EP2021632B1 - Refrigerant compressor - Google Patents

Description

The present invention relates to a hermetically sealed refrigerant compressor with a hermetically sealed compressor housing, in the interior of which a refrigerant-compressing piston-cylinder unit operates, and a suction channel is provided, via which refrigerant in the compressor housing or in a piston to the piston Cylinder unit coupled suction muffler is conveyed and a pressure channel is provided, via which refrigerant is transported from the piston-cylinder unit from the compressor housing, according to the preamble of claim 1. Such a refrigerant medium compressor is, for example US 6,607,369 B1 known. Such refrigerant compressors are used in domestic and industrial applications, where they are usually arranged on the back of a refrigerator or refrigerator. Your task is to compress a refrigerant circulating in the cooling system and weiterzubefördern, whereby heat dissipated from the interior of the refrigerator, delivered to the environment and a refrigerator or cooling rack is thus cooled in a known manner.

The refrigerant compressor has a hermetically sealed compressor housing and an electric motor which drives a cylinder oscillating piston in a cylinder for compressing the refrigerant via a crankshaft. The compressor housing consists mostly of a cover part and a base part and has connection openings, wherein a suction channel, a pressure channel and possibly other lines are provided, which lead through the connection openings in the compressor housing and out of this to the refrigerant to the cylinder and this again in the Transport refrigeration cycle. Before the refrigerant sucked in the suction duct enters the piston-cylinder unit, it is guided via a suction muffler, which has the task of absorbing or reducing the noise caused by the refrigerant circulation and the piston and valve movements.

On the one hand to lubricate the mutually sliding parts of the piston-cylinder unit and on the other hand to accomplish a cooling of the piston-cylinder unit, an oil pump is provided, which supplies the piston-cylinder unit with oil.

The oil circulating within the compressor housing in this manner is swirled either via suitable nozzles or via rotary elements mounted on the crankshaft and fed to the desired areas of the compressor system.

Here, it is desirable that the swirled and heated oil continues to be reflected on the compressor housing wall and the heat absorbed by the oil is discharged to the compressor housing and subsequently discharged to the environment.

However, it is not desirable here that a heat exchange takes place from the oil to the suction channel and to the pressure channel. If the heated oil flowing down the compressor housing wall and flowing away therefrom in the direction predetermined by the force of gravity comes into contact with the suction channel, it is undesirably heated and conveys this heat also to the heat transported in the suction channel and immediately before the compression process standing refrigerant. An increase in the intake temperature of the refrigerant, however, causes a deterioration of the Efficiency of the refrigerant compressor and should be avoided as possible.

The pressure channel also causes an indirect heating of the compressor housing and the suction channel. Since the compressed refrigerant discharged in the pressure channel has temperatures of up to 100 ° C., the pressure channel also heats up considerably, which is why the refrigerant ejected from the piston-cylinder unit is to be conveyed out of the compressor housing as hot as possible.

However, when the oil draining from the compressor housing wall comes into contact with the hot pressure channel, the lower temperature oil undesirably absorbs heat and, as it circulates within the compressor housing, discharges it to the compressor housing, causing heating of the whole Interior of the compressor housing, so also the suction channel and the piston-cylinder unit entails.

Considering the large number of refrigerant compressors in operation in the world, any efficiency improvement made to a refrigerant compressor has significant energy savings potential, which is becoming increasingly important as global energy resources become scarcer.

Possibilities for improving the efficiency are in particular in the lowering of the temperature of the sucked refrigerant at the beginning of the compression process. Each lowering of the intake temperature of the refrigerant into the cylinder of the piston-cylinder unit therefore causes a reduction as well as the lowering of the temperature during the compression process and associated Ausschiebetemperatur the required technical work for the compaction process.

STATE OF THE ART

From the US 6,637,216 B1 a baffle plate in the region of the inlet of the suction pipe is known in the compressor housing, which serves to prevent sucked through the suction pipe liquid refrigerant or lubricant enters a second, leading into the cylinder portion of the suction pipe and thus enters the cylinder. The design of this baffle depends on the gas flowing into the compressor housing, whereby the plate can have relatively narrow dimensions.

PRESENTATION OF THE INVENTION

It is therefore the object of the present invention to prevent contact of oil flowing down the compressor housing wall with the suction passage and the pressure passage to reduce heating of the refrigerant within the compressor housing and thus increase the efficiency of the refrigerant compressor.

