EP1171743A2 - Systeme refrigerant pour appareils frigorifiques domestiques - Google Patents

Systeme refrigerant pour appareils frigorifiques domestiques

Info

Publication number
EP1171743A2
EP1171743A2 EP00926921A EP00926921A EP1171743A2 EP 1171743 A2 EP1171743 A2 EP 1171743A2 EP 00926921 A EP00926921 A EP 00926921A EP 00926921 A EP00926921 A EP 00926921A EP 1171743 A2 EP1171743 A2 EP 1171743A2
Authority
EP
European Patent Office
Prior art keywords
compressor
piston
suction
fluxomizer
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP00926921A
Other languages
German (de)
English (en)
Inventor
Eberhard Günther
Ingrid GÜNTHER
Eberhard Findeisen
Matthias Schubert
Andre Trautmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guenther Engineering GmbH
Original Assignee
Guenther Engineering GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guenther Engineering GmbH filed Critical Guenther Engineering GmbH
Publication of EP1171743A2 publication Critical patent/EP1171743A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0016—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 adaptations of pistons with valve arranged in the piston
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/042—Details of condensers of pcm condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound

Definitions

  • the invention relates to a hermetic motor compressor, a nerêtrkolben for this purpose and a Fluxomizer as well as a refrigeration system for household cooling devices realized using the motor compressor with the piston and the Fluxomizer.
  • refrigeration systems In household refrigerators, refrigeration systems are usually used which operate on the principle of the compression refrigeration machine and consequently have a refrigerant circuit which consists of a compressor with suction and / or pressure damper, a condenser and an evaporator, with a relaxation throttle between the condenser and the evaporator a capillary tube is preferably arranged in household cooling devices.
  • the aforementioned components of the refrigerant circuit are known in a wide variety of designs as well as their arrangement in or on cooling devices.
  • the refrigeration unit is usually accommodated in the appliance base, with the exception of the evaporator, which is integrated in the rear wall of the appliance or forms it.
  • the known refrigeration units for household refrigeration appliances have the disadvantage that each component is assembled at the location provided for it and the refrigerant circuit is produced by means of corresponding lines, which means that the manufacture of the refrigeration appliances is technologically complex and therefore inexpensive.
  • the arrangement of the refrigeration unit as a preassembled module as is known, for example, from German utility model 92 06 167, provides a remedy in this regard.
  • the known solution relates to a refrigerator and / or freezer with a base part, in which the condenser and compressor are accommodated and which are blown by a fan.
  • the condenser, compressor and fan are arranged in a closed air duct, the suction and discharge openings of which are closed by porous and / or lattice-like disks and lie on a base side and are covered by doors or flaps.
  • the side walls of the air duct are lined with sound absorbing material, the air duct itself consists of a U-shaped, tube-like tube and is held on the surrounding base box by elastic or elastomeric elements or is supported in a similar manner on the base of the base box.
  • the known solution provides that the compressor and / or the condenser is connected to the wall of the air duct via elastic or elastomeric elements or is supported on the bottom of the air duct.
  • a disadvantage of the known solution is that the arrangement of the functional elements accommodated in the base part occupies the entire space of the armature, which not least means that the insulation of the room sound requires a relatively high outlay.
  • the known solution is tailored to the geometry of the base part of a specific cooling device, so that use in a different type requires at least structural modifications.
  • the storage conditions of the refrigerated goods are in the foreground.
  • the refrigerator compartment temperature is controlled by switching the compressor on and off relatively quickly, ie by intermittent operation of the refrigeration system.
  • this results in considerable fluctuations in the temperature of the refrigerator compartment, especially when storing new food, combined with the fact that there is a considerable difference between the temperature of the storage room and the surface of the evaporator and the resulting drying of the refrigerated goods.
  • a departure from intermittent operation is made possible by the use of an evaporator with latent heat storage, as is known from the German description of the invention 39 26 250 AI.
  • the evaporator is surrounded by a cold store, which is filled with a cold storage agent, which has a phase transition point at a certain temperature and whose heat capacity corresponds to the heat absorption of the cooling device in a predetermined time, which is at least several hours.
