EP2500567A1 - Refrigeration compressor - Google Patents

Refrigeration compressor Download PDF

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Publication number
EP2500567A1
EP2500567A1 EP10803207A EP10803207A EP2500567A1 EP 2500567 A1 EP2500567 A1 EP 2500567A1 EP 10803207 A EP10803207 A EP 10803207A EP 10803207 A EP10803207 A EP 10803207A EP 2500567 A1 EP2500567 A1 EP 2500567A1
Authority
EP
European Patent Office
Prior art keywords
compressor
heat
accumulating material
heat accumulating
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Withdrawn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
EP10803207A
Other languages
German (de)
English (en)
French (fr)
Inventor
Fernando Antonio Ribas Junior
Rodrigo Kremer
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.)
Whirlpool SA
Original Assignee
Whirlpool SA
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 Whirlpool SA filed Critical Whirlpool SA
Publication of EP2500567A1 publication Critical patent/EP2500567A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/048—Heat transfer

Definitions

  • the present invention relates to a refrigeration compressor and, more particularly, to a compressor whose cooling is carried out by using characteristics from its thermal transient when said compressor is applied to a refrigeration system.
  • a compressor has the function of increasing the pressure of a certain fluid volume to a pressure required for carrying out a refrigeration cycle.
  • hermetic compressors generally comprising a sealed housing where the compressor parts are mounted: a motor-compressor assembly comprising a cylinder block having an end closed by a cylinder head which defines a discharge chamber in communication with a compression chamber defined inside the cylinder, the compression chamber being closed by a valve plate provided between the cylinder end and the cylinder head.
  • Patent WO 2007/068072 utilizes the concept of insulating the heating sources of the cylinder.
  • a spacing conduit is built over the valve plate and open into the inner cavity of the compressor housing, maintaining the compressor cylinder cap spaced apart from the valve plate and forming an annular plenum around the spacing conduit. This allows to reduce the heat transmission from the cylinder cap to the valve plate, which eventually reduces the heating of the cylinder block in the region of the compression chamber, increasing the efficiency of the compressor.
  • the duct has a heat absorption end on the cylinder and another heat release end spaced apart from the cylinder block, such that the heat generated with the coolant compression inside the cylinder is absorbed and dissipated to an area further away from the cylinder, thereby reducing the cylinder temperature and also increasing the compressor efficiency.
  • the present invention aims to promote the cooling of the compressor by using characteristics of the thermal transient from the compressor when the same is applied to a refrigeration system.
  • the present invention takes advantage of the thermodynamics existing between the compressor and the compression system, achieving the reduction of internal temperatures reliably and efficiently and hence improving the performance of the compresor.
  • the present invention achieves the above objects by means of a hermetic compressor comprising a housing which encloses the component parts of the compressor, with a heat accumulating material occupying an internal volume or adjacent to the compressor housing.
  • the heat accumulating material acts as a thermal capacitor able to absorb high amounts of heat while the compressor is on and to reject heat while the compressor is off, in order to increase the thermal efficiency of the compressor.
  • the heat accumulating material rejects heat at a first amount of heat while the compressor is on and a second amount of heat while the compressor is off.
  • the heat accumulating material can reject a minimum amount of heat while the compressor is on and a high amount of heat while de compressor is off.
  • the heat accumulating material can absorb heat while the compressor is on and reject some from this heat to one of the components of the compressor while the compressor is off.
  • the heat accumulating material may be a latent heat accumulator or a sensitive heat accumulator, however, the use of a PCM (phase-change material) is particularly advantageous for the proposed inventive concept.
  • PCM phase-change material
  • the PCM comprises the entire material which, at a certain design temperature, starts to receive latent heat, that is, a process at a substantially constant temperature and with a high heat absorption capacity.
  • a PCM material is usually defined as a material that goes through a change between the liquid phase and the solid phase, there are a few PCM materials that, instead of changing their phase, change the structure of their matter; these PCMs are called solid-solid PCMs.
  • solid-solid PCMs solid-solid PCMs.
  • the PCM nomenclature also covers materials which change their structure at a certain design temperature, absorbing high heat rates.
  • the heat accumulating material may occupy an idle volume inside the compressor, or may even be a part of the structure from at least one of the compressor parts.
  • the present invention will be described in detail with reference to the examples as shown in the drawings. While the detailed description uses as an example an alternative compressor for the refrigeration, it should be understood that the principles of the present invention may be applied to any type, size or arrangement of refrigeration compressor. Accordingly, the present invention may be applied to hermetic or semi-hermetic reciprocating compressors, to rotating compressors or scrolling compressors, or to any type of refrigeration compressor able to receive a volume of a heat accumulating material acting as a thermal capacitor.
  • the heat capacity does not play any role, as it only serves to change the heating time of the components.
