EP2806164B1 - Scroll compressor and CO2 vehicle air conditioner with a scroll compressor - Google Patents
Scroll compressor and CO2 vehicle air conditioner with a scroll compressor Download PDFInfo
- Publication number
- EP2806164B1 EP2806164B1 EP13168729.5A EP13168729A EP2806164B1 EP 2806164 B1 EP2806164 B1 EP 2806164B1 EP 13168729 A EP13168729 A EP 13168729A EP 2806164 B1 EP2806164 B1 EP 2806164B1
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- European Patent Office
- Prior art keywords
- spiral
- scroll compressor
- displacement
- compressor according
- counter
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0253—Details concerning the base
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0284—Details of the wrap tips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/261—Carbon dioxide (CO2)
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
Definitions
- the invention relates to a scroll compressor for a CO 2 vehicle air conditioning system, and a CO 2 vehicle air conditioning system with such a scroll compressor.
- Non-combustible refrigerants are used for the air conditioning of motor vehicles in order to avoid the risk of explosion inside the vehicle in the event of an accident.
- the refrigerants used so far are either already banned or at least classified as problematic because of their high global warming potential.
- CO 2 non-combustible refrigerant
- CO 2 air conditioners operate with high operating pressures, which make special demands on the strength and tightness of the system components. The advantage associated with the high operating pressure is that the higher density of CO 2 requires a smaller volume flow to provide a relatively high refrigeration capacity.
- a scroll compressor for a CO 2 vehicle air conditioner is off JP 2006/144635 A known.
- a scroll compressor with the features of the preamble of claim 1 is made US 2009/0098001 A1 known.
- Such scroll compressors have variable speed electric drives to control the cooling capacity of the compressor.
- US 6,273,692 B1 a scroll compressor with a mechanical drive, which is connectable by an electromagnetic clutch to the compressor unit.
- US 2002/0081224 A1 discloses a variable low-pressure scroll compressor which can be switched on and off by a radial movement of one of the two scroll spirals. In this case, the eccentricity between the two scroll spirals is released, which thus get out of engagement in the radial direction.
- the invention has for its object to provide a scroll compressor for a CO 2 vehicle air conditioner, which is simple and improved in view of the tightness.
- the invention is also based on the object of specifying a CO 2 vehicle air conditioning system with such a scroll compressor.
- the object is achieved by a scroll compressor for a CO 2 vehicle air conditioner with the features of claim 1.
- the object is achieved by the subject matter of claim 11.
- the invention is suitable for variable speed or digitally controlled scroll compressors.
- the invention has the advantage that tilting moments which act on the displacement spiral are reduced, thereby achieving a uniform contact pressure of the displacement spiral.
- the uniform pressure leads to the fact that at each contact point between the two spirals substantially the same tightness prevails.
- the invention provides that the eccentric bearing is arranged in the displacement between the positive displacement spiral and the counter-spiral and has a bearing bush, which is integrally formed with the positive displacement spiral and whose bottom is aligned with the end face of the turns of the positive displacement spiral.
- the eccentric bearing is recessed in the VerdrDeutscherspirale in the direction of the pressure chamber, wherein the eccentric bearing is at least partially equal to the turns of the counter-spiral.
- the eccentric bearing so at least partially immersed in the counter-spiral. That in the known low-pressure scroll compressors used for final compression innermost volume between the displacement spiral and the counter-spiral is at least partially used to accommodate the eccentric bearing. As a result, lever lengths and tilting moments are effectively reduced, because the immersion depth of the eccentric bearing is particularly large.
- the invention also has the advantage that the suction side is securely separated from the high pressure side, because the bearing bush is formed integrally with the positive displacement spiral. Thus, no seals between the eccentric and the positive spiral are required.
- the bushing participates in the compression, because this one hand is in the displacement and on the other hand, the bottom of which is aligned with the end face of the turns of the positive displacement spiral.
- the bearing bush in the circumferential direction cooperates with the turns of the counter-spiral and in the axial direction with a sealing surface of the counter-spiral.
- any tilting moments are further reduced if the displacement spiral has a central recess in which at least partially a counterweight is accommodated, which is connected to the eccentric bearing.
- the surface of the eccentric bearing is smaller than the central area within the innermost turn of the counter-spiral such that at least one gas ejection opening formed in the region of the central area is accessible for fluid communication with the pressure chamber. This avoids that the gas ejection opening is covered by the recessed eccentric bearing.
- a further improvement of the tightness is achieved when the turns of the positive displacement spiral and the counter-spiral each have lubricating bevels.
- Lubricants can accumulate in the lubricating surfaces, which improves the sliding properties and reduces local resistance forces, so that there is a uniform contact pressure and thus a good seal between the two spirals. If the lubricating bevels are formed at both outer edges of each of the turns of the positive displacement spiral and the counter-spiral, good lubrication in both directions takes place in the reciprocal movement of the positive displacement spiral.
- the lubricating chamfers and / or a radius are formed in the corners between the turns and a sealing surface of the displacement spiral.
- the lubricating chamfers and / or a radius may be formed in the corners between the turns and a sealing surface of the counter-spiral.
- the gullies or radii in the corners preferably cooperate with the gullies on both outer edges of each of the turns of the positive displacement spiral and the counter-spiral. As a result, the sealing effect in the region of the respective gas chamber or gas pocket is improved, which is formed by the radial contact between the displacement spiral and the counter-spiral.
- the tightness can be improved if a closed to the suction side receiving space for the eccentric bearing fluidly connected to the pressure chamber and a rear wall of the positive displacement spiral can be acted upon by a contact pressure.
- the distance between the center of the counter-spiral and the center of the displacement spiral maximally 1.5 mm, in particular at most 1.2 mm, in particular at most 1.0 mm, in particular maximally 0.8 mm, in particular maximally 0.6 mm, in particular maximally 0.4 mm, in particular not more than 0.2 mm.
- the lower limit can be 0.1 mm.
- the counter-spiral has a winding angle of 660 ° to 720 °, in particular from 680 ° to 700 °, whereby a sufficient compression of the refrigerant is achieved.
- the volume of the pressure chamber by a factor of 5-7, in particular by a factor of 6, greater than the suction volume per revolution of the displacement spiral, whereby gas pulsations are effectively reduced.
- the scroll compressor described in detail below is designed for use in a CO 2 vehicle air conditioning system which typically includes a gas cooler, an internal heat exchanger, a throttle, an evaporator, and a compressor. Such systems are designed for maximum pressures over 100 bar.
- the compressor is a scroll compressor, also referred to as a scroll compressor.
- the scroll compressor has a mechanical drive 10 in the form of a pulley.
- the pulley may be connected in use to an electric motor or an internal combustion engine.
- the scroll compressor further includes a housing 30 having a housing cover 31 which closes the high pressure side of the compressor and is bolted to the housing 30.
- a housing intermediate wall 32 is arranged, which limits a suction chamber 33.
- a passage opening is formed, through which a drive shaft 11 extends.
- the outside of the Housing 30 arranged shaft end is rotatably connected to a driver 35 which engages in the rotatably mounted on the housing 30 pulley, so that a torque can be transmitted to the drive shaft 11 of the pulley.
