Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/32—Cooling devices
  • B60H1/3204—Cooling devices using compression
  • B60H1/3225—Cooling devices using compression characterised by safety arrangements, e.g. compressor anti-seizure means or by signalling devices
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
  • F04B39/06—Cooling; Heating; Prevention of freezing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
  • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
  • F04B39/125—Cylinder heads
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D9/00—Couplings with safety member for disconnecting, e.g. breaking or melting member
  • F16D9/02—Couplings with safety member for disconnecting, e.g. breaking or melting member by thermal means, e.g. melting member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D9/00—Couplings with safety member for disconnecting, e.g. breaking or melting member
  • F16D9/06—Couplings with safety member for disconnecting, e.g. breaking or melting member by breaking due to shear stress
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
  • F16H55/32—Friction members
  • F16H55/36—Pulleys
  • F16H2055/366—Pulleys with means providing resilience or vibration damping
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S417/00—Pumps
  • Y10S417/01—Materials digest

Definitions

• the invention relates to a compressor, in particular for the air conditioning system of a motor vehicle, with a housing and a compressor unit arranged in the housing for drawing in and compressing a refrigerant, the compressor unit being driven by a belt via a drive shaft and a drive wheel coupled to the drive shaft, and wherein the drive wheel has a pulley body which engages with the belt and which is coupled directly or indirectly to the drive shaft via a coupling device.
• Compressors of the type in question are mostly referred to as air conditioning compressors and are known in practice in a wide variety of embodiments.
• Such compressors comprise a housing which encloses a compressor or pump unit driven from outside.
• the pump unit for example designed as an axial piston pump, in turn comprises at least one piston which can be moved back and forth in a cylinder block.
• Such a compressor is usually equipped with several pistons and works according to the swash plate principle or swivel plate principle. When the swashplate rotates, the pistons are moved back and forth in the direction of their longitudinal axis.
• the principle briefly discussed above is only mentioned here by way of example.
• the compressors in question are driven by a belt which is guided by a pulley referred to below as the drive wheel.
• the belt is in turn driven by the crankshaft of the internal combustion engine of a motor vehicle.
• Malfunctions can occur when operating the compressor.
• the compressor unit or the drive shaft can block. If the belt covers the drive wheel with a very small wrap angle, the belt is likely to slip on the drive wheel or on the belt pulley, the drive wheel becoming very hot. After a short time, this leads to damage and ultimately destruction of the belt, so that the units which are further driven by the belt, for example as the water pump or the alternator, are no longer driven. The motor vehicle is therefore no longer functional.
• the belt covers the drive wheel or the pulley with a larger wrap angle, for example by more than 180 °, the belt can hardly slide on the drive wheel or on the pulley. This will either break the belt or stall the engine. Even in such a case, the motor vehicle is no longer operational.
• an electromagnetic clutch has already been integrated into the drive wheel of the compressor. If the belt slips or the coupling halves slip, this leads to very strong heating of the coupling. If a predetermined temperature is reached, a fuse interrupts the coil current and the clutch decouples the compressor, so that the belt can move with the pulley body of the drive wheel. This ensures the operation of safety-relevant components of the motor vehicle, for example the water pump and / or the alternator, which are also driven by this belt.
• the electromagnetic clutch known from practice is problematic insofar as it has a relatively large construction, is complex in terms of the individual components and thus represents a very considerable cost factor. Above all, due to its complexity, such an electromagnetic clutch causes a very considerable weight load, which diametrically opposes a weight reduction that is always sought in today's motor vehicle construction. Due to the considerable size of the compressor, it is not suitable for installation in small engine compartments.
• an overload coupling is provided with a disk-shaped, externally toothed rubber body, the teeth of which shear off in the event of excessive stress.
• This is a purely mechanical overload coupling, the decoupling behavior of which is only certain bandwidth is definable. In any case, such an overload coupling is not very reliable.
• the invention relates to a compressor, in particular for the air conditioning system of a motor vehicle, with a housing and a compressor unit arranged in the housing for sucking and compressing a refrigerant, the refrigerant also passing from a suction area preferably formed in an end-side housing cover through the compressor unit preferably flows in the housing cover formed outlet area.
• Air conditioning compressors of various designs work with one refrigerant.
• an inert gas for example CO 2
• CO 2 can be used as the refrigerant, which is harmless from an environmental point of view.