  • the compressor does not work uninterruptedly. It goes through a cycling process, wherein in some cases, it remains longer in the off state than in the on state. Hence, the temperatures of the internal components of the compressor during its operation on the refrigeration system are not stabilized.
  • the present invention is based on the use of elements which are able to absorb the heat from hot components during the compressor operation time.
  • the use of these elements has a direct impact on the temperature reduction of these components, increasing the thermodynamic efficiency of the compressor.
  • the present invention discloses a thermal managing mechanism for compressors which makes use of the thermal behavior of its components when on a refrigeration system, thereby reducing the heating of the compressor during its working period.
  • high heat content elements means heat absorbing elements, wherein a wide range of materials could be used for manufacturing such elements.
  • the present invention is based on the use of heat accumulating materials occupying an internal volume or adjacent to the compressor housing, and is not limited to a “self-contained element” to be inserted into the internal space of the compressor.
  • phase-change heat absorbing elements work with a substantially constant temperature during the heat absorbing process (which boosts this absorption and also prevents these components from heating the other components).
  • the working temperature from these components is set (by selecting a material having a desired phase-change temperature), it is possible to adjust the working temperature from the internal components at an optimum point based on the system dynamics, thereby achieving higher control over the solution.
  • phase change materials comprise paraffins, special-purpose greases, among other components, which may be manufactured so as to change their phase at different design temperatures. It is to be understood, however, that while most of the phase changes are solid-solid, structural changes from matter (solid-solid PCM) also able to absorb high amounts of heat at a design temperature are also included within the scope of the present invention.
  • this process provides a high energy absorption capacity with a substantially constant temperature, as opposed to a sensitive heat accumulation process, which entails significant temperature variations.
  • the present invention is based on the inclusion of a heat accumulating material occupying an internal volume or adjacent to the compressor housing.
  • this material may be employed in many locations in the compressor, wherein this location should be determined according to its efficacy in reducing the temperatures from the internal components, the available space for allocating these components, the involved costs, and the technological challenges to that end.
  • the heat accumulating material acts as a thermal capacitor, absorbing high amounts of heat while the compressor is on and rejecting this heat while the compressor is off.
  • thermo capacitor may take two different forms: it may absorb high amounts of heat, rejecting as little as possible while the compressor is on and then reject heat while in the off state, or it may absorb high amounts of heat during the on state and keep an uniform heat removal rate during on and off times. In this latter form, although there is a heat rejection while the compressor is on, the energy removal generated is much higher during this same period, contributing to the lowering of the thermal profile.
  • the presence of one or another dynamic characteristic will depend on heat input and output boundary conditions (convection coefficients and temperature potential), and will vary according to the design.
  • Figure 1 shows a first embodiment of the present invention, where the heat accumulating material is located in a volume formed between a casing which surrounds the cylinder cap and the compressor cylinder cap.
  • This region of the cylinder cap is critical for the compressor, since various gas communications flow therethrough.
  • the suction gas in order to get into the cylinder, passes over the region of the suction muffler which is in contact with the cylinder cap.
  • the high temperature gas from the compression is also discharged to the cap, from where it follows to the remainder of the discharge system.
  • the cap upon cooling, absorbs more heat from the cylinder, promoting the thermodynamic efficiency of the compressor.
  • FIG 1 a portion of a compressor is shown, along with the casing 1 which surrounds the cap 2 of the cylinder 3. Inside the space formed between the casing 1 and the cap 2, a volume 4 is created, where the heat accumulating material is stored (as previously mentioned, this material could be a grease, a paraffin, another type of PCM, or even another material having a high heat capacity).
  • this material could be a grease, a paraffin, another type of PCM, or even another material having a high heat capacity).
  • the casing 1 may further comprise outer fins 5.
  • the choice of adding the 5 results from the system thermodynamics itself: The entrance of heat into this system is very intense, as the gas from the cylinder cap strikes against the walls of the respective cap at high speed, giving rise to a high heat transfer rate. In order to reject the heat from the internal environment of the compressor, however, gas speeds are lower, especially while the compressor is off, when the gas in the internal environment only moves by natural convection. In order to be able to reject all the heat absorbed at high rates during the time period in which the compressor is on, the external heat transfer area is increased by adding fins 5.
  • a dark painting may also be chosen for the casing 1 and the fins 5, so as to increase the heat transfer by radiation.
  • fins 5 is only a preferred embodiment, and is not required in order to achieve the advantages obtained by adding a heat accumulating material into the volume formed between the cylinder cap 2 and the casing 1.