  • the compressor operation can thus be regulated within narrow limits close to the phase transition temperature, especially since a fan for forced convection advantageously improves the heat transfer between the evaporator surface and the cooling compartment. This ensures a high temperature consistency in the storage compartment, a high cooling rate and a significant reduction in the drying out of the refrigerated goods.
  • a refrigeration system for household cooling devices forming a refrigerant circuit, which consists of a hermetic motor compressor, a condenser on the pressure side connected to the motor compressor, a capillary tube which is connected on the outlet side to the condenser and which is in thermal contact with the suction line of the motor compressor there is an evaporator connected to the capillary tube, which is thermally coupled to a latent heat store and connected to the motor compressor on the suction side, and a fan for increasing the convection in the cooling compartment of the cooling unit, the output of the evaporator being connected to the suction port of the motor compressor connected Fluxomizer is guided, the motor compressor and the Fluxomizer are mounted elastically in a soundproof sleeve on a chassis and the maximum height of the chassis including the assembled modules and the soundproofing cover corresponds to the base height of the cooling unit.
  • a preferred embodiment of the refrigeration system according to the invention is that the maximum overall height of the chassis, including the assembled assemblies and the soundwave
  • This relates to a hermetic motor compressor with a capsule bottom and a capsule cover, which are hermetically connected to one another.
  • a drive motor is arranged in the interior of the capsule, the power supply of which is hermetically guided through the capsule cover.
  • a cylinder assembly is hermetically connected to the capsule cover, a suction valve being arranged in the cylinder head.
  • the stator pack of the drive motor is preferably pressed into the capsule cover.
  • a pressure line is led hermetically through the capsule bottom to the outside.
  • a tube is fixedly arranged between the capsule base and the capsule lid, the tube interior being connected to the interior of the capsule and to the pressure line by means of at least one jacket bore. The tube serves as a bearing axis for the rotor package of the drive motor.
  • the upper bearing shell of the rotor is designed as a cylindrical disk and is arranged eccentrically with respect to the tube axis and serves as a lifting disk in that the connecting rod bearing surrounds the outer surface of the cylindrical disk.
  • the connecting rod pivotally connected to the connecting rod bearing is rigidly connected to the piston oscillating in the cylinder.
  • the piston is equipped with a pressure valve.
  • the rotor core can suitably have a balance mass balance.
  • connection between the flow path and the displacement of the piston is advantageously arranged at a crank angle of approximately 20 ° above the bottom dead center position of the piston.
  • the flow section is connected on the input side to the connecting line of the condenser to the capillary, during which the outlet of the flow section opens into the condenser inlet or into the pressure line.
  • Compressor piston is provided, which is arranged rigidly connected to a reciprocating connecting rod, has a sealing lip abutting the cylinder inner wall and has a flow channel for the refrigerant with a valve which opens the flow channel during the compression stroke and closes during the intake stroke, whereby at a bell-shaped guide element is rigidly attached to the reciprocating connecting rod and has a cylindrical, axially arranged jacket region. On the side of the guide element facing the compression chamber, this is arranged in a radially projecting manner and has a flat piston head.
  • the edge of the cylindrical region of the guide element facing away from the piston crown is angled all around towards the inner wall of the cylinder, the guide element being surrounded by a sealing ring which is slidably arranged on the cylindrical outer surface and which has an edge which lies all around the inner wall of the cylinder.
  • the guide element is provided with passages whose openings on the compression chamber side are released by the sealing ring during the compression stroke and are covered during the suction stroke.
  • the length of the connecting rod is at least eight times the crank radius.
  • the object of the invention is achieved by the design of the fluxomizer, which consists of a liquid separator into which the suction line connected to the evaporator outlet of a refrigeration system opens and which has a liquid collecting container, and a suction damper which is connected to the liquid separator and to the suction nozzle the compressor of a refrigeration system is connected.
  • the suction damper is designed as an internal counterflow heat exchanger.
  • a riser pipe is arranged in the liquid collecting container and opens as an injection cannula into the suction port of the compressor.