This object is achieved by a hermetically sealed refrigerant compressor with the characterizing features of claim 1.

A generic refrigerant compressor has a hermetically sealed compressor housing, in the interior of which a refrigerant-compressing piston-cylinder unit operates, which is supplied via a discharging into the compressor housing or in the compressor housing suction channel with refrigerant and connected to a leading from the compressor housing pressure channel ,

According to the invention, it is provided that in the operating position of the compressor housing above the passage of the suction channel or pressure channel through the compressor housing wall to the same deflection means are provided which prevent contact of flowing down on the compressor housing wall oil with the suction channel or pressure channel.

The inventive arrangement of the deflection means a heat exchange between the oil and the suction channel or pressure channel is prevented, in particular it is avoided that the flowing oil heats the suction channel and that the pressure channel heats the flowing oil.

This avoids that the standing immediately before the compression process refrigerant heats in an undesirable manner, thus achieving an increase in the efficiency of the refrigerant compressor.

According to the characterizing features of claim 2, the deflection means are at least one leading extension projecting inwards from the compressor housing wall. Such a guide extension reliably shields the suction channel or pressure channel from the oil flowing down the compressor housing wall, since it can flow off or drip along the longitudinal extent of the conductive extension without wetting the suction channel or pressure channel.

In the case of the deflection means arranged above the suction channel or pressure channel, it can also be, as experiments have shown, instead of a guide extension at least one recess provided directly in the compressor housing wall, which provides adequate shielding of the suction channel or pressure channel from the downflowing Oil causes by the at the Compressor housing wall draining oil follows the course of the recess and is thus guided around the suction channel 2 and the pressure channel 3.

In a preferred embodiment according to the characterizing features of claim 4, the Leitfortsatz is substantially V-shaped, wherein the tip of the V is arranged in the operating position of the compressor housing above the suction channel or pressure channel. The subject V-shape is easy to manufacture and allows a direct deflection of the downflowing oil from the immediate area of the suction or pressure channel by dividing the downflow of oil at the top of the V to the left and right and according to the gravity of the two legs of the V flows without contacting the suction channel or pressure channel.

In order to ensure that the oil flowing down the compressor housing wall is guided completely around the suction channel or pressure channel and excludes any drop in flight, it is provided according to the characterizing features of claim 5 that the two legs of the V extend below the suction channel or below the suction channel Pressure ducts run.

According to the characterizing features of claim 6, the conductive extension or the recess can have a umbrella-shaped design, which means that the conductive extension or the recess has a convex longitudinal extent (viewed in the operating position of the refrigerant compressor).

To preclude creeping rivulets of oil from continuing from the top of the conductive extension on the underside thereof and subsequently reaching the suction channel or pressure channel, it is provided according to the characterizing features of claim 7 that the conductive extension has a trough-shaped or a in the suction channel or pressure channel opposite direction has concave cross-sectional profile.

In order to prevent contact of the downflowing oil with the suction channel or pressure channel by drop formation and around the deflection creeping around oil flows, it may be advantageous according to the characterizing features of claim 8 moreover, to arrange a plurality of conductive extensions or recesses on top of each other. Thus, if a certain quantity of oil overcomes the barrier formed by a first deflection means and approaches the suction channel or pressure channel in accordance with gravity, then at the latest the barrier formed by a second deflection means ensures that this quantity of oil is deflected by the suction channel or pressure channel and these not contacted.

According to the characterizing features of claim 9, the suction channel and / or the pressure channel is tubular. The tubular cross-section of the suction channel and pressure channel allows a simple connection ebendieser to the compressor housing by means provided in the compressor housing bores or a suitable connection element.

BRIEF DESCRIPTION OF THE FIGURES

• Fig.1 einen Basisteil eines Verdichtergehäuses in Schrägansicht
• Fig.2 einen Basisteil eines Verdichtergehäuses in Draufsicht
• Fig.3 eine partielle Schnittdarstellung des Verdichtergehäuses aus Fig.2 entlang Linien A-A bzw. B-B
• Fig.4 eine Detailansicht eines erfindungsgemäßen Ablenkmittels gemäß Blickrichtung D aus Fig.2
• Fig.5 eine Detailansicht eines erfindungsgemäßen Ablenkmittels gemäß Blickrichtung D aus Fig.2
• Fig.6 eine schematische Darstellung eines erfindungsgemäßen Leitfortsatzes in Schnittdarstellung gemäß der Linien A-A bzw. B-B aus Fig.2
• Fig.7 eine schematische Darstellung eines erfindungsgemäßen Leitfortsatzes in Schnittdarstellung gemäß der Linien A-A bzw. B-B aus Fig.2