- the drive shaft 11 is rotatably mounted on the one hand in the housing bottom 34 and on the other hand in the housing intermediate wall 32.
- the sealing of the drive shaft 11 against the housing bottom 34 is effected by a first shaft seal 36 and against the housing intermediate wall 32 by a second shaft seal 37.
- the drive shaft 11 transmits the torque to a compressor unit, which is constructed as follows.
- the compressor unit comprises a movable displacement spiral 13 and a counter-spiral 14.
- the displacement spiral 13 and the counter-spiral 14 engage each other.
- the counter-spiral 14 is fixed in the circumferential direction and in the radial direction.
- the coupled with the drive shaft 11 movable displacement spiral 13 describes a circular path, so that in a conventional manner by this movement several gas pockets or gas chambers are generated, which migrate radially between the displacement spiral 13 and the counter-spiral 14.
- refrigerant vapor is sucked into the open outer gas chamber and compressed with the further spiral movement and the concomitant reduction of the gas chamber.
- the refrigerant vapor is increasingly compressed linearly from radially outward to radially inward direction and expelled in the center of the counter-spiral 14 into a pressure chamber 15.
- an eccentric bearing 12 is provided, which is connected to the drive shaft by an eccentric pin 38 (s. FIG. 2 ).
- the eccentric bearing 12 and the displacement spiral 13 are arranged eccentrically with respect to the counter-spiral 14.
- the gas chambers are separated from each other pressure-tight by conditioning the Verdrticianerspirale 13 on the counter-spiral 14.
- the radial contact pressure between the displacement spiral 13 and the counter-spiral 14 is adjusted by the eccentricity.
- the eccentricity results from the distance x between the center of the counter-spiral and the center of the displacement spiral (s. FIG. 6 ).
- the distance x may preferably be in a range from 0.1 mm to 1.5 mm, in particular from 0.1 mm to 1.0 mm, in particular from 0.1 mm to 0.8 mm, in particular from 0.1 mm to 0.6 mm, in particular from 0.1 mm to 0.4 mm, in particular from 0.1 mm to 0.2 mm.
- a rotational movement of the displacement spiral is avoided by a plurality of guide pins 39, which, as in FIG. 2 shown, are mounted in the intermediate wall 32.
- the guide pins 39 engage in corresponding guide bores 40 which are formed in the displacement spiral 13.
- a counterweight 28 is connected, preferably in one piece, to the eccentric bearing 12 to compensate for the imbalance caused by the orbital motion of the displacer coil 13.
- the eccentric bearing 12 is recessed in the positive displacement spiral 13 in the direction of the pressure chamber 15.
- the eccentric bearing 12 is thus at least partially equal to the turns of the counter-spiral 14.
- the eccentric bearing 12 is disposed in the displacement between the displacement spiral 13 and the counter-spiral 14.
- the eccentric bearing 12 has a pin 58 which is rotatably arranged in a bearing bush 26.
- the bearing bush 26 is designed in one piece or in one piece with the displacement spiral 13.
- the bushing 26 and the pin 58 may be made of the same material, for example. From bronze.
- the bearing bush 26 and thus also the pin 58 are arranged at the same height as the turns of the two spirals 13, 14 and thus dive into the counter-spiral 14.
- the outer wall of the bearing bush 26 forms part of the winding of the displacement spiral 13 and cooperates with the counter-spiral 14 for compressing the gas.
- the axial sealing takes place through the bottom 58 of the bearing bush 26, which is aligned with the end face of the turns.
- the end face and the bottom 58 are aligned parallel to the sealing surface 59 of the counter-spiral 14 and seal against them in the axial direction (s. Fig. 4 ).
- the structure of the eccentric bearing 12 is in cross section in FIG. 6 shown.
- the winding of the displacement spiral 13 widens towards the center.
- the widened inner part of the displacement spiral 13 receives the pin 58 and integrally forms the bearing bush 26 in which the pin 58 rotatably seated.
- the surface of the eccentric bearing 12 is smaller than the central surface 55 within the innermost turn of the counter-spiral 14.
- the surface of the eccentric bearing 12 corresponds to the surface of the bottom 54 of the bearing bush 26. This ensures that formed in the region of the central surface 55 gas ejection port (not shown) for the fluid connection with the pressure chamber 15 is accessible.
- lubricating lands 56 are formed complementary to the lubrication lands 56 at the outer edges of the turns.
- the complementary lubricating bevels 56 may have the same angle. It is also possible that the lubricating bevels 56 in the corners have a shallower angle than the lubricating bevels 56 at the outer edges.
- the corners may have radii 57 which are so large that they accommodate the associated lubricating bevels 56 at the outer edges (see FIG. Fig. 9 ).
- FIGS. 1 . 2 shown scroll compressor is clutchless.
- the scroll compressor is switched on and off (digital circuit).
- the counter-spiral 14 in the axial direction ie in a direction parallel to the drive shaft 11 is alternately movable.
- the displacement spiral 13 is fixed in the axial direction.
- the counter-spiral 14 can be lifted from the displacement spiral 13 in the axial direction, as in the FIGS. 1 to 3 shown.
- a pressure equalizing gap 41 is created between the displacement spiral 13 and the counter-spiral 14, which connects the gas chambers, which are separated from each other in the radial direction, between the displacement spiral 13 and the counter-spiral 14.
- the sliding surface 42 is machined and seals against the counter-spiral 14.
- the rear wall 21 of the counter-spiral 14 forms the bottom of the pressure chamber 15.
- the counter-spiral 14 therefore closes directly with the pressure chamber 15.
- the rear wall 21 also has a flange 22, in particular an annular flange 22, which rests against the sliding surface 42 of the pressure chamber 15.
- the flange 22 serves as an axial guide of the counter-spiral 14 in the pressure chamber 15.
- On the outer circumference of the flange 22, a groove with a sealing means, for example a sealing ring 43 is formed.
- the pressure chamber 15 is bounded by a peripheral wall 44 which forms a stop 45 and limits the axial movement of the counter-spiral 14.
- the pressure chamber 15 is provided in the housing cover 31. As a result, the assembly of the axially movable counter-spiral 14 is simplified. In addition, it has a rotationally symmetrical cross section.
- axial force For the alternating movement of the counter-spiral 14 between the open position ( FIG. 3 ) and the closed position ( FIG. 4 ) opposite axial forces are required.
- the spring 16 may be formed, for example, as a plate spring.
- the spring 16 is in the closed position according to FIG. 4 biased and urges the counter-spiral 14 and the displacement spiral 13 apart.
- the spring 16 is disposed opposite to the pressure chamber 15.
- a central recess 46 is provided in the counter-spiral 14, in which the spring 16 is arranged.
- the spring 16 is supported on the displacement spiral 13.
- the bearing bush 26 of the eccentric bearing 12 is recessed in the VerdrDeutscherspirale 13.
- the bearing bush 26 dips into the counter-spiral 14 and protrudes into the counter-spiral 14.
- the bottom of the bearing bush 26, on which the spring 16 is supported is at the same height as the inner edges of the turns of the displacer spiral 13. This is well in FIG. 3 to recognize (open position). In the closed position according to FIG. 4 Therefore, the bottom of the bearing bush 26 abuts against the counter-spiral 14 and seals the innermost gas chamber between the displacement spiral 13 and the counter-spiral 14.