  • the fluxomizer according to the invention is advantageously designed in that its outlet opening is connected directly to the suction port of the compressor.
  • the inner counterflow heat exchanger consists of the capillary of the refrigeration system connecting the condenser to the evaporator, which is wound twice around the suction line, and the suction line.
  • the fluxomizer according to the invention is advantageously designed in that it represents a closed assembly which is thermally decoupled from the environment, in particular by a cylindrical casing is provided which, in addition to the thermal decoupling, functions as elastic mounting and sound insulation, preferably both for the fluxomizer and for the hermetic compressor.
  • the hermetic compressor, condenser and fluxomizer limits the overall height of the refrigeration system according to the invention to the base height of household appliances and the compact construction and arrangement of the components, the hermetic compressor, condenser and fluxomizer, is the prerequisite for applications in cooling units of various designs. With the exception of the installation of the evaporator, both the components and the refrigeration system are installed independently of the manufacture of the cooling units.
  • the components and in particular the hermetic compressor consist of a few, easily assembled components. Because of the liquid reservoir arranged in the Fluxomizer, there is no need to optimize the refrigerant charge. Instead, there is a self-regulating behavior in that the compressor draws in the optimal amount of refrigerant.
  • the design of the hermetic compressor makes it possible to dispense with the function of heat dissipation via the capsule surface and to reduce the noise level to a low level by means of secondary noise protection measures.
  • the secondary noise protection measures around the hermetic compressor also form the elastic mounting of the hermetic compressor and the fluxomizer in the chassis of the refrigeration system.
  • the process behavior of the refrigeration system according to the invention is further optimized in such a way that a high specific refrigeration capacity is generated and undefined liquid suction of the compressor is avoided by the refrigerant being overheated to the ambient temperature.
  • the overheating heat is not extracted from the environment but is obtained from the subcooling of the liquefied refrigerant through the use of the counterflow heat exchanger.
  • the overall energetic behavior is characterized in that compression begins at ambient temperature and is isotropic in principle, but takes place under adiabatic when liquid refrigerant is injected. The losses of the compressor are minimized and added to the refrigerant after compression.
  • the suction gas mass flow drawn in by the compressor is compressed in the displacement and, according to the direct current principle, reaches the interior of the capsule through the pressure valve arranged in the piston.
  • the piston force corresponds to the rod force, so that the process forces do not produce any normal force that causes wear.
  • the rod force is lower than with conventional engine designs. The result is a lower torque requirement for the drive motor. Since the sealing ring is extremely slippery and its surface abutting the inner wall of the cylinder is small due to the configuration as a lip, the friction losses between the piston and the cylinder are minimal.
  • the friction is nevertheless sufficient to prevent the axial vibration behavior of the sealing ring, as a result of which the function of the sealing ring as a pressure valve is performed without bounce, without the need for a valve spring, since the mass force of the sealing ring provides the closing force for the valve.
  • the stroke gap area of the pressure valve realized by means of the sealing ring can be chosen to be so large due to its location outside the compression space without enlarging the harmful space that the flow losses remain minimal.
  • the reduction of the oscillating mass in comparison to conventional engine designs to is up to V 35 results in a noticeable acoustic improvement in the operation of reciprocating compressors in addition to a reduction in the manufacturing effort.
  • a DC compressor implemented with the suction valve in the cylinder head and the pressure valve in the piston is characterized by the almost complete avoidance of heating of the suction gas on its way into the cylinder.
  • the face of the piston which can be made completely flat, ensures minimal damage volume during compression. Due to the compressed gas atmosphere in the interior of the capsule and the targeted delivery of compressed gas, there is no need for a special pressure damper to reduce the pressure pulsation.
  • the compressed gas flows through the stator package, the annular gap between the stator and the rotor, the rotor bearings and the annular space within the rotor, from which it passes through the jacket bore into the interior of the axle tube and from there into the pressure line, whereby it passes on this Way the engine heat loss absorbs.