The invention will now be explained in more detail with reference to an embodiment. Showing:

• Fig.1 a base part of a compressor housing in an oblique view
• Fig.2 a base part of a compressor housing in plan view
• Figure 3 a partial sectional view of the compressor housing Fig.2 along lines AA and BB
• Figure 4 a detailed view of a deflection according to the invention according to the viewing direction D from Fig.2
• Figure 5 a detailed view of a deflection according to the invention according to the viewing direction D from Fig.2
• Figure 6 a schematic representation of a lead extension according to the invention in a sectional view according to the lines AA and BB Fig.2
• Figure 7 a schematic representation of a lead extension according to the invention in a sectional view according to the lines AA and BB Fig.2

WAYS FOR CARRYING OUT THE INVENTION

The present refrigerant compressor has a hermetically sealed compressor housing 1, into which a suction channel 2, a pressure channel 3 and a service pipe 9 open via connection openings 5.

In a known manner flows via the suction channel 2, a refrigerant to a disposed within the compressor housing 1 (not shown) piston-cylinder unit in which a compression of the refrigerant takes place, wherein the pressure channel 3, the compressed and therefore highly heated refrigerant as a result the piston-cylinder unit leads out of the compressor housing 1 out into a (also not shown) cooling circuit of a cold room. The piston-cylinder unit is driven by an electric motor via a crankshaft, so that the cooling space associated with the refrigerant compressor is continuously cooled by means of the circulating refrigerant.

The sucked in the suction passage 2 refrigerant passes through a coupled to the piston-cylinder unit suction muffler in the piston-cylinder unit to absorb the noise caused by the refrigerant circulation and the piston and valve movements. The suction channel 2 can either be free in the compressor housing open, wherein the refrigerant is sucked in this case from the compressor housing in the piston-cylinder unit, or the suction channel 2 is directly connected to the suction muffler, whereby the refrigerant is passed directly, via the suction muffler, in the piston-cylinder unit. In the former case, the suction pipe usually protrudes slightly into the interior of the compressor housing.

Suction channel 2 and pressure channel 3 are preferably tubular, but may also have other cross-sectional shapes.

The compressor housing 1 has a plurality of stand elements 8, by means of which it can be positioned on a predetermined footprint of a cooling device.

Although in this context in Fig.1 only one base part of a compressor housing 1 is shown, on which in the sequence a (not shown) cover part is placed, the compressor housing 1 can also be configured in other ways, for example in the form of an obliquely divided or otherwise composite compressor housing 1. Likewise, it is conceivable , Suction channel 2, pressure channel 3 or service pipe 9 to lead over the cover part into the interior of the compressor housing, wherein the suction channel 2, the pressure channel 3 is not necessarily the same as in Fig.1 shown, must run in pairs next to each other, but also in any staggered connection openings 5 of the compressor housing 1 open or can lead out of these.

The service tube 9 is only a factory-filling of the compressor housing 1 with a suitable gas or for filling with oil 4, whose application is described below.

Fig.2 shows a plan view of the in Fig.1 illustrated as an oblique view compressor housing 1 and forms with the therein drawn sectional guides AA and BB, the reference of in Fig. 3 shown, partial sectional view showing a connection of the suction channel 2 and the pressure channel 3 to the compressor housing 1. Suction channel 2 or pressure channel 3 in this case pass through a hermetically sealed to the compressor housing 1, disk-shaped connection element 7 through the compressor housing arranged in the connection openings 10, wherein the connection element 7 in turn hermetically sealed to the suction channel 2 and Druckkanal 3 verbunden ist. Usually, the attachment of the suction channel 2 / pressure channel 3 on the connection element 7 and the connection element 7 takes place on the compressor housing 1 by means of welding or soldering.

Within the compressor housing 1 a (not shown) oil pump is further arranged, the task of which is to convey the already mentioned oil 4, with which the compressor housing 1 is filled, to the sliding parts of the piston-cylinder unit to lubricate and to cool. In particular, the bearings of the connecting rod to crankshaft and piston are supplied in this way continuously with circulating oil 4.

On the other hand, the circulation of oil also causes cooling of the piston-cylinder unit and continuously dissipates the heat generated there during the refrigerant compression.