- a piston 17, in particular an annular piston 17 is provided which is coaxial with the longitudinal axis of the counter-coil 14 slidably.
- annular piston 17 a plurality of arranged on the circumference of the counter-spiral 14 cylindrical piston can be provided.
- the annular piston 17 engages the rear wall 21 of the counter-spiral 14 and acts on it with a closing force which operates against the spring force of the spring 16.
- the piston 17 engages, as in the FIGS. 1 to 4 to recognize, in addition to the pressure chamber 15 to the counter-coil 14 at.
- the piston 17 is thus arranged outside the pressure chamber 15 or generally eccentrically.
- a simple outlet opening may be formed in the counter-spiral 14 (not shown).
- the annular piston 17 has a pressure ring 47, which is connected to a bottom 48 of the piston.
- the piston head 48 is axially displaceable and pressure-tight in an axial guide 18.
- the axial guide 18 is formed as an annular chamber.
- the annular chamber with a Supply terminal 20c connected.
- the supply port 20c is connected to a 2/3-way valve, which in turn is connected to a high pressure port 20a and a suction pressure port 20b, so that the annular chamber can be acted upon alternately with high pressure or suction pressure.
- the counter-spiral 14 can be alternately moved back and forth between the open position or the closed position.
- the annular piston 17 operates substantially only against the spring force of the spring 16, because the pressure prevailing in the pressure chamber 15 and acting on the counter-spiral 14 pressure is at least partially compensated by the pressure acting between the counter-spiral 14 and the displacement spiral 13 during compression.
- only relatively small strokes are required to adjust the pressure equalizing gap 41. For example, stroke ranges of about 0.3 to 0.7 mm, in particular a stroke of about 0.5 mm.
- the power control takes place in the scroll compressor by switching on or off the compressor power, specifically by changing the frequency of the cyclic or alternating movement of the counter-spiral 14th
- the compressed gas collected in the pressure chamber 15 flows through an outlet 49 from the pressure chamber 15 into an oil separator 29, which in the present case is designed as a cyclone separator.
- the compressed gas flows through the oil separator 29 and a check valve 19 in the circuit of the air conditioner.
- the check valve 19, which prevents the compressed gas from flowing back into the scroll compressor which is switched off, is designed, for example, for pressure differences of 0.5 to 1 bar.
- a receiving space 24 also referred to as a backpressure space ( FIG. 1 ), in which a part of the counterweight 28 and the eccentric bearing 12 are arranged, fluidly connected to the high pressure side.
- the receiving space 24 is bounded by the rear wall 25 of the compressor spiral 13 and the housing intermediate wall 32.
- the receiving space 24 is fluid-tightly separated from the suction space 33 by the second shaft seal 37 described above.
- a sealing and sliding ring 52 is disposed between the displacement spiral 13 and the housing intermediate wall 32 and seals the receiving space 24 against the high pressure side.
- the sealing and sliding ring 52 is seated in an annular groove in the housing intermediate wall 32. Between the housing intermediate wall 32 and the displacement spiral 13, a gap is formed (not shown).
- the displacement spiral 13 is therefore not supported in the axial direction directly on the housing intermediate wall 32 but on the sealing and sliding ring 52 and slides on this.
- the sealing and sliding ring 52 protrudes from the annular groove and seals the gap.
- the gap can be about 0.2 mm to 0.5 mm wide.
- a line 50 connects the oil separator 29 with the receiving space 24. This extends through the housing cover 31, the counter-spiral 14 and the intermediate wall 32. Between the oil separator 29 and the receiving space 24, specifically between the counter-spiral 14 and the Housing cover 31, a pressure reducer 53 is arranged, which ensures that between the high pressure side and the receiving space 24, a pressure difference of about 10% -20% prevails. This ensures that in the closed position of the axial contact pressure between the displacement spiral 13 and the counter-spiral 14 and thus the axial tightness is increased.
- the pressure chamber 15 is encapsulated (s. FIG. 4 ).
- the pressure chamber 15 is free of installation.
- the pressure chamber may have an inner shell 51, in particular made of stainless steel or stainless steel.
- the inner shell 51 has a lower thermal conductivity than aluminum.
- the thermal insulation of the oil separator 29 reduces the heating of the refrigerant vapor on the suction side.
- the thermal insulation is carried out by an encapsulation, for example by an inner shell of stainless steel or stainless steel, which surrounds the cyclone.
- the pressure reducer 53 is isolated by encapsulation with an inner shell of stainless steel or stainless steel.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
Die Erfindung betrifft einen Scrollkompressor für eine CO2-Fahrzeugklimaanlage, sowie eine CO2-Fahrzeugklimaanlage mit einem solchen Scrollkompressor.The invention relates to a scroll compressor for a CO 2 vehicle air conditioning system, and a CO 2 vehicle air conditioning system with such a scroll compressor.
Zur Klimatisierung von Kraftfahrzeugen kommen nichtbrennbare Kältemittel zum Einsatz, um bei einem Unfall die Explosionsgefahr im Fahrzeuginnenraum zu vermeiden. Die bisher verwendeten Kältemittel sind allerdings wegen ihres hohen Treibhauspotentials entweder bereits verboten oder werden zumindest als problematisch eingestuft. Als umweltverträgliches, nichtbrennbares Kältemittel kommt CO2 (R744) in Frage, das die bisherigen Kältemittel bereits teilweise ersetzt. CO2-Klimaanlagen arbeiten allerdings mit hohen Betriebsdrücken, die besondere Anforderungen an die Festigkeit und Dichtigkeit der Anlagekomponenten stellen. Der mit dem hohen Betriebsdruck verbundene Vorteil besteht darin, dass durch die höhere Dichte von CO2 ein geringerer Volumenstrom notwendig ist, um eine relativ hohe Kälteleistung zu erbringen.Non-combustible refrigerants are used for the air conditioning of motor vehicles in order to avoid the risk of explosion inside the vehicle in the event of an accident. However, the refrigerants used so far are either already banned or at least classified as problematic because of their high global warming potential. As an environmentally friendly, non-combustible refrigerant CO 2 (R744) comes into question, which already partially replaces the existing refrigerant. However, CO 2 air conditioners operate with high operating pressures, which make special demands on the strength and tightness of the system components. The advantage associated with the high operating pressure is that the higher density of CO 2 requires a smaller volume flow to provide a relatively high refrigeration capacity.
Ein Scrollkompressor für eine CO2-Fahrzeugklimaanlage ist aus
So offenbart
Bei den bekannten Scrollkompressoren ist die Dichtigkeit zwischen Verdränger- und Gegenspirale problematisch, was sich auf die Leistung auswirkt.In the known scroll compressors, the tightness between positive and negative spiral is problematic, which has an effect on performance.
Der Erfindung liegt die Aufgabe zugrunde, einen Scrollkompressor für eine CO2-Fahrzeugklimaanlage anzugeben, der einfach aufgebaut ist und mit Blick auf die Dichtigkeit verbessert ist. Der Erfindung liegt ferner die Aufgabe zugrunde, eine CO2-Fahrzeugklimaanlage mit einem solchen Scrollkompressor anzugeben.The invention has for its object to provide a scroll compressor for a CO 2 vehicle air conditioner, which is simple and improved in view of the tightness. The invention is also based on the object of specifying a CO 2 vehicle air conditioning system with such a scroll compressor.