  • the fins could be inner fins, adjacent to the heat accumulating material, which would facilitate the flow of heat along its structure. As some materials exhibit low thermal conductivity, the inclusion of fins allows to maximize the heat flow along the material. In addition, other solutions designed for maximizing the heat transfer along the heat accumulating material could also be used within the scope of the present invention, such as, for example, porous metallic matrices injected along with the heat accumulator.
  • Figures 2 and 3 show graphs illustrating the results from the simulation performed (in figures, line A corresponds to the embodiment with the volume of heat accumulating material and line B corresponds to a conventional compressor).
  • Figure 2 shows a graph illustrating the heat rejected from the cylinder cap into the internal environment of the compressor. Although it seems that the cap having the heat accumulating material dissipates more heat than the normal cap, it should be analyzed the heat removed from the refrigerant gas inside the cylinder cap. This analysis, shown in figure 3 , shows that while the compressor is on (ON period in the figure) the heat accumulating element dissipates about 3W more than the normal cap, however, during this same period, the system removes extra 8 W from the gas. Thus, on the overall balance, a gas cooling is achieved and, hence, the thermal profile of the compressor is lowered, which contributes to increasing the energetic efficiency.
  • the graphs from figures 2 and 3 may be interpreted according to the following analysis of the system behavior:
  • the heat enters the heat accumulating material from a gas at high speed and temperature.
  • more time is required, since it is discharged into a gas at a lower speed (low convection coefficient) and with a lower temperature potential.
  • this process ends up by being a continuous discharge process, but having a much more intense heat gas absorption during the period in which the compressor is on (which period should be taken into account for purposes of the present invention).
  • FIG. 4 shows a second example embodiment of the present invention.
  • the heat accumulating material is provided into the discharge system of the compressor.
  • One of the benefits from adding the heat accumulating material onto the discharge way, whether on the cylinder cap or any other component downstream, is that, depending on the design optimization, upon achieving a substantially reduced gas temperature on the compressor outlet, the latter will have to reject less heat on the system condenser, which involves lowering the condensation temperature (and pressure), and hence, the cycle efficiency will be increased as a whole, as the difference between the temperatures of the heated source (condenser) and the cold source (evaporator) is reduced.
  • this embodiment shown in figure 4 may include fins 5, preferably arranged externally and attached to the concentric casing 7. The presence of these fins increases the external area, and consequently, aids in removing heat while the compressor is off.
  • internal fins could be provided in order to maximize the heat transfer along the heat accumulator matrix.
  • FIGS 5a, 5b, and 5c show a third embodiment of the present invention, wherein the heat accumulating material is employed externally to the region of the compressor crankcase 8.
  • a volume of phase-change material 6 is provided on the lower portion of the compressor in a volume separate from the internal environment of the compressor.
  • This volume may assume the form of a reservoir 9 to be closed by means of welding, gluing, or other forms that can assure the airtightness of the subject region, so as to ensure the sealing between the internal compressor volume and the heat accumulator volume.
  • this reservoir 9 may include metal fins 10 in the region of the heat accumulator volume, in order to facilitate the heat transfer from the heat accumulating material into the external environment, thereby maximizing the efficiency of the heat discharge process.
  • the compressor components in this case, the oil
  • the oil may go through fairly differentiated temperature regimes.
  • the oil On a pull-down test (critical scenario), the oil is very hot, and on a power consumption test, it is much cooler.
  • the oil viscosity highly differs between the two regimes, which affects the entire bearing design and does not allow these components to be accurately optimized.
  • phase-change heat accumulators at a certain temperature allows them to be adjusted so as to remove more heat on high temperature regimes and, thus, reduce the oil temperature on critical regimes, such as pull-down, thus bringing the temperatures from both pull-down and power consumption operation modes closer to each other. Consequently, oil viscosity variations in the application are reduced, allowing for a more optimized bearing design, which leads to increased energetic efficiency of the compressor.
  • a fourth illustrative embodiment of the present invention involves adding the heat accumulating material into a region on the outer portion of the compressor housing, said region being generated in association with the compressor base plate.
  • This embodiment shown in Figure 6 , comprises providing an enclosure 11 formed in association with the base plate 12 of the compressor at the portion adjacent to the outer portion of the compressor crankcase region 8.
  • the body of the enclosure 11 utilizes part of the base plate 12, thereby facilitating the assembly process.
  • the outer wall of the enclosure 11 may be provided with fins 13, in order to facilitate the heat transfer and to maximize the efficiency of the process of dissipating heat to the external environment.
  • a fifth illustrative embodiment of the present invention comprises adding a heat accumulating material into an enclosure 14 formed in the region of the compressor crankcase 8, wherein the enclosure 14 is internal to the compressor.
  • This embodiment shown in figure 7 , comprises an enclosure partially defined by the inner wall of the housing and by a further wall 15, wherein the enclosure 14 thus defined is located in a region immersed into the compressor oil.
  • the wall of the enclosure 14 may be provided with fins 16, in order to facilitate the heat transfer and to maximize the efficiency of the process.