• the use of such a refrigerant leads to higher pressures within the compressor, which necessitates very special design measures, for example with regard to the choice of material and wall thickness of the housing.
• a high-strength material is used for the housing of the compressor, it is readily possible to absorb the high pressures required or occurring in the case of a refrigerant which has a high density even in the suction state. For example, it is necessary to withstand burst pressures of up to 30 MPa at outlet temperatures in the range of approximately 160 ° C to 170 ° C.
• compressors of the type in question here comprise a suction area and an outlet area. While on the suction side - in the intake area - refrigerant flows in with a temperature in the range between 30 ° C and 40 ° C, on the pressure side, i.e. in the outlet area, temperatures in the range between 120 ° C and up to about 170 ° C.
• the compressor housing is usually made of metal, for example aluminum, stainless steel or high-strength steel.
• the high temperature in the outlet area will - inevitably - affect the intake area affect when this is warmed up via the housing material coming into contact with the refrigerant and the "interior" of the compressor.
• the suction-side gaseous refrigerant is heated thereby, whereby its density decreases. This in turn leads to a loss of delivery or a reduction in the mass flow of refrigerant and thus to a loss of performance of the compressor. Due to the temperature influence of the outlet area compared to the suction area, the efficiency of a conventional compressor is significantly reduced.
• the present invention has for its object to design and develop a compressor of the type mentioned in such a way that the efficiency is cheaper compared to conventional compressors, the compressor is smaller, the weight is reduced and the compressor can therefore be manufactured more easily and inexpensively. Furthermore, the performance is to be increased and at least the same safety, in particular protection of the belt drive and the internal combustion engine, is to be ensured with less effort as with previously known compressors.
• a compressor of the type mentioned at the outset is characterized in that the coupling device is forcibly decoupled when a defined thermal and / or mechanical load limit is exceeded.
• the decoupling must take place compulsorily, namely when a defined thermal load limit, a defined mechanical load limit is exceeded, or when one of the two aforementioned load limits is exceeded. Ultimately, it should be ensured here that a forced decoupling takes place in any case, the type of the load limit to be exceeded and the amount of the load capacity being specifiable.
• the aim is to ensure that the belt can continue to run more or less unhindered even when the compressor unit or the drive shaft is blocked, with only the compressor being out of operation due to the defect that has occurred.
• the coupling device coupling during proper operation of the compressor could comprise a coupling element acting between the pulley body and a coupling disc coupled to the drive shaft.
• This coupling element is responsible for the actual coupling and thus for driving the compressor unit.
• the coupling element is arranged between the inner surface of the pulley body and the outer surface of the coupling disc, in which case the two surfaces - inner surface of the pulley body and outer surface of the coupling disc - are arranged coaxially to one another are.
• the pulley body serving to receive the belt extends essentially in a ring shape around the coupling disk, both the pulley body and the coupling disk having two mutually adjacent and thereby parallel surfaces.
• the coupling device with the coupling element is arranged in between.
• a vibration damper assigned to the coupling device for damping the torsional vibrations could be provided between the coupling element and the coupling disk or a drive flange of the compressor unit, which can be an elastomer element or a rubber-metal element.
• the coupling device can comprise the coupling element on the one hand and the vibration damper on the other hand.
• the component used for decoupling is, however, the coupling element.
• the coupling element having to achieve a defined decoupling when a thermal and / or mechanical load limit is exceeded.
• the coupling element could be designed as a spring, which acts when the temperature is above a predetermined temperature. limit value at least partially loses its elastic spring force and thereby decouples.
• the coupling achieved by spring force is thus canceled by a quasi "weakening" of the spring, the spring also being able to have a double function to the extent that the spring also permits decoupling when a mechanical load limit is exceeded, namely acting in the sense of a slip coupling. Both modes of operation - decoupling when a thermal and a mechanical load limit are exceeded - are possible.
• the coupling element as a permanent magnet which interacts directly or indirectly with the magnetic material of the pulley body and the coupling disc.
• This permanent magnet should at least partially lose its magnetic effect when exposed to temperature above a predetermined limit and thereby decouple. In this respect, the decoupling would be guaranteed if a definable thermal load limit was exceeded.
• a magnetically operating coupling device could also bring about a form-fitting coupling, namely in that the coupling element comprises form-fittingly coupling magnetic coupling parts and an at least weak electromagnet which, when the drive shaft is detected, disengages the coupling parts and thereby decouples them.