Erfindungsgemäß wird die Aufgabe durch einen Scrollkompressor für eine CO2-Fahrzeugklimaanlage mit den Merkmalen des Anspruchs 1 gelöst. Hinsichtlich der CO2-Fahrzeugklimaanlage wird die Aufgabe durch den Gegenstand des Anspruchs 11 gelöst. Die Erfindung ist für drehzahlgeregelte oder digital geregelte Scrollkompressoren geeignet.According to the invention the object is achieved by a scroll compressor for a CO 2 vehicle air conditioner with the features of claim 1. With regard to the CO 2 vehicle air conditioning system, the object is achieved by the subject matter of
Die Erfindung hat den Vorteil, dass Kippmomente, die auf die Verdrängerspirale wirken, reduziert werden und dadurch ein gleichmäßiger Anpressdruck der Verdrängerspirale erreicht wird. Der gleichmäßige Anpressdruck führt dazu, dass an jeder Berührungsstelle zwischen den beiden Spiralen im Wesentlichen die gleiche Dichtigkeit herrscht.The invention has the advantage that tilting moments which act on the displacement spiral are reduced, thereby achieving a uniform contact pressure of the displacement spiral. The uniform pressure leads to the fact that at each contact point between the two spirals substantially the same tightness prevails.
Dazu ist erfindungsgemäß vorgesehen, dass das Exzenterlager im Verdrängerraum zwischen der Verdrängerspirale und der Gegenspirale angeordnet ist und eine Lagerbuchse aufweist, die einstückig mit der Verdrängerspirale ausgebildet ist und deren Boden mit der Stirnseite der Windungen der Verdrängerspirale fluchtet.For this purpose, the invention provides that the eccentric bearing is arranged in the displacement between the positive displacement spiral and the counter-spiral and has a bearing bush, which is integrally formed with the positive displacement spiral and whose bottom is aligned with the end face of the turns of the positive displacement spiral.
Das Exzenterlager ist in der Verdrängerspirale in Richtung der Druckkammer vertieft angeordnet, wobei sich das Exzenterlager zumindest teilweise auf Höhe der Windungen der Gegenspirale befindet. Das Exzenterlager taucht also zumindest teilweise in die Gegenspirale ein. Das bei den bekannten Niederdruck-Scrollkompressoren zur Endverdichtung genutzte innerste Volumen zwischen der Verdrängerspirale und der Gegenspirale wird zumindest teilweise zur Aufnahme des Exzenterlagers genutzt. Dadurch werden Hebellängen und Kippmomente effektiv verringert, weil die Eintauchtiefe des Exzenterlagers besonders groß ist.The eccentric bearing is recessed in the Verdrängerspirale in the direction of the pressure chamber, wherein the eccentric bearing is at least partially equal to the turns of the counter-spiral. The eccentric bearing so at least partially immersed in the counter-spiral. That in the known low-pressure scroll compressors used for final compression innermost volume between the displacement spiral and the counter-spiral is at least partially used to accommodate the eccentric bearing. As a result, lever lengths and tilting moments are effectively reduced, because the immersion depth of the eccentric bearing is particularly large.
Die Erfindung hat außerdem den Vorteil dass die Saugseite sicher von der Hochdruckseite getrennt ist, weil die Lagerbuchse einstückig mit der Verdrängerspirale ausgebildet ist. Damit sind keine Dichtungen zwischen dem Exzenterlager und der Verdrängerspirale erforderlich. Die Lagerbuchse nimmt an der Verdichtung teil, weil sich diese einerseits im Verdrängerraum befindet und andererseits deren Boden mit der Stirnseite der Windungen der Verdrängerspirale fluchtet. Dadurch wirkt die Lagerbuchse in Umfangsrichtung mit den Windungen der Gegenspirale und in axialer Richtung mit einer Dichtfläche der Gegenspirale zusammen.The invention also has the advantage that the suction side is securely separated from the high pressure side, because the bearing bush is formed integrally with the positive displacement spiral. Thus, no seals between the eccentric and the positive spiral are required. The bushing participates in the compression, because this one hand is in the displacement and on the other hand, the bottom of which is aligned with the end face of the turns of the positive displacement spiral. As a result, the bearing bush in the circumferential direction cooperates with the turns of the counter-spiral and in the axial direction with a sealing surface of the counter-spiral.
Bevorzugte Ausführungen sind in den Unteransprüchen angegeben.Preferred embodiments are specified in the subclaims.
Etwaige Kippmomente werden weiter verringert, wenn die Verdrängerspirale eine mittige Ausnehmung aufweist, in der zumindest teilweise ein Gegengewicht aufgenommen ist, das mit dem Exzenterlager verbunden ist.Any tilting moments are further reduced if the displacement spiral has a central recess in which at least partially a counterweight is accommodated, which is connected to the eccentric bearing.
Vorzugsweise ist die Fläche des Exzenterlagers kleiner als die mittige Fläche innerhalb der innersten Windung der Gegenspirale und zwar derart, dass wenigstens eine im Bereich der mittigen Fläche ausgebildete Gasausstoßöffnung für die Fluidverbindung mit der Druckkammer zugänglich ist. Dadurch wird vermieden, dass die Gasausstoßöffnung von dem vertieft angeordneten Exzenterlager überdeckt wird.Preferably, the surface of the eccentric bearing is smaller than the central area within the innermost turn of the counter-spiral such that at least one gas ejection opening formed in the region of the central area is accessible for fluid communication with the pressure chamber. This avoids that the gas ejection opening is covered by the recessed eccentric bearing.
Eine weitere Verbesserung der Dichtigkeit wird erreicht, wenn die Windungen der Verdrängerspirale und der Gegenspirale jeweils Schmierfasen aufweisen. In den Schmierfasen kann sich Schmiermittel sammeln, das die Gleiteigenschaften verbessert und lokale Widerstandskräfte verringert, so dass ein gleichmäßiger Anpressdruck und damit eine gute Dichtigkeit zwischen den beiden Spiralen herrscht. Wenn die Schmierfasen an beiden Außenkanten jeweils der Windungen der Verdrängerspirale und der Gegenspirale ausgebildet sind, erfolgt eine gute Schmierung in beiden Richtungen bei der reziproken Bewegung der Verdrängerspirale.A further improvement of the tightness is achieved when the turns of the positive displacement spiral and the counter-spiral each have lubricating bevels. Lubricants can accumulate in the lubricating surfaces, which improves the sliding properties and reduces local resistance forces, so that there is a uniform contact pressure and thus a good seal between the two spirals. If the lubricating bevels are formed at both outer edges of each of the turns of the positive displacement spiral and the counter-spiral, good lubrication in both directions takes place in the reciprocal movement of the positive displacement spiral.