  • the provision of the heat accumulator on the crankcase region has the advantage of relying on the whole base region of the housing together with the base plate as heat dissipating elements for the heat stored during the compressor operation time, which makes the discharge process of this thermal capacitor easier to be implemented.
  • a latent heat accumulator (particularly a phase change material - PCM) is highly advantageous in this scenario, since it could be employed not only reduce suction chamber and cylinder temperatures, but also to control and modulate the oil temperature.
  • Figure 8 shows a sixth illustrative embodiment of the present invention, where the heat accumulating material is added to the suction muffler.
  • an enclosure having a heat accumulating material 18 is provided on the suction tube 19 of the suction filter 20 of the compressor.
  • the heat accumulating material acts on the cooling of the gas when it passes through the tube 19, reducing its temperature on the cylinder entrance, and consequently increasing the energetic and volumetric efficiency.
  • the phase change temperature should be lower than the gas temperature at the region of the tube, such as to generate a temperature potential which favors heat removal.
  • the heat accumulating material could be a sensitive heat accumulator (e.g., water or oil), wherein, in this case, it must be carefully designed, taking into account temperature variations both in the absorption process and in the heat dissipation process by the heat accumulating matrix.
  • the heat accumulator is provided on the suction muffler in view of the system characteristics: a major cause of energetic inefficiency in compressors is the gas overheating during suction, and is based on the unnecessary heating of gas along the way from the suction pipe to the compression cylinder. Substantial efficiency gains were observed in the past by changing metal suction filters for plastic suction filters.
  • the temperature of gas at the cylinder entrance is around 20 to 30°C, which is higher than the temperature at the compressor entrance.
  • the heat accumulating material acts on the cooling of the gas when it passes through the tube 19, reducing its temperature on the cylinder entrance, and consequently increasing the energetic and volumetric efficiency.
  • phase change temperature should be lower than the gas temperature at the region of the tube, such as to generate a temperature potential which favors heat removal.
  • a sensitive heat accumulator e.g., water or oil
  • this design should be carefully planned in order to ensure the thermal discharge of the heat accumulator while the compressor is off.
  • the fins as seen in the drawings are only an illustrative embodiment, and whether they should be provided depends upon the application design for the heat accumulator.
  • the provision of such fins aims at enhancing gas heat removal (by increasing its area) from the tube to the region of the heat accumulator.
  • Figure 9 shows a seventh illustrative embodiment of the present invention, wherein the heat accumulating material is provided at the region of the compressor cylinder 3.
  • holding channels 23 for the heat accumulating material 24 are formed along the cylinder.
  • the channels 23 can be closed by the seal of the cylinder head 22 itself.
  • the channels can be alternatively closed by means of welding, gluing, or any other suitable means.
  • the heat accumulating material is a latent heat accumulator (PCM)
  • PCM latent heat accumulator
  • region of the cylinder would be the addition of a material having a phase change temperature higher than the continuous operation temperature, yet lower than in critical operation periods, such as to adjust the proper operation of the heat accumulator to extreme working regimes, such as high thermal stress regimes.
  • the efficiency could be increased indirectly, since by having a higher robustness at extreme condition, some of the design criteria may be relaxed (such as, for example, reducing the oil viscosity, since, at high temperatures, the PCM ensures a proper viscosity), allowing to improve the compressor operation at normal operation conditions.
  • fins 25 were provided with a view to facilitate the thermal discharge by increasing the exchange area of the heat accumulating matrix (which may be latent - PCM - or sensitive) as the thermal charging, due to the high convection inside the cylinder, is more intense than at the side of the internal environment of the compressor.
  • the heat accumulating matrix which may be latent - PCM - or sensitive
  • FIG 10 shows an eighth illustrative embodiment of the present invention, wherein the heat accumulating material is included in an enclosure or cylinder jacket 27 of the electric motor of the compressor (see figure 10 , where numeral 26 denotes the rotor and numeral 26 the stator.)
  • this cylinder jacket 27 is fitted by interference into the outer region of the stator 26, such as to reduce the thermal resistances inherent to this kind of assembly to a minimum.
  • the motor heats, and upon reaching a certain working temperature specified in the application of the heat accumulator, the latter would absorb the heat dissipated by the motor, causing it to work at lower temperature than it would without the presence of the heat accumulator.
  • the presence of the heat accumulator prevents the heat dissipated into this component to from escaping to the internal environment of the compressor, resulting in reduction of the cavity temperature and indirectly of energy losses due to overheating of gas.
  • Another advantage from this solution is to be able to ensure the reliability of compressors working at a critical temperature regime, such as, for example, compressors having low energy efficiency, thus reducing the use of steel and particularly copper (low-cost compressors).
  • dissipating fins were not included; however, such fins could be added within the inventive concept of the present invention.
  • FIGS 11a and 11b show a ninth illustrative embodiment of the present invention, wherein the heat accumulating material is applied to the suction tube 28, the discharge tube 29, or to both suction and discharge tubes 28, 29 (tubes).
