For this purpose, the inner element 9 can, as can be seen well in the front view of fig. 1b, for example have a fastening element in the form of an ear 16, with which the fastening means can engage. In the exemplary embodiment shown in fig. 4, a bracket 31 is provided as a fastening means, which engages with the lug 16 and establishes the connection of the inner element 9 to the stator 21.

As can be seen, for example, from fig. 3, in the operating state the inner element 9 is arranged in the clear cross section 5 of the sleeve element 4 in such a way that a gap 30 with a gap width is provided between an outer surface 34 of the spiral 14 and an inner wall 33, which outer surface 34 delimits the spiral 14 radially to the outside. Said gap 30 ensures that the inner element 9 and the sleeve element 4 are free from problematic relative rotations with respect to each other.

Accordingly, when the inner element 9 and the sleeve element 4 project at least partially into the lubricant groove 26, oil 15 from the lubricant groove 26 can enter the gap 30 and the passage 32. The sleeve element 4 projects into the lubricant groove 26, in particular in the region of its lower end 8, and the inner element 9 projects into the lubricant groove, in particular in the region of its lower end 12 of its outer circumferential surface 10. Due to the viscosity of the oil 15 or the friction between the oil 15 and the sleeve element 4, a corresponding centrifugal force acts on the oil 15 when the sleeve element 4 rotates. The centrifugal force presses the oil 15 in the gap 30 and in particular in the channel 32 in the direction from the lower end 12 to the upper end 13 of the outer circumferential surface 10 and thus in the direction of the crankshaft 2.

In any case, the oil 15 can flow particularly well through the channel 32 to the crankshaft 2, irrespective of the exact gap width. In the exemplary embodiment shown, the bore 27 of the crankshaft 2 is in fluid connection with the clear cross section 5 and therefore ultimately also with the channel 32, so that the oil 15 can reach the bore 27.

In operation, tilting of the inner element 9 relative to the sleeve element 4 may occur, so that the angle of tilt between the longitudinal axis 6 of the sleeve element 4 and the longitudinal axis 11 of the inner element 9 is adjusted. In order to define the angle of inclination and thus to prevent the inner element 9 from jamming in the sleeve element 4 or the clear cross section 5, according to the invention at least one contact section 35 is provided in the region of the upper end 13 of the outer circumferential surface 10, which projects radially beyond the outer circumferential surface 10 and whose course differs from the spiral course of the spiral 14. By the following means: the at least one contact section 35 projects beyond the outer circumferential surface 10 in the radial direction, i.e. in a direction perpendicular to the longitudinal axis 11 or the outer circumferential surface 10, in a direction which is directed away from the contact section, and the contact section 35 can contact the inner wall 3 during tilting and thus define a tilting angle such that no jamming occurs.

In this case, it is possible to realize that the course of the at least one contact section 35 differs from the course of the spiral 14, on the one hand, the arrangement of the at least one contact section 35 can be kept concentrated in the region of the upper end 13 of the outer circumferential surface 10 and, on the other hand, at the same time, a sufficiently large angular region 36 around the longitudinal axis 11 of the inner element 9 is covered by the at least one contact section 35 in order to ensure a secure contact against the inner wall 33 when tilting occurs.

Of course, a plurality of, for example, two, three or more abutment sections 35 can also be provided in the region of the upper end 13 of the outer circumferential surface 10. The inner element 9 of fig. 1a has, for example, two bearing sections 35, as can be seen clearly in comparison with fig. 1 b. In fig. 1a, it can be seen that the spiral 14 is directly connected to one of the abutment sections 35, wherein the transition to the abutment section 35 is indicated by a dashed line. The contact portion 35 encloses an angular range 36 of approximately 100 °. The other of the two contact portions 35 is arranged on the opposite side of the outer circumferential surface 10, i.e. the two contact portions are arranged along a circular line around the longitudinal axis 11, wherein the circular line lies in a plane perpendicular to the longitudinal axis 11. The other of the two abutment sections also covers an angular range of approximately 100 °, so that the two abutment sections 35 cover approximately 200 ° in total. Correspondingly, the possibility of one of the abutment sections 35 abutting against the inner wall 33 and effectively defining the angle of inclination occurring when the inner element 9 is inclined is high.

Furthermore, the arrangement of the at least one contact portion 35 in the region of the upper end 13 of the outer circumferential surface 10 also ensures that the at least one contact portion 35 does not hinder the entry of oil 15 into the channel 32. The latter channels are important for reliable lubrication, in particular at low rotational speeds, wherein the oil 15 typically does not completely fill the channel 32 or the channel cross section 42 when the oil is fed in the direction of the crankshaft 2.