Vorzugsweise sind die Schmierfasen und/oder ein Radius in den Ecken zwischen den Windungen und einer Dichtfläche der Verdrängerspirale ausgebildet. Zusätzlich können die Schmierfasen und/oder ein Radius in den Ecken zwischen den Windungen und einer Dichtfläche der Gegenspirale ausgebildet sein. Die Schmierfasen oder Radien in den Ecken wirken vorzugsweise mit den Schmierfasen an beiden Außenkanten jeweils der Windungen der Verdrängerspirale und der Gegenspirale zusammen. Dadurch wird die Dichtwirkung im Bereich der jeweiligen Gaskammer bzw. Gastasche verbessert, die durch die radiale Anlage zwischen der Verdrängerspirale und der Gegenspirale gebildet wird.Preferably, the lubricating chamfers and / or a radius are formed in the corners between the turns and a sealing surface of the displacement spiral. In addition, the lubricating chamfers and / or a radius may be formed in the corners between the turns and a sealing surface of the counter-spiral. The gullies or radii in the corners preferably cooperate with the gullies on both outer edges of each of the turns of the positive displacement spiral and the counter-spiral. As a result, the sealing effect in the region of the respective gas chamber or gas pocket is improved, which is formed by the radial contact between the displacement spiral and the counter-spiral.
Die Dichtigkeit kann dadurch verbessert werden, wenn ein zur Saugseite abgeschlossener Aufnahmeraum für das Exzenterlager mit der Druckkammer fluidverbunden und eine Rückwand der Verdrängerspirale mit einem Anpressdruck beaufschlagbar ist.The tightness can be improved if a closed to the suction side receiving space for the eccentric bearing fluidly connected to the pressure chamber and a rear wall of the positive displacement spiral can be acted upon by a contact pressure.
Es hat sich gezeigt, dass eine relativ geringe Exzentrizität für eine ausreichende Verdichtung des Kältemittels genügt. Dazu kann der Abstand zwischen dem Mittelpunkt der Gegenspirale und dem Mittelpunkt der Verdrängerspirale maximal 1,5 mm, insbesondere maximal 1,2 mm, insbesondere maximal 1,0 mm, insbesondere maximal 0,8 mm, insbesondere maximal 0,6 mm, insbesondere maximal 0,4 mm, insbesondere maximal 0,2 mm betragen. Die Untergrenze kann 0,1 mm betragen. Vorzugsweise weist die Gegenspirale einen Windungswinkel von 660° bis 720°, insbesondere von 680° bis 700° auf, wodurch eine ausreichende Verdichtung des Kältemittels erzielt wird. Vorzugsweise ist das Volumen der Druckkammer um den Faktor 5-7, insbesondere um den Faktor 6, größer als das Saugvolumen pro Umdrehung der Verdrängerspirale, wodurch Gaspulsationen wirksam verringert werden.It has been found that a relatively low eccentricity is sufficient for a sufficient compression of the refrigerant. For this purpose, the distance between the center of the counter-spiral and the center of the displacement spiral maximally 1.5 mm, in particular at most 1.2 mm, in particular at most 1.0 mm, in particular maximally 0.8 mm, in particular maximally 0.6 mm, in particular maximally 0.4 mm, in particular not more than 0.2 mm. The lower limit can be 0.1 mm. Preferably, the counter-spiral has a winding angle of 660 ° to 720 °, in particular from 680 ° to 700 °, whereby a sufficient compression of the refrigerant is achieved. Preferably, the volume of the pressure chamber by a factor of 5-7, in particular by a factor of 6, greater than the suction volume per revolution of the displacement spiral, whereby gas pulsations are effectively reduced.
Die Erfindung wird mit weiteren Einzelheiten unter Bezug auf die beigefügten schematischen Zeichnungen anhand von Ausführungsbeispielen näher erläutert.The invention will be explained in more detail with reference to the accompanying schematic drawings with reference to embodiments.
In diesen zeigen
- Figur 1
- einen Längsschnitt eines Scrollkompressors nach einem erfindungsgemäßen Ausführungsbeispiel;
- Figur 2
- einen weiteren Längsschnitt des Scrollkompressors gemäß
Figur 1 , der den Aufbau des Exzenterlagers verdeutlicht; Figur 3- eine Detailansicht des Scrollkompressors gemäß
Figur 1 im Bereich des Gehäusedeckels; - Figur 4
- eine Detailansicht wie in
, wobei sich der Kompressor in der Schließstellung befindet;Figur 3 - Figur 5
- einen Längsschnitt eines Kompressors nach einem weiteren erfindungsgemäßen Ausführungsbeispiel mit einem elektrischen Antrieb mit konstanter bzw. fester Drehzahl;
Figur 6- einen Querschnitt eines Kompressors nach
Figur 1 ; - Figur 7
- eine Detailansicht der Schmierfasen;
- Figur 8
- eine Detailansicht der Schmierfasen gemäß
Figur 7 , an einer anderen Windungsstelle ; und - Figur 9
- eine Detailansicht der Ecken, die mit Radien ausgebildet sind;
- FIG. 1
- a longitudinal section of a scroll compressor according to an embodiment of the invention;
- FIG. 2
- a further longitudinal section of the scroll compressor according to
FIG. 1 , which illustrates the structure of the eccentric camp; - FIG. 3
- a detailed view of the scroll compressor according to
FIG. 1 in the area of the housing cover; - FIG. 4
- a detail view like in
FIG. 3 with the compressor in the closed position; - FIG. 5
- a longitudinal section of a compressor according to another embodiment of the invention with an electric drive with a constant or fixed speed;
- FIG. 6
- a cross section of a compressor after
FIG. 1 ; - FIG. 7
- a detailed view of the lubricating chamfers;
- FIG. 8
- a detailed view of the lubricating chamfer according
FIG. 7 at another winding location; and - FIG. 9
- a detailed view of the corners, which are formed with radii;
Der nachfolgend im Detail beschriebene Scrollkompressor ist für den Einsatz in einer CO2-Fahrzeugklimaanlage konzipiert, die typischerweise einen Gaskühler, einen inneren Wärmetauscher, eine Drossel, einen Verdampfer und einen Verdichter umfasst. Solche Anlage sind für Maximaldrücke über 100 bar ausgelegt. Der Verdichter ist ein Scrollkompressor, der auch als Spiralverdichter bezeichnet wird. Wie in den
Der Scrollkompressor umfasst ferner ein Gehäuse 30 mit einem Gehäusedeckel 31, der die Hochdruckseite des Kompressors verschließt und mit dem Gehäuse 30 verschraubt ist. Im Gehäuse 30 ist eine Gehäusezwischenwand 32 angeordnet, die einen Saugraum 33 begrenzt. Im Gehäuseboden 34 ist eine Durchtrittsöffnung ausgebildet, durch die sich eine Antriebswelle 11 erstreckt. Das außerhalb des Gehäuses 30 angeordnete Wellenende ist drehfest mit einem Mitnehmer 35 verbunden, der in die am Gehäuse 30 drehbar gelagerte Riemenscheibe eingreift, so dass von der Riemenscheibe ein Drehmoment auf die Antriebswelle 11 übertragen werden kann. Die Antriebswelle 11 ist einerseits im Gehäuseboden 34 und andererseits in der Gehäusezwischenwand 32 drehbar gelagert. Die Abdichtung der Antriebswelle 11 gegen den Gehäuseboden 34 erfolgt durch eine erste Wellendichtung 36 und gegen die Gehäusezwischenwand 32 durch eine zweite Wellendichtung 37.The scroll compressor further includes a
Die Antriebswelle 11 überträgt das Drehmoment auf eine Verdichtereinheit, die wie folgt aufgebaut ist.The
Die Verdichtereinheit umfasst eine bewegliche Verdrängerspirale 13 und eine Gegenspirale 14. Die Verdrängerspirale 13 und die Gegenspirale 14 greifen ineinander ein. Die Gegenspirale 14 steht in Umfangsrichtung und in radialer Richtung fest. Die mit der Antriebswelle 11 gekoppelte bewegliche Verdrängerspirale 13 beschreibt eine kreisförmige Bahn, so dass in an sich bekannter Weise durch diese Bewegung mehrere Gastaschen oder Gaskammern erzeugt werden, die zwischen der Verdrängerspirale 13 und der Gegenspirale 14 radial nach innen wandern. Durch diese orbitierende Bewegung wird in die geöffnete äußere Gaskammer Kältemitteldampf angesaugt und mit der weiteren Spiralbewegung und der damit einhergehenden Verkleinerung der Gaskammer verdichtet. Der Kältemitteldampf wird von radial außen nach radial innen linear zunehmend verdichtet und im Zentrum der Gegenspirale 14 in eine Druckkammer 15 ausgestoßen.