Instead of an oil pump provided with a nozzle, it is also possible for the purpose of lubrication and cooling of the piston-cylinder unit to provide along the axis of the vertically arranged crankshaft a hollow channel, through which in Base part of the compressor housing 1 at the bottom accumulated oil 4 due to the rotation of the crankshaft in a suction effect transported upwards and swirled on exit from the hollow channel at the upper end of the crankshaft mounted on the crankshaft rotation elements and the desired areas of the piston-cylinder unit is supplied. It must be prevented by suitable seals that the swirled oil 4 enters the cylinder head and enters together with the refrigerant in the cooling circuit.

The use of so-called Archimedean spirals on the crankshaft in order to oil demands on the piston is known.

Regardless of which system is used concretely for effecting the oil circuit, it is in any case the case that the swirled and heated oil 4 continuously precipitates on the compressor housing wall and flows down there in the direction of gravity (see Figure 3 ). In this way, the heat absorbed by the oil 4 can be released to the compressor housing 1 and subsequently discharged to the environment.

In order to prevent the oil 4 from contacting the suction channel 2 or the pressure channel 3 during its downflow, for example on the section of the suction channel 2 protruding into the compressor housing or in the region of the pressure tube guided through the wall of the compressor housing, and a heat exchange from the oil associated therewith 4 to suction port 2 or from (hot). Pressure channel 3 is carried on the oil 4, which causes a further heating of the compressor housing 1 and thus also of the suction channel 2, according to the invention at least one deflection means is provided which shields the suction channel 2 and 3 pressure channel of herabfließendem oil 4.

The deflection means is arranged above the passage of the suction channel 2 or pressure channel 3 through the connection opening 10 of the compressor housing wall 1, the distance from the deflection means to the suction channel 2 / pressure channel 3 or to the connecting element 7 enclosing this depending on the application according to the size of the circulating oil volume, the type of the respective pump or Verwirbelungstechnik, and the specific interior geometry and component arrangement of the refrigerant compressor is to be selected individually, but the distance may not be so large that the fluid flow of the already passed past the deflection means 4 oil again in the direction of the suction channel 2 / Spread pressure channel 3 and could come into contact with these.

In a preferred embodiment according to Figure 4 the deflection means is designed as a conductive extension 5 protruding inward from the compressor housing wall. As shown by the illustration in Figure 4 to understand, the Leitfortsatz 5 shields the suction channel 2 and the pressure channel 3 from the flowing down to the compressor housing wall 1 oil 4, by this can flow along the longitudinal extent of the Leitfortsatzes 5 or drain. The oil 4 thus passes through the immediate region of the passage of the suction channel 2 and the pressure channel 3 through the connection opening 10 in the compressor housing wall 1, without coming into contact with the suction channel 2 or the pressure channel 3.

The guide extension 5 is preferably a separately manufactured component which is attached to the inside of the compressor housing 1 by means of conventional connection technology, such as welding, soldering or gluing. If this proves to be advantageous under the respective requirements of series production, however, the lead extension 5 can also be mounted in the intended position by means of dowel pins, a latching connection or the like become. The one-piece production of the Leitfortsatzes 5 with the compressor housing is possible and represents a simplification of the production.

Although according to Figure 4 umbrella-shaped, so formed with an upwardly convex longitudinal extent, the Leitfortsatz 5 may also be formed, for example, V-shaped. In the case of a V-shaped configuration, the tip of the V in the operating position of the compressor housing 1 is arranged above the suction channel 2 or pressure channel 3, so that the flowing down to the compressor housing wall stream of the oil 4 is divided at the top of the V to the left and right and accordingly the gravity on the two legs of the V flows without contacting the suction channel 2 or 3 pressure channel.

In order to guide the oil completely around the suction channel 2 or pressure channel 3, the two legs of the V are pulled down below the suction channel 2 or pressure channel 3 and shield the suction channel 2 or the pressure channel 3 to a certain extent like a pitched roof.

It is understood that the subject V-shape can be designed in many variations, such as with curved portions of the longitudinal extension or the like.

It may also be advantageous to provide the main extension 5 with longitudinal grooves, ie with notches arranged along its longitudinal extension. In this way it is prevented that around the Leitfortsatz 5 creeping oil flows to the suction channel 2 and Druckkanal 3 arrive (not shown).