  • the application of heat accumulators to the suction tube gives rise to at least two advantages.
  • the first is concerned with the overheating of the suction gas still before entering the compressor, due to the heating of this tube by the housing, which is at a higher temperature.
  • This flow of heat upon going through the tube, finds lower resistance on the suction gas, which exhibits a heat transfer coefficient much higher than the external side, since the latter is generally characterized as natural convection.
  • the addition of the heat accumulating material into an enclosure 30 around the suction tube 28 is intended to create a preferential passageway for the flow of heat coming from the housing, different from the suction gas. Accordingly, the addition of fins 31 can increase the exchange area for the heat accumulator.
  • Another advantage from this application lies in creating a barrier for the heat coming from the discharge tube 29, which is much hotter than the suction tube 28 and the housing itself.
  • the suction tube 28 and the discharge tube are very close to each other 29 (see, for example, the illustrated example embodiment). Accordingly, a thermal short-circuit should be expected, since there is a high temperature gradient between the suction and discharge gases.
  • the presence of this heat accumulating element also acts by creating a preferential passageway for the heat coming from this component.
  • this heat accumulator 32 is applied to the discharge tube 29, forming a passageway for the preferential heat other than the one that carries this heat energy towards the suction area.
  • the presence of fins 33 plays the role of facilitating this heat transference into the heat accumulating matrix.
  • Another advantage inherent to the application of the heat accumulator 32 to the discharge tube 29 is the temperature reduction of the discharge gas, since the heat dissipation for this accumulator is enhanced. As the discharge temperature is reduced, there may be indirect efficiency gains due to a reduced need of exchanging this heat on the condenser. As a consequence from this reduction on the heat to be exchanged on the condenser, it could have its size reduced (cost reduction) or, while maintaining the size of the condenser, the pressure and the saturation temperature therein is reduced, increasing the efficiency of the thermodynamic cycle.
  • the enclosure for the heat accumulator could be made from metal and/or plastic, wherein when it is made from metal, the latter could be welded to the housing and the tube. In the case of plastic, gluing would be the first feasible choice.
  • Figure 12 shows a tenth illustrative embodiment of the present invention, wherein the heat accumulating material is applied to the top 35 of the compressor housing.
  • a preferably metallic plate 36 is laid over the compressor cap, said components being joined by any suitable means (e.g., welding or gluing), ensuring the formation of a hermetic enclosure for housing the heat accumulating material 37.
  • the plate 36 may comprise fins 38 intended to increase the heat transfer area.
  • inventive concept underlying the present invention lies in taking advantage from the thermodynamics existing between the compressor and the refrigeration system in order to achieve a reduction on the internal compressor temperatures reliably and efficiently and, consequently, to increase the performance of the compressor.
  • This inventive concept is implemented by means of a refrigeration compressor comprising a heat accumulating material which acts as a thermal capacitor, so as to increase the thermal efficiency of the compressor.
  • the figures show embodiments in which the heat accumulating material (preferably, a PCM) is applied to an idle volume inside the compressor housing - whether in an enclosure specifically designed to that purpose, or in a space formed between components of the compressor, or even in enclosed spaces formed inside the components of the compressor, or a volume externally adjacent to the compressor housing.
  • the heat accumulating material preferably, a PCM
  • the present invention is not limited to the embodiments described herein.
  • the present invention rather than using a volume created between two plates, for example, could use an elastic material having a PCM therein (a rubber sheet), wherein said material could be attached to the compressor housing by means of glue or other adhesion means.
  • a PCM a rubber sheet
  • This variant would allow the PCM material to be changed over the time.
  • the heat accumulating material (preferably a PCM) could, for example, be used directly in the manufacturing of one of the compressor components or even in the compressor housing.
  • the fins provided by the described embodiments could be external, as shown in the figures, or internal, adjacent to the heat accumulating material, in order to facilitate the flow of heat along its structure.
  • the addition of fins allows to maximize the flow of heat along the material.
  • other solutions for maximizing the heat transfer along the heat accumulating material could also be used within the scope of the present invention, such as, for example, porous metallic matrices injected along with the heat accumulator.
  • PCM materials which could be used within the scope of the present invention are listed for informative purposes: models RT52 and RT65 available from Rubitherm Technologies GmbH, models Plus Ice - S58 and S72 (PCM solutions based on hydrated salt) and models Plus Ice A55, A62 and A70 (organic base PCM solutions) available from Change Material Products Limited, and models Climsel C58 and Climsel C70 available from Climator Sweden AB.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP10803207A 2009-11-10 2010-11-09 Refrigeration compressor Withdrawn EP2500567A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BRPI0904785-9A BRPI0904785A2 (pt) 2009-11-10 2009-11-10 compressor de refrigeraÇço
PCT/BR2010/000373 WO2011057373A1 (pt) 2009-11-10 2010-11-09 Compressor de refrigeração