Für die orbitierende Bewegung der Verdrängerspirale 13 ist ein Exzenterlager 12 vorgesehen, das mit der Antriebswelle durch einen Exzenterstift 38 verbunden ist (s.
For the orbiting movement of the
Die Exzentrizität ergibt sich aus dem Abstand x zwischen dem Mittelpunkt der Gegenspirale und dem Mittelpunkt der Verdrängerspirale (s.
Eine Rotationsbewegung der Verdrängerspirale wird durch mehrere Führungsstifte 39 vermieden, die, wie in
Wie in den
Das Exzenterlager 12 weist einen Zapfen 58 auf, der in einer Lagerbuchse 26 drehbar angeordnet ist. Die Lagerbuchse 26 ist einteilig bzw. einstückig mit der Verdrängerspirale 13 ausgeführt. Die Lagerbuchse 26 und der Zapfen 58 können aus dem selben Material bestehen, bspw. aus Bronze.The
Die Lagerbuchse 26 und damit auch der Zapfen 58 sind auf derselben Höhe wie die Windungen der beiden Spiralen 13, 14 angeordnet und tauchen damit in die Gegenspirale 14 ein. Damit bildet die Außenwand der Lagerbuchse 26 Teil der Windung der Verdrängerspirale 13 und wirkt mit der Gegenspirale 14 zum Verdichten des Gases zusammen. Die axiale Abdichtung erfolgt durch den Boden 58 der Lagerbuchse 26, der mit der Stirnfläche der Windungen fluchtet. Die Stirnfläche und der Boden 58 sind parallel zur Dichtfläche 59 der Gegenspirale 14 ausgerichtet und dichten gegen diese in axialer Richtung ab (s.
Der Aufbau des Exzenterlagers 12 ist im Querschnitt in
Die Fläche des Exzenterlagers 12 ist kleiner als die mittige Fläche 55 innerhalb der innersten Windung der Gegenspirale 14. Die Fläche des Exzenterlagers 12 entpricht der Fläche des Bodens 54 der Lagerbuchse 26. Dadurch wird erreicht, dass eine im Bereich der mittigen Fläche 55 ausgebildete Gasausstoßöffnung (nicht dargestellt) für die Fluidverbindung mit der Druckkammer 15 zugänglich ist.The surface of the
In den
Gegenüber den Außenkanten, d.h. am Fuß der jeweiligen Windung, sind Ecken zwischen der Dichtfläche 59 und der jeweiligen Windung ausgebildet. Diese weisen Schmierfasen 56 sind komplementär zu den Schmierfasen 56 an den Außenkanten der Windungen ausgebildet. Dabei können die komplementären Schmierfasen 56 den selben Winkel aufweisen. Es ist auch möglich, dass die Schmierfasen 56 in den Ecken einen flacheren Winkel als die Schmierfasen 56 an den Außenkanten aufweisen.Opposite the outer edges, i. at the foot of the respective turn, corners are formed between the sealing surface 59 and the respective turn. These lubricating lands 56 are formed complementary to the lubrication lands 56 at the outer edges of the turns. In this case, the complementary lubricating bevels 56 may have the same angle. It is also possible that the lubricating bevels 56 in the corners have a shallower angle than the lubricating bevels 56 at the outer edges.
Anstelle der Schmierfasen 56 können die Ecken Radien 57 aufweisen, die so groß ausgebidlet sind, dass diese die zughörigen Schmierfasen 56 an den Außenkanten aufnehmen (s.
Der in
Die für die axiale Beweglichkeit der Gegenspirale 14 erforderliche Axialführung wird durch die Druckkammer 15 erfüllt, die außerdem Gaspulsationen dämpft. Die Druckkammer 15 hat daher eine Doppelfunktion:
- Sie ist der Gegenspirale in Strömungsrichtung nachgeordnet und steht mit dieser in Fluidverbindung durch den nicht dargestellten Auslass der
Gegenspirale 14. Der Auslass ist nicht exakt im Mittelpunkt der Gegenspirale 14 angeordnet, sondern befindet sich außermittig im Bereich der innersten Kammer zwischen der Verdrängerspirale 13 und derGegenspirale 14. Dadurch wird erreicht, dass der Auslass von der Lagerbuchse 26 desExzenterlagers 12 nicht abgedeckt wird und der endverdichtete Dampf indie Druckkammer 15 ausgestoßen werden kann.
- It is arranged downstream of the counter-spiral in the flow direction and is in fluid communication with the outlet of the counter-spiral 14 (not shown). The outlet is not arranged exactly in the center of the counter-spiral 14, but is located off-center in the region of the innermost chamber between the
displacement spiral 13 and the counter-spiral 14. This ensures that the outlet is not covered by the bearingbush 26 of theeccentric bearing 12 and the final compressed steam can be ejected into thepressure chamber 15.