  • the pressurized gas then flows through the condenser, the expansion capillary and the evaporator, from which the mass flow is sucked into the fluxomizer.
  • the mass flow enters the liquid separator of the fluxomizer, liquid components of the mass flow are separated, which can contain both oil and liquid refrigerant.
  • the gas mass flow flows through the suction line inside the fluxomizer, which is part of the counterflow heat exchanger, which also acts as a suction damper, absorbs heat, causing the liquid flow through the capillary to be supercooled, and reaches the suction port of the compressor.
  • Liquid oil / refrigerant mixture is introduced into the suction gas stream via the injection cannula opening into the suction nozzle, so that under-adiabatic compression is achieved.
  • the sub-adiabatic behavior which leads to a reduction in compressor losses, is reinforced by additional cooling of the cylinder.
  • the additional cooling takes place with liquid refrigerant by passing it through the flow section thermally coupled to the cylinder or additionally sucking it out of the flow section through the injection bore into the displacement when the piston reaches the area of bottom dead center and thereby the injection bore releases, and evaporates in the displacement.
  • Spray lubrication is carried out in the same way as the lubrication of 2-stroke engines, but without oil combustion, which supplies all bearing points with sufficient oil and lubricates them safely.
  • Fig. 1 is a block diagram of a refrigeration system according to the invention
  • 2 shows a diagram of a hermetic compressor according to the invention
  • FIG. 3 shows a diagram of a fluxomizer according to the invention
  • FIG. 4 shows a diagram of a compressor piston according to the invention
  • Fig. 5 is a block diagram of a refrigeration system according to the invention with cylinder cooling and
  • FIG. 6 shows a diagram of a hermetic compressor according to the invention with cylinder cooling.
  • the fluxomizer 40 comprises a suction damper 43 designed as an internal heat exchanger and a liquid separator 41, in the liquid reservoir of which an injection cannula 45 is immersed, which opens into the middle of the suction nozzle 44 of the compressor 102.
  • a suction line 6 connected to the outlet of an evaporator 3 opens tangentially into the liquid separator 41.
  • the evaporator 3 has a latent heat accumulator for lowering the difference between the evaporator surface temperature and the storage room temperature, in that heat is also absorbed when the refrigeration system is switched off.
  • the refrigerant inlet of the evaporator 3 is connected to a condenser 2 via a capillary tube 42.
  • the capillary tube 42 is in thermal contact with the suction damper 43.
  • a pressure line 5 opens into the condenser 2 and is hermetically guided outwards from the capsule of the hermetic compressor 10.
  • the refrigeration system according to the invention is designed as a compact assembly.
  • the hermetic compressor 10, the fluxomizer 40 and the condenser 2 are accordingly arranged on a chassis and constructed such that the overall height, including secondary soundproofing means, does not exceed 100 mm.
  • the secondary soundproofing means simultaneously serve for the elastic mounting of the hermetic compressor 10 and the fluxomizer 40 on the chassis.
  • the coupling point of the suction line 6 with the fluxomizer 40 is vibration-free. forms to avoid excitation of the evaporator 3.
  • the capsule of the hermetic compressor 10 consists of a capsule base 11 and a capsule cover 12, which are hermetically connected to one another.
  • a cylinder assembly 13 is hermetically connected to the capsule cover 12.
  • a stator pack 14 of a drive motor 101 with a field winding 14 ′ is pressed into the capsule cover 12.
  • An axle tube 15 is arranged centrally between the capsule base 11 and the capsule cover 12.
  • the capsule cover 12 has a pin 12 ', onto which the axle tube 15 is pressed, and the capsule bottom 11 has a socket 11' which is advantageously designed to accommodate a bearing and into which the axle tube 15 is inserted.
  • the axle tube 15 is provided at least half of its length with at least one radial jacket bore 16.
  • a pressure line 5 opens into the interior of the axle tube 15, which is hermetically guided out of the capsule base 11.
  • a rotor 18 of the drive motor 101 with an upper bearing plate 19 and a lower bearing plate 20 is mounted on the axle tube 15, a lower bearing 20 ′, preferably designed as a sliding bearing, being received at the end by the bushing 11 ′.
  • An upper bearing 19 ' which is arranged in the region of the pin 12', can be designed as a gas or sliding bearing.
  • the upper end plate 19 of the rotor 18 is designed as a circular disk which is arranged eccentrically with respect to the tube axis and is surrounded by a connecting rod bearing 21.
  • a connecting rod 22 is pivotally connected to the connecting rod bearing 21, to which a piston 23 is rigidly attached.