The problem of crawling amounts of oil which move around the Leitfortsatz 5 and continue from the top of the Leitfortsatzes 5 on the underside, from where they then directly to the suction channel 2 and Druckkanal 3rd can also be met in such a way that the Leitfortsatz is equal to a gutter with a facing away in the suction channel 2 and the pressure channel 3 direction concave cross-sectional profile is provided. Such an embodiment is shown schematically in FIG Figure 6 shown.

Also, an arrangement of the Leitfortsatzes 5 according to Figure 7 according to which this encloses an acute angle or an angle α <90 ° with the section of the compressor housing wall extending above the contact point of the main extension 5 with the compressor housing 1, a described creep of the oil 4 can be obstructed, since in this case the trickle 4 'forming oil 4 is guided according to the gravitational tendency along the inclination of the Leitfortsatzes 5.

Instead of on the compressor housing wall inwardly projecting Leitfortsatzes 5 can as a deflection in an alternative embodiment according to Figure 5 Also find at least one recess 6 in the compressor housing wall 1 use. Which recess profile is chosen is up to the possibilities of the manufacturing method used and the individual design. By way of example, a simple V-notch shape, a simple groove, a T-groove, a dovetail groove or a rounded groove may be mentioned at this point.

In any case, the provision of a recess 6 also results in the oil 4 flowing down the compressor housing wall and impinging on the profiled recess 6, as shown in FIG Figure 5 continued along the course of the recess 6 and the side of the suction channel 2 and the pressure channel 3 is guided past.

Also essential in this embodiment variant is that the recess 6 extends continuously over the suction channel 2 or pressure channel 3. In the specific embodiment of the recess 6 with respect to their longitudinal extent is thus valid the same thing that has been said so far for the design of the lead extension 5: So the recess 6 may thus have any gradients and be executed, for example, umbrella-shaped or V-shaped.

The recess 6 is produced in a known manner by means of cutting or non-cutting processing methods.

If necessary, it may be necessary to arrange a plurality of conductive extensions 5 or recesses 6 one above the other in order to completely exclude any contact of the downflowing oil 4 with the suction channel 2 or pressure channel 3 by dripping and oil quantities creeping around the deflection means. For example, if a recess 6 arranged approximately parallel to this is provided below a guide extension 5, oil drops or creeping amounts of oil which overcome the guide extension 5 and continue to move in the direction of the suction channel 2 or pressure channel 3 are prevented at the latest from the recess 6 to contact the suction channel 2 and 3 pressure channel.

Claims (9)

1. A hermetically encapsulated refrigerant compressor which has a hermetically sealed compressor housing (1), in the interior of which operates a refrigerant-compressing piston-cylinder unit, and is provided with a suction duct (2), via which refrigerant is conveyed into the compressor housing (1) or in a suction muffler connected to the piston-cylinder unit, and is provided with a pressure duct (3), via which refrigerant is conveyed out of the compressor housing (1) by the piston-cylinder unit, characterized in that in the operating position of the compressor housing (1) deflection means (5, 6) are provided on the same above the passage of the suction duct (2) or pressure duct (3) through the compressor housing wall, which deflection means prevent contact of oil (4) flowing down the compressor housing wall with the suction duct (2) or pressure duct (3).
2. A hermetically encapsulated refrigerant compressor according to claim 1, characterized in that the deflection means are designed as at least one guide extension (5) which protrudes inwardly from the compressor housing wall.
3. A hermetically encapsulated refrigerant compressor according to claim 1, characterized in that the deflection means are designed as at least one recess (6), preferably at least one groove, in the compressor housing wall.
4. A hermetically encapsulated refrigerant compressor according to claim 2 or 3, characterized in that the guide extension (5) or the recess (6) is substantially arranged in the shape of a V and the tip of the V is arranged above the suction duct (2) or pressure duct (3) in the operating position of the compressor housing (1).
5. A hermetically encapsulated refrigerant compressor according to claim 4, characterized in that the two legs of the V extend until beneath the suction duct (2) or pressure duct (3).
6. A hermetically encapsulated refrigerant compressor according to one of the claims 2 to 5, characterized in that the guide extension (5) or the recess (6) is arranged substantially in the manner of an umbrella or has an upwardly convex longitudinal extension.
7. A hermetically encapsulated refrigerant compressor according to one of the claims 2 to 5, characterized in that the guide extension (5) comprises a groove-like cross-sectional profile or one that is concave in the direction averted in the suction duct (2) or pressure duct (3).
8. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 7, characterized in that several deflection means are arranged on top of one another.
9. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 8, characterized in that the suction duct and/or the pressure duct are arranged in a tubular way.

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