• the coupling element comprises form-fittingly coupling magnetic coupling parts and an at least weak electromagnet which, when the drive shaft is detected, disengages the coupling parts and thereby decouples them.
• the coupling element is designed in the form of an annular pressure body for non-positive coupling between the pulley body and the coupling disc or the drive shaft. Due to its state pressed between the components, this pressure element causes a force-locking coupling, and in the case of the additional provision of a vibration damper, the coupling element and thus the pressure element is arranged between the pulley body and the vibration damper.
• the pressure body between the pulley body and the drive shaft in each case via those components which are arranged between them in functional terms.
• the pressure body could be designed as a bellows, preferably as a thin-walled metal bellows.
• a thin-walled configuration would be advantageous insofar as it could be spatially expanded by a flow medium.
• the pressure body could namely be filled with a flow medium under predeterminable pressure for non-positive coupling, the flow medium being a gas, a liquid or at least partially a liquid and otherwise a gas.
• the pressure body in the pressurized state effects a forced coupling, so that the compressor is driven in rotation via the pulley body.
• the flow medium could have such a high coefficient of thermal expansion that it opens the pressure body at least in regions or even bursts when a predetermined temperature is exceeded due to the then prevailing internal pressure and thereby decouples it. In any case, this presupposes that the belt slips over the pulley body, heats it up to about 300 ° C. in practice, and transmits the temperature to the pressure body lying directly on the inner surface of the pulley body.
• the temperature increase leads to such an expansion of the flow medium that the pressure body leaks or even bursts, as a result of which the pressure can escape and as a result of which the pressure body no longer applies the contact pressure required for the positive coupling between the pulley body and the drive shaft or coupling disc. Decoupling is thus achieved when a thermal limit value is exceeded.
• the pressure body has at least one mechanical predetermined breaking point which serves to relieve pressure and thus to decouple.
• a predetermined breaking point could tear open, so that the inside of the pressure body prevailing pressure or the flow medium present there can escape.
• the force required for tearing is less than the force with which the pressure body is held in position relative to the coupling disk or to the vibration damper arranged therebetween by static friction, adhesion or the like. In this respect, the decoupling would be guaranteed if a mechanical load limit was exceeded.
• the pressure body could have at least one fuse, which serves to relieve pressure and thus to decouple, which melts regardless of a possible rise in pressure within the pressure body when a predeterminable temperature is reached and releases the pressure medium.
• a plurality of fuses are provided along the circumference of the pressure body, so that, regardless of the angular position of the pulley or the pulley body, at least one fusible link is arranged in the vicinity of the region of the pulley that is hot due to the belt slipping. In any case, this also creates a forced decoupling by exceeding a defined thermal load limit.
• the pressure body can have at least one mechanical predetermined breaking point serving to relieve pressure and at least one fuse for decoupling serving to relieve pressure. It should be ensured that the pressure body is held firmly in place, but at least with a high coefficient of static friction, so that the predetermined breaking point actually tears open with a corresponding mechanical load.
• the pressure body With regard to a specific configuration of the pressure body, it is a further advantage if it extends in an annular shape, preferably in the sense of a hollow cylinder, between the inner surface of the pulley body and the outer surface of the coupling disc or a vibration damper.
• the pressure body extends in an annular manner between the pulley body and the coupling disk, specifically between the two inner surfaces of the components in question, which are to be coupled to one another.
• the vibration damper provided there can serve as a quasi intermediate element, but has nothing to do with the coupling or decoupling from a functional point of view.
• the latter could have an essentially rectangular pressure chamber, with this rectangular pressure chamber - in longitudinal section - tapered, outwardly directed separating regions of the pressure body from the pressure chamber.
• These separating areas have closely adjacent walls which, due to their proximity to one another, are closed altogether, zonally or selectively.
• a connection of the walls in the separation areas can also be designed in the sense of a predetermined breaking point.
• two mutually opposite separating areas are formed which, in the longitudinal section of the pressure body, connect their legs to the pressure chamber in a U-shape, the one separation area being used for decoupling when a defined thermal load limit is exceeded and the other separation area when a defined mechanical load limit is exceeded.
• One separation area is a fuse and the other separation area is a mechanical predetermined breaking point, and both the melting fuse and the predetermined breaking point can be provided continuously, zonally or only selectively along the entire circumference of the pressure body.