  • the piston 23 oscillates translationally in the cylinder assembly 13 due to the stroke generated by means of the eccentric mounting of the upper end plate 19 and transmitted via the connecting rod 22.
  • the piston 23 is shown in its bottom dead center position.
  • the rigid connection of the piston 23 to the connecting rod 22 causes the piston 23 to undergo a tilting vibration with respect to the cylinder axis, as a result of which the piston force is transmitted directly to the connecting rod 22 and thus corresponds to the rod force, that is to say that there is no disassembly into a normal and a Rod force share takes place.
  • This has the advantage of reducing the wear and tear that occurs with conventional piston designs. gene with a connecting rod pivotally mounted on a piston pin results essentially from the normal force.
  • the piston 23 is also provided with a pressure valve shown in Figure 4, which consists of a slightly axially displaceable sealing ring 236, whereby the direct current principle of the refrigerant mass flow and thus the spray lubrication of all bearings is realized by the suction valve arranged in the cylinder head, not shown
  • Aspirated suction gas including any liquid refrigerant and oil after compression through the pressure valve located in the piston 23 enters the capsule interior so that it flows through the annular gap between the stator 14 and rotor 18 and the upper rotor bearing 19 'one between the rotor 18 and the axle tube 15 located annular space 24, from which it passes through the radial bore 16 into the interior of the axle tube 15 and from this into the pressure line 5.
  • the forced path of the pressurized gas flow in the interior of the capsule formed in this way lubricates all bearing points and absorbs the heat loss from the engine, so that the capsule itself does not have to perform any heat transfer function. This makes it possible to absorb the vibrations outside the capsule by means of an elastic covering which provides sound insulation.
  • a fluxomizer 40 according to the invention is shown in FIG. 3. It consists of a cylindrical liquid separator 41, into which the suction line 6 connected to the outlet of the evaporator 3 opens tangentially, and a suction damper 43 designed as an inner heat exchanger.
  • the inner heat exchanger 43 comprises a spiral-shaped flow body through which the suction gas flow flows and in addition to whose calming is dampened in the liquid separator 41, and a double-helical section 47, pressed into the flow body, of the capillary tube 42 connecting the condenser 2 to the evaporator 3 as a relaxation throttle, which can advantageously be wound around the suction line 6 before it enters the fluxomizer 40.
  • a liquid reservoir 46 is formed, into which a riser tube is immersed, which, as an injection cannula 45, opens centrally in the outlet opening of the fluxomizer 40, into which the suction nozzle 44 of the compressor 102 is inserted and hermetically connected to the fluxomizer 40.
  • An elastic covering of the fluxomizer 40 is not shown, which the damping mounting of the fluxomizer 40 on the chassis and also for its thermal decoupling from the environment and advantageously forms a unit with the casing of the hermetic compressor 10.
  • the Fluxomizer 40 is essentially responsible for ensuring that the process behavior actually achieved is optimally approximated to the theoretical cycle. Because of the liquid reservoir 46, which is at the same time a refrigerant collector and a lubricant depot, the assembly of the refrigeration system according to the invention is simplified since an optimization of the refrigerant charge is not necessary.
  • FIG. 4 shows a preferred embodiment of the piston according to the invention.
  • the drawing shows cylinder walls 237 of a reciprocating compressor 102 (according to FIG. 1), between which a piston according to the invention oscillates. The stroke movements are indicated by dashed arrows. Accordingly, the left side of the drawing symbolizes the piston during the compression stroke and the right side the piston during the intake stroke.
  • the cylinder has a cylinder head which is connected to a suction line 6 (according to FIG. 1) and in which a suitable suction valve is arranged.
  • the piston consists of a guide element 232, which is bell-shaped and rigidly connected to a connecting rod 22 on its side facing away from the crank, and a piston head 233, which is fixedly connected to the guide element 232.
  • connecting rod 22 and guide element 232 in one piece.
  • the connecting rod 22 is articulated on a crank driven by an electric motor.
  • the guide element 232 has an annular end face on which the piston head 233 is fastened flat.
  • the diameter of the piston head 233 is smaller than the diameter of the cylinder bore in order to prevent the piston from jamming with the cylinder inner wall 237, since the piston rigidly connected to the connecting rod 22 oscillates axially with the crank rotation.
  • the diameter of the guide element 232 is in turn smaller than the diameter of the piston head 233, the guide element 232, starting from the annular end face, being formed on its periphery coaxially and cylindrically to the connecting rod 22 and in this way as a sliding surface 234 facing the inner cylinder wall 237.