At the same time, the at least one contact portion 35 defines a channel 32 or a channel cross section 42 in the region of the upper end 13 of the outer circumferential surface 10. As can be seen well in fig. 1a and 1b and the sectional view of fig. 1c, the passage cross section 42 in the region of the upper end 13 of the outer circumferential surface 10 or in the region of the contact section 35 is significantly smaller by the contact section 35 than in the region between the upper end 13 and the lower end 12 or in the region of the lower end 12 of the outer circumferential surface 10. The passage cross section 42 thus reduced in the region of the abutment section 35 effects a restriction of the lubricant flow at high rotational speeds. I.e. at high rotational speeds, the channel 32 is normally completely filled with oil 15. By locally limiting the passage 32 by means of the at least one contact section 35, a narrowing of the passage 32 is achieved, which therefore leads to an accumulation of oil 15 and thus limits lubricant delivery at high rotational speeds.

In contrast to the tapered course of the spiral 14, the abutment section 35 has a substantially non-tapered course in the exemplary embodiment of fig. 1a, 1b, 1c, so that the described reduction of the channel cross section 42 is achieved. The abutment section 35 is designed in such a way that, as viewed along the longitudinal axis 11 of the inner element 9, it is delimited by a first boundary surface 40 and a second boundary surface 41, which are arranged one behind the other, wherein the second boundary surface 41 is perpendicular to the longitudinal axis 11 of the inner element 9.

As fig. 1c shows, the inner element 9 of the illustrated embodiment has a hollow space 38 which is open toward the upper end 13 of the outer circumferential surface 10. This allows cost-effective and simple production.

Fig. 2a, 2b, 2c show an inner element 9 of another embodiment of the lubricant reservoir 1 according to the invention. The inner element also has a hollow space 38 which is open in the direction of the upper end 13 of the outer circumferential surface 10. In this exemplary embodiment, only one abutment section 35 is provided, which is designed as a closed abutment section 37. The closed contact portion 37 covers the entire angular range 36 of 360 ° and, in the exemplary embodiment shown, extends on a circular line which lies in a plane perpendicular to the longitudinal axis 11. It is thus possible to ensure a very high degree of safety against undesired jamming when tilting in all directions.

In this case, the spiral 14 is also directly connected to the contact section 35, which is illustrated in fig. 2a and 2b by dashed lines. Correspondingly, the channel cross section 42 tapers to zero. Nevertheless, in order to be able to continue the supply of oil 15 from the channel 32 to the crankshaft 2, the gap 30 is available in principle, but the supply per unit time is limited as a result. In addition, a backflow calculation through the gap 30 may also be utilized. In this exemplary embodiment, two flow openings 39 are therefore provided, which are arranged opposite one another in the region of the upper end 13 of the outer circumferential surface 10 and which fluidically connect the channel 32 to the hollow space 38. In other words, the oil 15 can pass from the channel 32 through the flow openings 39 into the hollow space 38 and from there (since it opens upward, i.e. in the direction of the upper end 13 of the outer circumferential surface 10) into the clear cross section 5 of the sleeve element 4 or to the crankshaft 2. This facilitates improved lubricant delivery.

Furthermore, what has been described above in connection with the embodiments of fig. 1a, 1b, 1c also applies to the embodiments of fig. 2a, 2b, 2 c.

List of reference numerals

1 lubricant container

2 crankshaft

3 refrigerant compressor

4 sleeve element

5 clear cross section of the sleeve element

6 longitudinal axis of sleeve member

7 upper end of sleeve element

8 lower end of sleeve element

9 inner member

10 outer peripheral surface of inner member

11 longitudinal axis of inner member

12 lower end portion of the outer peripheral surface

13 upper end portion of outer peripheral surface

14 helical part

15 oil

16 ear handle

18 compressor shell

19 electric drive unit

20 rotor

21 stator

22 piston-cylinder unit

23 piston

24 cylinder

25 bottom region

26 lubricant groove

27 bore of crankshaft

28 discharge hole

29 axis of rotation of crankshaft

30 gap

31 bow member

32 channels

33 inner wall

34 outer surface of the spiral part

35 abutting section

36 angular range

37 closed contact section

38 hollow space

39 discharge opening

40 first side interface

41 second boundary surface

42 channel cross section