• the compressor in contact with the refrigerant coming components preferably the walls forming the flow path between the suction area and the outlet area, are at least slightly and in some areas thermally insulated from the refrigerant.
• the problems analyzed here can be reduced by, to a certain extent, heat-insulating the components that come into contact with the refrigerant, so that the heating of the drawn-in refrigerant is at least reduced.
• the walls forming the flow path between the suction area and the outlet area are at least slightly - in some areas - thermally insulated from the refrigerant.
• thermal insulation here is not to be understood as complete insulation to avoid heat transfer.
• this is to be understood to mean a reduction in the thermal conductivity from the components of the compressor to the refrigerant by means of passive measures, a heat insulation which is provided in some areas already reducing the warming-up of the drawn-in refrigerant and thus increasing the efficiency of the compressor.
• the thermal insulation could be designed as a lining made of a material with a low thermal conductivity. Accordingly, the walls forming the flow path within the compressor are lined, and here too, a partial lining in the suction area leads to very considerable success.
• the heat insulation could be designed as a coating made of a material having a low thermal conductivity.
• the thermal insulation is provided on the inner wall of the intake duct. This alone reduces the heating of the drawn-in refrigerant on the suction side.
• the heat insulation is provided in a particularly advantageous manner on the inner wall of the entire suction area. This further reduces heating of the drawn-in refrigerant in the suction area.
• both the suction area and the outlet area are formed in a housing cover, which is often also referred to as a pressure cover
• the thermal insulation could equally be provided on the inner wall of the outlet channel or even on the inner wall of the entire outlet area, namely the entire one Provide the inside wall of the housing cover with appropriate thermal insulation. To this extent, the thermal insulation could be handled uniformly on the entire inner wall of the housing cover or applied there uniformly in the case of a coating.
• the thermal insulation could be in the form of a liner.
• the lining could be at least slightly spaced from the inner wall of the housing cover, so that there is a space between the actual inner wall of the housing cover and the lining. This space further reduces the heat transfer between the housing cover and the refrigerant.
• the lining with partially formed, preferably integral spacers could rest against the inner wall of the housing cover, so that the distance between the insert and the inner wall of the housing cover is not reduced due to the inflowing refrigerant.
• the lining or coating could be designed as a porous foam, as a result of which a gas cushion - within the foam - leads to a reduction in the heat transfer between the inner wall of the housing cover and the refrigerant.
• the foam should have an open porosity so that the structure is not destroyed when pressure differences occur.
• the inner wall of the housing cover could also be coated as a whole, namely wherever the flow path of the refrigerant is defined by the inner wall of the housing cover.
• a coating it is also conceivable to give it a surface structure which favors the flow, for example to provide a defined roughness there, which can have the surface structure of a shark skin. In any case, such a measure can favor the flow within the suction area and the outlet area.
• the housing cover comprising the suction region and the outlet region borders on a valve plate, so that the flow path of the refrigerant is at least partially defined between the valve plate and the inner wall of the housing cover.
• the thermal insulation is also provided on the valve plate.
• the valve plate on the side facing the housing cover could be be stratified, as can also be the case with the inner wall of the housing cover.
• the above explanations relate to a reduction in the thermal conductivity between the inner wall of the housing cover and the refrigerant. Heating of the refrigerant can be further reduced by additionally coating the surfaces in the pump unit that form the flow path or adjoin the flow path with a material that has a low conductivity. Such a coating could have two tasks, namely the desired reduction in heat transfer between the components of the compressor and the refrigerant and the application of a wear protection layer to extend the life of the compressor.
• the pump unit is designed as an axial piston pump
• the cylinder running surface in the cylinder block could be coated with the material having a low conductivity.
• a thermal insulation applied there, which also serves as a wear protection layer, is of particular advantage due to the mechanical stress that usually occurs there.
• a further measure for reducing the heat transfer could be that the housing cover itself is made of one material is manufactured with low thermal conductivity.
• the housing cover could consist of a metal with low thermal conductivity, for example a high-strength steel, which has a considerably lower thermal conductivity than aluminum.
• the housing cover is made of a ceramic material or a ceramic composite material, as a result of which the heat transfer is considerably reduced even without coating or lining the flow path.