Für die Axialführung der Gegenspirale 14 bildet die Druckkammer 15 am axialen Ende, das der Gegenspirale 14 zugewandt ist, eine innere Gleitfläche 42. Die Gleitfläche 42 ist bearbeitet und dichtet gegen die Gegenspirale 14 ab. Die Rückwand 21 der Gegenspirale 14 bildet den Boden der Druckkammer 15. Die Gegenspirale 14 schließt also direkt mit der Druckkammer 15 ab. Die Rückwand 21 weist ferner einen Flansch 22, insbesondere einen Ringflansch 22 auf, der an der Gleitfläche 42 der Druckkammer 15 anliegt. Der Flansch 22 dient als Axialführung der Gegenspirale 14 in der Druckkammer 15. Auf dem Außenumfang des Flansches 22 ist eine Nut mit einem Dichtmittel, beispielsweise einem Dichtring 43 ausgebildet. Die Druckkammer 15 wird durch eine Umfangswandung 44 begrenzt, die einen Anschlag 45 bildet und die axiale Bewegung der Gegenspirale 14 begrenzt.For the axial guidance of the counter-spiral 14, the
Die Druckkammer 15 ist im Gehäusedeckel 31 vorgesehen. Dadurch wird die Montage der axialbeweglichen Gegenspirale 14 vereinfacht. Außerdem weist sie einen rotationssymmetrischen Querschnitt auf.The
Für die alternierende Bewegung der Gegenspirale 14 zwischen der Offenstellung (
Wie in
Um die Gegenspirale 14 aus der in
Der Kolben 17 greift, wie in den
Der Ringkolben 17 weist einen Anpressring 47 auf, der mit einem Boden 48 des Kolbens verbunden ist. Der Kolbenboden 48 ist in einer Axialführung 18 axial verschieblich und druckdicht gelagert. Die Axialführung 18 ist als Ringkammer ausgebildet. Für die Betätigung des Ringkolbens 17 ist die Ringkammer mit einem Versorgungsanschluss 20c verbunden. Wie in
Die Leistungsregelung erfolgt bei dem Scrollkompressor durch Ein- bzw. Ausschaltung der Verdichterleistung, konkret durch die Änderung der Frequenz der zyklischen bzw. alternierenden Bewegung der Gegenspirale 14.The power control takes place in the scroll compressor by switching on or off the compressor power, specifically by changing the frequency of the cyclic or alternating movement of the counter-spiral 14th
Das in der Druckkammer 15 gesammelte verdichtete Gas strömt durch einen Auslass 49 aus der Druckkammer 15 in einen Ölabscheider 29, der vorliegend als Zyklonabscheider ausgebildet ist. Das verdichtete Gas strömt durch den Ölabscheider 29 und ein Rückschlagventil 19 in den Kreislauf der Klimaanlage. Das Rückschlagventil 19, das ein Zurückströmen des verdichteten Gases in den ausgeschalteten Scrollkompressor verhindert, ist beispielsweise auf Druckdifferenzen von 0,5 bis 1 bar ausgelegt.The compressed gas collected in the
Die Abdichtung der Verdrängerspirale 13 gegen die Gegenspirale 14 in axialer Richtung wird dadurch unterstützt, dass eine Rückwand 25 der Verdrängerspirale mit Hochdruck beaufschlagt wird. Dazu ist ein Aufnahmeraum 24, auch als Backpressure-Raum bezeichnet (
Der Aufnahmeraum 24 ist durch die eingangs beschriebene zweite Wellendichtung 37 vom Saugraum 33 fluiddicht getrennt. Ein Dicht- und Gleitring 52 ist zwischen der Verdrängerspirale 13 und der Gehäusezwischenwand 32 angeordnet und dichtet den Aufnahmeraum 24 gegen die Hochdruckseite ab. Der Dicht- und Gleitring 52 sitzt in einer Ringnut in der Gehäusezwischenwand 32. Zwischen der Gehäusezwischenwand 32 und der Verdrängerspirale 13 ist ein Spalt ausgebildet (nicht dargestellt). Die Verdrängerspirale 13 stützt sich deshalb in axialer Richtung nicht direkt auf der Gehäusezwischenwand 32 sondern auf dem Dicht- und Gleitring 52 ab und gleitet auf diesem. Der Dicht- und Gleitring 52 steht dazu aus der Ringnut vor und dichtet den Spalt ab. Der Spalt kann ca. 0,2 mm bis 0,5 mm breit sein.The receiving
Für den Anschluss an die Hochdruckseite verbindet eine Leitung 50 den Ölabscheider 29 mit dem Aufnahmeraum 24. Diese erstreckt sich durch den Gehäusedeckel 31, die Gegenspirale 14 und die Zwischenwand 32. Zwischen dem Ölabscheider 29 und dem Aufnahmeraum 24, konkret zwischen der Gegenspirale 14 und dem Gehäusedeckel 31, ist ein Druckminderer 53 angeordnet, der dafür sorgt, dass zwischen der Hochdruckseite und dem Aufnahmeraum 24 eine Druckdifferenz von ca. 10%-20% herrscht. Dadurch wird erreicht, dass in der Schließstellung der axiale Anpressdruck zwischen der Verdrängerspirale 13 und der Gegenspirale 14 und damit die axiale Dichtigkeit erhöht wird.For connection to the high pressure side, a
In thermischer Hinsicht ist der in
Damit ist es möglich, den Gehäusedeckel 31 beispielsweise aus Aluminium zu fertigen, ohne dass eine übermäßige Wärmeübertragung von der Hochdruckseite auf die Saugseite zu befürchten ist.This makes it possible to manufacture the
Der einzige Unterschied zwischen dem Scrollkompressor gemäß
- 1010
- Antriebdrive
- 1111
- Antriebswelledrive shaft
- 1212
- Exzenterlageeccentric position
- 1313
- VerdrängerspiraleVerdrängerspirale
- 1414
- Gegenspiraleagainst spiral
- 1515
- Druckkammerpressure chamber
- 1616
- Federfeather
- 1717
- Kolben / RingkolbenPiston / ring piston
- 1818
- Kolbenführungpiston guide
- 1919
- Rückschlagventilcheck valve
- 20a20a
- HochdruckanschlussHigh pressure port
- 20b20b
- SaugdruckanschlussSaugdruckanschluss
- 20c20c
- Versorgungsanschlusssupply terminal
- 2121
- Rückwand GegenspiraleRear wall counter-spiral
- 2222
- Flanschflange
- 2323
- Innenwandinner wall
- 2424
- Aufnahmeraumaccommodation space
- 2525
- Rückwand VerdrängerspiraleRear wall displacement spiral
- 2626
- Lagerbuchsebearing bush
- 2727
- Ausnehmungrecess
- 2828
- Gegengewichtcounterweight
- 2929
- Ölabscheideroil separator
- 3030
- GewichtWeight
- 3131
- Gehäusedeckelhousing cover
- 3232
- GehäusezwischenwandHousing partition
- 3333
- Saugraumsuction
- 3434
- Gehäusebodencaseback
- 3535
- Mitnehmertakeaway
- 3636
- erste Wellendichtungfirst shaft seal
- 3737
- zweite Wellendichtungsecond shaft seal
- 3838
- Exzenterstifteccentric
- 3939
- Führungsstifteguide pins
- 4040
- Führungsbohrungenguide bores
- 4141
- DruckausgleichsspaltPressure compensation gap
- 4242
- Gleitflächesliding surface
- 4343
- Dichtringseal
- 4444
- Wandungwall
- 4545
- Anschlagattack
- 4646
- zentrale Ausnehmungcentral recess
- 4747
- Anpressringcompression ring
- 4848
- Kolbenbodenpiston crown
- 4949
- Auslassoutlet
- 5050
- Leitungmanagement
- 5151
- Innenhülleinterior Skin
- 5252
- Gleit- und DichtringSliding and sealing ring
- 5353
- Druckmindererpressure reducer
Claims (11)
- A scroll compressor for a CO2 vehicle air conditioning system, having a movable displacement spiral (13), which is rotatably connected to an eccentric bearing (12) and which engages into a counterpart spiral (14) such that, between the windings of the displacement spiral (13) and of the counterpart spiral (14), there are formed chambers which travel radially inward in order to compress the refrigerant and discharge it into a pressure chamber (15),
wherein the displacement spiral (13) is arranged on the suction side and the counterpart spiral (14) is arranged on the high-pressure side,
wherein the eccentric bearing (12) is arranged in the displacement chamber between the displacement spiral (13) and the counterpart spiral (14) and has a bearing bushing (26) which is formed in one piece with the displacement spiral (13),