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EP2500567A1 true EP2500567A1 (en) 2012-09-19

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EP10803207A Withdrawn EP2500567A1 (en) 2009-11-10 2010-11-09 Refrigeration compressor

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US (1) US20130045119A1 (pt)
EP (1) EP2500567A1 (pt)
KR (1) KR20120103605A (pt)
CN (1) CN102667157A (pt)
BR (1) BRPI0904785A2 (pt)
WO (1) WO2011057373A1 (pt)

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WO2014103320A1 (ja) * 2012-12-27 2014-07-03 パナソニック株式会社 密閉型圧縮機及びそれを備える冷凍装置
EP3123083A4 (en) * 2014-03-24 2018-01-10 The Coca-Cola Company Refrigeration system with phase change material heat exchanger

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WO2017006389A1 (ja) * 2015-07-03 2017-01-12 三菱電機株式会社 ヒートポンプ装置
KR20170011237A (ko) * 2015-07-22 2017-02-02 한국항공우주연구원 저온 펌프의 온도 제어 장치 및 방법
CN108895721B (zh) * 2018-07-26 2024-06-11 青岛海尔空调器有限总公司 用于t3工况的压缩机及包括该压缩机的空调器
KR102072153B1 (ko) * 2018-09-11 2020-01-31 엘지전자 주식회사 소형 압축기 및 이를 구비한 냉장고
CN109185099B (zh) * 2018-11-09 2024-04-19 广西玉柴机器股份有限公司 全水冷空气压缩机

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WO2011057373A1 (pt) 2011-05-19
KR20120103605A (ko) 2012-09-19
US20130045119A1 (en) 2013-02-21
CN102667157A (zh) 2012-09-12
BRPI0904785A2 (pt) 2013-07-30

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