• FIG. 1 is a schematic longitudinal section of an embodiment of a generic compressor with the essential components
• FIG. 3 shows the object from FIG. 2 in detail "X" in an enlarged view
• Fig. 5 shows the object of Fig. 4 in detail "Y" in an enlarged view
• FIG. 6 in a schematic side view, partly and in section, a further embodiment of a compress according to the invention sors, where only the suction area and the outlet area are shown in the housing cover and
• FIG. 7 shows an enlarged side view, in section, of the suction area in the housing cover, a lining spaced apart from the inner wall of the housing cover being provided as thermal insulation.
• FIG. 1 The exemplary embodiment of a generic compressor shown only by way of example in FIG. 1 is an axial piston compressor, the compressor unit 1 (not described in more detail here) being arranged in a housing 2.
• the housing 2 essentially comprises two housing parts 3, 4, the housing part 3 forming a so-called drive chamber 5 in which the compressor unit
• the compressor unit 1 is driven via a pulley 6, for example by an internal combustion engine.
• the drive takes place from there via a drive shaft 7, which rotates about an axis of rotation 8.
• the drive shaft 7 is rotatably supported in the housing 2 and in the area of the pulley 6.
• a swash plate 10 which has bearings
• I I acts on a non-rotatably mounted receiving disc 12 in the housing 2.
• the receiving disc 12 is coupled to the piston or pistons 9 via a connecting rod 13. According to this arrangement, when the swash plate 10 rotates, the piston 9 moves back and forth over the receiving plate 12 in the direction of its longitudinal axis, the exemplary embodiment shown here comprising a plurality of pistons 9.
• the compressor shown here is a compressor for the air conditioning system of a motor vehicle, it is driven by the internal combustion engine of a motor vehicle, not shown here, with a drive torque in a drive wheel via a suitable pulley which is coupled to the crankshaft of the internal combustion engine 14 of the compressor is initiated.
• This Drive wheel 14 comprises a pulley body 15, over which the belt 16 is guided.
• the pulley body 15 is brought into a rotational movement by the belt 16.
• the torque introduced into the pulley body 15 is - in the exemplary embodiments shown in FIGS. 2 to 5 - transmitted to the drive shaft 7 via a coupling device 17, the coupling device 17 - in the exemplary embodiments selected here - comprising a vibration damper 18.
• the coupling device 17 is designed in such a way that when a defined thermal and / or mechanical load limit is exceeded, it is forcibly decoupled, so that the pulley body 15 can rotate freely in the decoupled state.
• the coupling device 17 comprises a coupling element 20 acting between the pulley body 15 and the drive shaft 7 or the coupling disc 19, the coupling element 20 being arranged between the inner surface of the pulley body 15 and the outer surface of the coupling disc 19 and wherein the two surfaces - inner surface of the pulley body 15 and outer surface of the coupling disc 19 - are arranged coaxially to one another.
• a vibration damper 18 assigned to the coupling device 17 for damping the torsional vibrations is provided between the coupling element 20 and the coupling disk 19 or between the two adjacent surfaces of these components, this vibration damper 18 having nothing to do with the actual process of coupling or decoupling has to do.
• Figures 2 to 5 also show that the coupling element 20 is designed in the sense of an annular pressure body 21 for the non-positive coupling between the pulley body 15 and the coupling disc 19.
• the pressure body 21 is concerned around a thin-walled metal bellows, which is filled with a flow medium under a predeterminable pressure for frictional coupling.
• the clamping effect caused by the pressure body 21 brings about the coupling between the pulley body 15 and the coupling disk 19, wherein the pressure body 21 can be fixed in its position by means of gluing, soldering, spot welding or the like.
• FIG. 3 shows that the pressure body 21 has mechanical predetermined breaking points 22 for pressure relief and thus for decoupling. Fuses 23 are also provided there, so that in the exemplary embodiment shown in FIGS. 2 and 3, a combination of a coupling device 17 is realized, which forcibly decouples when both a defined thermal and a defined mechanical load limit are exceeded.
• the mechanical predetermined breaking points 22 and the fuses 23 do not lie opposite one another as in the exemplary embodiment shown in FIGS. 2 and 3, but rather are only formed on the side of the pressure body 21 facing the inner surface of the pulley body 15 .
• FIGS. 2 to 5 further show jointly that the pressure body 21 comprises a pressure chamber 24 which is essentially rectangular in longitudinal section and adjoining outwardly directed separating regions 25 which are tapered in cross-section with respect to the pressure chamber 24, with the one shown in FIGS Embodiment shown two separation areas are arranged opposite each other, which in the longitudinal section of the pressure body 21 connect U-shaped with their legs to the actual pressure chamber 24.