characterized in that
its base (54) is aligned with the face side of the windings of the displacement spiral (13). - The scroll compressor according to claim 1,
characterized in that
the displacement spiral (13) has a central recess (27) in which there is at least partially received a counterweight (28) which is connected to the eccentric bearing (12). - The scroll compressor according to one of the preceding claims,
characterized in that
the surface of the eccentric bearing (12) is smaller than the central surface (55) within the innermost winding of the counterpart spiral (14), such that at least one gas discharge opening formed in the region of the central surface (55) is accessible for the fluid connection to the pressure chamber (15). - The scroll compressor according to one of the preceding claims,
characterized in that
the windings of the displacement spiral (13) and of the counterpart spiral (14) respectively have lubrication chamfers (56) which are formed on both outer edges respectively of the windings of the displacement spiral (13) and of the counterpart spiral (14). - The scroll compressor according to one of the preceding claims,
characterized in that
further lubrication chamfers (56) and/or a radius (57) are formed in the corners between the windings and a sealing surface (59) of the displacement spiral (13). - The scroll compressor according to one of the preceding claims,
characterized in that
further lubrication chamfers (56) and/or a radius (57) are formed in the corners between the windings and a sealing surface (59) of the counterpart spiral (14). - The scroll compressor according to one of the preceding claims,
characterized in that
a receiving space (24), which is closed off with respect to the suction side, for the eccentric bearing (12) is fluidically connected to the pressure chamber (15), and a rear wall (25) of the displacement spiral (13) can be acted upon with a surface pressure. - The scroll compressor according to one of the preceding claims,
characterized in that
the distance between the central point of the counterpart spiral (14) and the central point of the displacement spiral (13) is at most 1.5 mm, in particular at most 1.2 mm, in particular at most 1.0 mm, in particular at most 0.8 mm, in particular at most 0.6 mm, in particular at most 0.4 mm, in particular at most 0.2 mm. - The scroll compressor according to one of the preceding claims,
characterized in that
the counterpart spiral (14) has a winding angle of 660° to 720°, in particular of 680° to 700°. - The scroll compressor according to one of the preceding claims,
characterized in that
the volume of the pressure chamber (15) is greater by a factor of 5-7, in particular by a factor of 6, than the suction volume per revolution of the displacement spiral (13) and/or the pressure chamber (15) is thermally insulated. - A vehicle air conditioning system that contains CO2 as refrigerant, having a scroll compressor according to claim 1.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13168729.5A EP2806164B1 (en) | 2013-05-22 | 2013-05-22 | Scroll compressor and CO2 vehicle air conditioner with a scroll compressor |
US14/282,509 US9512840B2 (en) | 2013-05-22 | 2014-05-20 | Scroll-type compressor and CO2 vehicle air conditioning system having a scroll-type compressor |
CN201410216902.9A CN104179682B (en) | 2013-05-22 | 2014-05-21 | Scroll compressor and the CO with scroll compressor2Vehicle air conditioner |
JP2014104948A JP6425417B2 (en) | 2013-05-22 | 2014-05-21 | CO2 vehicle air conditioning system having a scroll compressor and a scroll compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13168729.5A EP2806164B1 (en) | 2013-05-22 | 2013-05-22 | Scroll compressor and CO2 vehicle air conditioner with a scroll compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2806164A1 EP2806164A1 (en) | 2014-11-26 |
EP2806164B1 true EP2806164B1 (en) | 2015-09-09 |
Family
ID=48569935
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13168729.5A Active EP2806164B1 (en) | 2013-05-22 | 2013-05-22 | Scroll compressor and CO2 vehicle air conditioner with a scroll compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US9512840B2 (en) |
EP (1) | EP2806164B1 (en) |
JP (1) | JP6425417B2 (en) |
CN (1) | CN104179682B (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10350966B2 (en) | 2015-08-11 | 2019-07-16 | Ford Global Technologies, Llc | Dynamically controlled vehicle cooling and heating system operable in multi-compression cycles |
DE102015120151A1 (en) | 2015-11-20 | 2017-05-24 | OET GmbH | Displacement machine according to the spiral principle, method for operating a positive displacement machine, vehicle air conditioning and vehicle |
DE102016105302B4 (en) | 2016-03-22 | 2018-06-14 | Hanon Systems | Control flow control valve, in particular for scroll compressors in vehicle air conditioners or heat pumps |
DE102017105175B3 (en) | 2017-03-10 | 2018-08-23 | OET GmbH | Positive displacement machine according to the spiral principle, method for operating a positive displacement machine, positive displacement spiral, vehicle air conditioning system and vehicle |
DE102017110913B3 (en) | 2017-05-19 | 2018-08-23 | OET GmbH | Displacement machine according to the spiral principle, method for operating a positive displacement machine, vehicle air conditioning and vehicle |
DE102018217911A1 (en) * | 2018-10-19 | 2020-04-23 | Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg | Compressor module and electromotive refrigerant compressor |
GB2583373A (en) * | 2019-04-26 | 2020-10-28 | Edwards Ltd | Scroll pump crank sleeve |
WO2021040360A1 (en) * | 2019-08-27 | 2021-03-04 | Samsung Electronics Co., Ltd. | Scroll compressor |
DE102020110097A1 (en) * | 2020-04-09 | 2021-10-14 | OET GmbH | Displacement machine, process, vehicle air conditioner and vehicle |
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JPH05187371A (en) * | 1992-01-13 | 1993-07-27 | Hitachi Ltd | Scroll compressor and end mill for machining scroll lap |
US5199280A (en) | 1991-11-25 | 1993-04-06 | American Standard Inc. | Co-rotational scroll compressor supercharger device |
JP3170111B2 (en) * | 1993-09-24 | 2001-05-28 | 株式会社日立製作所 | Scroll compressor |
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JP2002161875A (en) * | 2000-11-27 | 2002-06-07 | Matsushita Electric Works Ltd | Scroll pump |
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-
2013
- 2013-05-22 EP EP13168729.5A patent/EP2806164B1/en active Active
-
2014
- 2014-05-20 US US14/282,509 patent/US9512840B2/en active Active
- 2014-05-21 CN CN201410216902.9A patent/CN104179682B/en not_active Expired - Fee Related
- 2014-05-21 JP JP2014104948A patent/JP6425417B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US9512840B2 (en) | 2016-12-06 |
CN104179682B (en) | 2018-03-02 |
US20140348681A1 (en) | 2014-11-27 |
JP6425417B2 (en) | 2018-11-21 |
EP2806164A1 (en) | 2014-11-26 |
CN104179682A (en) | 2014-12-03 |
JP2014228002A (en) | 2014-12-08 |
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