  • the cylindrical sliding surface area 234 of the guide element 232 is provided with through openings 238 distributed at the same angle over the entire lateral surface.
  • the sliding surface area 234 is delimited by the rear side of the peripheral area of the piston head 233 projecting over the guide element 232. on the one hand and an edge 235 angled all round towards the cylinder inner wall 237, which serves as a lift catcher, on the other hand.
  • a sealing ring 236 made of polytetrafluoroethylene is placed around the cylindrical region 234 of the guide element 232 and has a first sliding edge abutting against the sliding surface 234 and a second one against the inner wall 237 of the cylinder.
  • the side of the sealing ring 236 facing the rear of the piston head 233 is flat.
  • the sealing ring 236 changes its position due to a greater friction on the cylinder inner wall 237 than on the sliding surface 234.
  • the sealing ring 236 is in contact with the stroke catcher 235 and releases a stroke gap 239V.
  • the left side of the drawing symbolizes this state.
  • the right side of the drawing shows the position of the sealing ring 236 during the suction stroke of the piston.
  • the sealing ring 236 lies flat against the rear of the piston head 233.
  • sealing ring 236, each with a sealing lip resting on the cylinder inner wall 237 and a sealing lip on the sliding surface 234, results in a slidability on the respective surfaces which, even with the greatest inclination of the connecting rod 22 with respect to the cylinder axis and thus the greatest tendency of the piston to tilt, seals the compression chamber 2310 against the crankcase between the piston and the cylinder inner wall 237 and the function of the sealing ring 236 as a pressure valve.
  • the embodiment of the refrigeration system according to the invention according to FIGS. 5 and 6 has an additional cylinder cooling 51. Since the rest of the design is identical, reference is made to the explanations relating to FIGS. 1 and 2.
  • the additional cylinder The cooling of the compressor 102 consists of a flow section 51 through which liquid refrigerant flows. The liquid refrigerant is branched off from the connection between the condenser 2 and the capillary 42 and, after flowing through the flow path 51, is returned to the pressure line 5 between the compressor outlet and the condenser inlet, both the branch and the return connection being arranged at positions that are suitable in terms of construction can.
  • FIG. 1 the flow path 51
  • FIG. 6 shows its connection to the cylinder displacement 2310 (according to FIG. 4) in the form of at least one injection bore 25.
  • the injection bores 25 are at a crank angle of 20 ° above the bottom dead center position of the piston 23. They are evenly distributed over the circumference of the cylinder wall 237 (according to FIG. 4). The transition from the inner surface of the cylinder wall to the bore is as burr-free as possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un système réfrigérant pour appareils frigorifiques domestiques, utilisant un motocompresseur à piston compresseur oscillant et un fluxomiseur. L'invention a pour but de fournir un système réfrigérant du type précité, pouvant être fabriqué avec une faible dépense en moyens technologiques, utilisable pour différents cas d'application sans recourir à des modifications importantes et utilisant de façon optimale le cycle de Carnot théorique. Ce but est atteint grâce au système selon l'invention, lequel est caractérisé en ce qu'il comprend un motocompresseur hermétique, un condenseur connecté, côté refoulement, au motocompresseur, un tube capillaire connecté, à sa sortie, au condenseur, et se trouvant en contact thermique avec le conduit d'aspiration du motocompresseur, un évaporateur connecté au tube capillaire, accouplé thermiquement avec un régulateur thermique à changement d'état et connecté, côté aspiration, au motocompresseur, ainsi qu'un ventilateur pour amplifier la convection dans le compartiment réfrigérant de l'appareil frigorifique, en ce que la sortie de l'évaporateur est guidée sur un fluxomiseur connecté à la tubulure d'aspiration du motocompresseur, le motocompresseur et le fluxomiseur sont montés sur un châssis porté élastiquement dans une enveloppe d'insonorisation, et en ce que l'encombrement maximum en hauteur du châssis, y compris des groupes montés et de l'enveloppe d'insonorisation, correspond à la hauteur du socle de l'appareil réfrigérant. Le but de l'invention est atteint, en outre, grâce à la conception du compresseur hermétique, du piston compresseur oscillant et du fluxomiseur.
EP00926921A 1999-04-15 2000-04-13 Systeme refrigerant pour appareils frigorifiques domestiques Withdrawn EP1171743A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19916993 1999-04-15
DE19916993A DE19916993C1 (de) 1999-04-15 1999-04-15 Kolben für Kältemittelverdichter
PCT/EP2000/003356 WO2000063627A2 (fr) 1999-04-15 2000-04-13 Systeme refrigerant pour appareils frigorifiques domestiques