• a pressure chamber 24 which is essentially rectangular in longitudinal section and adjoining outwardly directed separating regions 25 which are tapered in cross-section with respect to the pressure chamber 24, with the one shown in FIGS Embodiment shown two separation areas are arranged opposite each other, which in the longitudinal section of the pressure body 21 connect U-shaped with their legs to the actual pressure chamber 24.
• a separation area 25 is provided only on one side of the pressure body 21 - on the side facing the inner surface of the pulley body 15 - at which both the mechanical predetermined breaking points 22 and the fuses 23 are provided.
• needle bearings 26 are provided according to the representations in FIGS. 2 and 4, which support the drive shaft 7 outside the drive chamber 5.
• the needle bearings 26 serve to mount the coupling disk 19. Because of the provision of the needle bearings 26 outside the drive chamber 5, these bearings run in an ambient atmosphere, with seals
• FIGS. 2 and 4 also show that friction linings 28 are provided between the pulley body 15 and the coupling disk 19, which serve as an "emergency bearing” or bearing surface or bearing coating. If the compressor locks up and decoupling occurs as described above, then the previously discussed needle bearings 26 are also in place so that the pulley body 15 can continue to rotate freely for an acceptable period of time, for example for at least a few hours Emergency storage of the pulley body 15 required over the friction lining
• Temperature-resistant storage materials can be used for this.
• the compressor comprises a housing 101 and a compression unit 102 arranged in the housing 101 for sucking in and compressing a refrigerant, which refrigerant can be CO.
• the refrigerant flows from a suction area 104 formed in a front housing cover 103 through the compressor unit 102 into the outlet area 105 also formed in the housing cover 103.
• the components of the compressor that come into contact with the refrigerant namely the walls forming the flow path 106 between the suction area 104 and the outlet area 105, are at least partially thermally insulated from the refrigerant.
• the heat insulation 107 is designed as a coating made of a material having a low thermal conductivity, the heat insulation 107 being provided both on the inner wall 108 of the intake duct 109 and on the inner wall 110 of the outlet duct 111.
• the entire inner walls 108, 110 of the suction area 104 and the outlet area 105 are coated in a heat-insulating manner, the entire inner wall 108, 110 of the housing cover 103 ultimately being coated for this purpose.
• the suction region 104 it is indicated for the suction region 104 that the inner wall 108, 110 of the housing cover 103 is lined there, namely in the form of a loose insert 112.
• This insert 112 is of the inner wall 108, 110 slightly spaced, this spacing being brought about by integral spacers 113.
• the spacers 113 lie directly on the inner wall 108, 110 of the housing cover 103.
• FIG. 6 further shows that the housing cover 103 is adjacent to a valve plate 114.
• Thermal insulation 115 is also provided on the valve plate 114, the valve plate 114 being coated there on the side facing the housing cover 103, preferably with the same material as the inner wall 108, 110 of the housing cover 103. In this respect, that is between the housing cover 103 and Flow plate formed entirely valve plate 114 and thus heat insulated.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Compressor (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
• Applications Or Details Of Rotary Compressors (AREA)

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ID=26039567

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Citations (8)

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• 1998
  • 1998-08-31 DE DE59809739T patent/DE59809739D1/de not_active Expired - Lifetime
  • 1998-08-31 DE DE19881579T patent/DE19881579D2/de not_active Expired - Fee Related
  • 1998-08-31 EP EP98951242A patent/EP1007847B1/de not_active Revoked
  • 1998-08-31 DE DE19881577T patent/DE19881577D2/de not_active Ceased
  • 1998-08-31 WO PCT/DE1998/002560 patent/WO1999011934A1/de not_active Ceased
  • 1998-08-31 WO PCT/DE1998/002559 patent/WO1999011929A2/de not_active Ceased
  • 1998-08-31 US US09/486,599 patent/US6457947B1/en not_active Expired - Fee Related
  • 1998-08-31 GB GB0004880A patent/GB2348467A/en not_active Withdrawn
  • 1998-08-31 JP JP2000508907A patent/JP4181745B2/ja not_active Expired - Fee Related

Patent Citations (8)

Non-Patent Citations (3)

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