Publications (1)

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EP1171743A2 true EP1171743A2 (fr) 2002-01-16

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EP00926921A Withdrawn EP1171743A2 (fr) 1999-04-15 2000-04-13 Systeme refrigerant pour appareils frigorifiques domestiques

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EP (1) EP1171743A2 (fr)
JP (1) JP2002542448A (fr)
KR (1) KR20020000799A (fr)
CN (1) CN1347490A (fr)
AU (1) AU4549000A (fr)
BR (1) BR0009796A (fr)
CA (1) CA2370346A1 (fr)
DE (1) DE19916993C1 (fr)
WO (1) WO2000063627A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11015595B2 (en) 2016-06-30 2021-05-25 Graco Minnesota Inc. Piston pump and seal ring
CN107899803A (zh) * 2017-12-26 2018-04-13 安徽开诚电器有限公司 一种电器开关元件加工的喷涂设备
DE102019217779A1 (de) * 2019-04-26 2020-10-29 Continental Reifen Deutschland Gmbh Tragbares/transportables System zum Abdichten und Aufpumpen von Fahrzeugluftreifen mit gradliniger Druckluftströmung

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE643935A (fr) *
US2530648A (en) * 1946-09-26 1950-11-21 Harry Alter Company Combination accumulator, heat exchanger, and metering device for refrigerating systems
US3070973A (en) * 1961-06-16 1963-01-01 Gen Motors Corp Refrigerating apparatus
US3084523A (en) * 1962-01-30 1963-04-09 Refrigeration Research Refrigeration component
US3283524A (en) * 1964-03-17 1966-11-08 Byron John Thomson Refrigeration system
US3319577A (en) * 1965-02-25 1967-05-16 Margrete L Stinnes Sliding seal and valve for reciprocating pump plunger
FR1540705A (fr) * 1967-10-11 1968-09-27 Danfoss As Motocompresseur blindé, notamment pour réfrigérateurs
US3545891A (en) * 1968-11-01 1970-12-08 Lennox Ind Inc Compressor crankshaft arrangement
US3563677A (en) * 1969-04-01 1971-02-16 Carrier Corp Compressor
DE2915848A1 (de) * 1979-04-19 1980-11-06 Helmut Thurner Verdichter- und sauggeraet und kolben fuer dieses geraet
JPS60164684A (ja) * 1984-02-08 1985-08-27 Hitachi Ltd 自動車用空気調和装置の圧縮機
DE3616968A1 (de) * 1986-05-20 1987-11-26 Bosch Gmbh Robert Taumelkolben-kompressor
JPS63137267U (fr) * 1987-02-27 1988-09-09
DE3926250A1 (de) 1989-08-09 1991-02-14 Juergen Mertens Kuehl- und gefrierschrank
DE9206167U1 (fr) 1992-05-08 1993-06-09 Liebherr-Hausgeraete Gmbh, 7955 Ochsenhausen, De
JPH0679883A (ja) * 1992-09-02 1994-03-22 Fuji Xerox Co Ltd 流体移送ポンプ
DE4243320A1 (de) * 1992-12-21 1994-06-23 Illbruck Gmbh Kühlmöbel
DE4429097A1 (de) * 1994-08-17 1996-02-22 Thurner Bayer Druckguss Kolbenverdichter für gasförmige Medien
US5669232A (en) * 1994-11-22 1997-09-23 Sanyo Electric Co., Ltd. Refrigerating unit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0063627A2 *

Also Published As

Publication number Publication date
CA2370346A1 (fr) 2000-10-26
CN1347490A (zh) 2002-05-01
AU4549000A (en) 2000-11-02
KR20020000799A (ko) 2002-01-05
WO2000063627A2 (fr) 2000-10-26
JP2002542448A (ja) 2002-12-10
BR0009796A (pt) 2002-03-26
DE19916993C1 (de) 2000-02-10
WO2000063627A3 (fr) 2001-03-15

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