EP3676544B1 - Wärmepumpe mit einer kühlvorrichtung zum kühlen eines leitraums und eines saugmunds - Google Patents

Wärmepumpe mit einer kühlvorrichtung zum kühlen eines leitraums und eines saugmunds Download PDF

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Publication number
EP3676544B1
EP3676544B1 EP18759919.6A EP18759919A EP3676544B1 EP 3676544 B1 EP3676544 B1 EP 3676544B1 EP 18759919 A EP18759919 A EP 18759919A EP 3676544 B1 EP3676544 B1 EP 3676544B1
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EP
European Patent Office
Prior art keywords
liquid
guide space
condenser
suction mouth
cooling
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Active
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EP18759919.6A
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German (de)
English (en)
French (fr)
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EP3676544A2 (de
Inventor
Oliver Kniffler
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Vertiv SRL
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Efficient Energy GmbH
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Publication of EP3676544A2 publication Critical patent/EP3676544A2/de
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    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/071—Compressor mounted in a housing in which a condenser is integrated
    • 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
    • F25B2500/09—Improving heat transfers

Definitions

  • FIGs 8A and 8B represent a heat pump as described in the European patent EP 2016349 B1 is described.
  • the heat pump initially includes an evaporator 10 for evaporating water as the working fluid in order to generate steam in a working-steam line 12 on the output side.
  • the evaporator includes an evaporating space (in Figure 8A not shown) and is designed to generate an evaporation pressure of less than 20 hPa in the evaporation space, so that the water evaporates at temperatures below 15 °C in the evaporation space.
  • the water is, for example, groundwater, brine circulating freely in the ground or in collector pipes, i.e. water with a certain salt content, river water, lake water or sea water.
  • All types of water can be used, i.e. calcareous water, calcareous water, salty water or salt-free water. This is because all types of water, i.e. all these "hydrogens", have the favorable water property, namely that water, which is also known as "R 718", has an enthalpy difference ratio that can be used for the heat pump process of 6, which corresponds to more than 2 times the typical usable enthalpy difference ratio of eg R134a.
  • the water vapor is fed through the suction line 12 to a compressor/condenser system 14 which has a turbomachine such as a centrifugal compressor, for example in the form of a turbo compressor, which in Figure 8A is denoted by 16.
  • the turbomachine is designed to compress the working steam to a steam pressure of at least greater than 25 hPa.
  • 25 hPa corresponds to a condensation temperature of around 22 °C, which can already be a sufficient heating flow temperature for underfloor heating, at least on relatively warm days.
  • pressures greater than 30 hPa can be generated with the turbomachine 16, with a pressure of 30 hPa having a condensation temperature of 24 °C, a pressure of 60 hPa having a condensation temperature of 36 °C, and a pressure of 100 hPa corresponds to a condensation temperature of 45 °C.
  • Underfloor heating is designed to be able to heat sufficiently with a flow temperature of 45 °C even on very cold days.
  • the turbomachine is coupled to a condenser 18 which is designed to liquefy the compressed working vapor.
  • a condenser 18 which is designed to liquefy the compressed working vapor.
  • the energy contained in the working vapor is supplied to the liquefier 18 in order to then be supplied to a heating system via the flow 20a.
  • the working fluid flows back into the condenser via the return line 20b.
  • Figure 8B shows a table to illustrate different pressures and the evaporation temperatures assigned to these pressures, from which it follows that very low pressures in the evaporator are to be selected, particularly for water as the working medium.
  • the DE 4431887 A1 discloses a heat pump system with a lightweight, large volume, high efficiency centrifugal compressor. Vapor exiting a second stage compressor has a saturation temperature that exceeds ambient temperature or that of any available cooling water, thereby allowing heat removal.
  • the compressed vapor is transferred from the second-stage compressor into the condenser unit, which consists of a packed bed provided within a cooling water sprayer at a top supplied by a water circulating pump.
  • the compressed water vapor rises in the condenser through the packed bed, where it comes into direct countercurrent contact with the cooling water flowing downwards.
  • the steam condenses and the latent heat of condensation absorbed by the cooling water is expelled to atmosphere via the condensate and cooling water, which are removed from the system together.
  • the condenser is continuously flushed with non-condensable gases via a pipeline using a vacuum pump.
  • the WO 2014072239 A1 discloses a condenser having a condensing zone for condensing vapor to be condensed in a working liquid.
  • the condensation zone is designed as a volume zone and has a lateral boundary between the upper end of the condensation zone and the lower end.
  • the Condenser a steam introduction zone, which extends along the lateral end of the condensation zone and is designed to introduce steam to be condensed laterally over the lateral boundary into the condensation zone.
  • the actual condensation is made into a volume condensation, because the vapor to be liquefied is introduced not only frontally from one side into a condensation volume or into the condensation zone, but laterally and preferably from all sides.
  • a general problem with heat pumps is the fact that moving parts, and particularly fast-moving parts, have to be cooled.
  • the compressor motor in particular and the motor shaft in particular are problematic here.
  • shaft temperatures can reach values that are problematic because they lead to the destruction of the components can.
  • superheated working medium vapor must first reduce its overheating in order to then be able to condense particularly well and efficiently.
  • efficient condensation is particularly important in order to achieve a heat pump that, on the one hand, creates high performance values for heating or cooling, depending on the use of the heat pump.
  • a heat pump should occupy as small a space as possible, which entails limitations for the dimensioning of the condenser. The smaller the condenser is dimensioned, the smaller the "footprint" or overall volume or space that the heat pump occupies. Therefore it is of great importance to achieve highly efficient condensing in the condenser of a heat pump. Only then can a heat pump with good efficiency on the one hand and not too large a volume or footprint on the other hand be created.
  • the U.S. 2002/106278 A1 discloses a turbo compressor. It comprises a housing provided with an inlet port and an outlet port; a rotary shaft operated by a drive mechanism; an impeller provided integrally with the rotary shaft; and a diffuser portion composed of a pair of a first wall portion and a second wall portion disposed on the outer peripheral side of the impeller to serve as a fluid passage for a refrigerant to be blown.
  • the refrigerant is sucked through the inlet port by the action of the impeller, which is rotated together with the rotary shaft and driven by a motor to be compressed and discharged through the outlet port.
  • the diffuser portion (46) is constructed so that the width dimension in the axial direction of the discharge port is made larger than the width dimension of the intake port.
  • the U.S. 2002/106278 A1 also discloses a cooling device for cooling an outside of the guide space, which is arranged in order to guide the refrigerant conveyed by the impeller to a condenser in its interior.
  • the U.S. 2011/107787 A1 discloses a heat pump having an evaporator and a condenser and a gas section extending between the evaporator and the condenser.
  • the condenser (500) is arranged above the evaporator (200) in one operating mode.
  • the U.S. 2011/107787 A1 discloses a heat pump having an evaporator and a condenser and a gas section extending between the evaporator and the condenser.
  • the condenser (500) is arranged above the evaporator (200) in one operating mode.
  • 2011/107787 A1 also discloses a cooling device for cooling an outside of the guide space, which is arranged to conduct the refrigerant conveyed by the radial impeller to the condenser inside, and for cooling an outside of the suction mouth which is arranged to convey the refrigerant evaporated by the evaporator to the inside To conduct radial impeller, and thus discloses a heat pump according to the preamble of independent claim 1.
  • the object of the present invention is to create a more efficient heat pump.
  • the present invention is based on the knowledge that, in order to avoid a reduced condenser efficiency due to overheated working medium vapor, the guide space and the suction mouth are cooled with a liquid. In this way, the temperature of the guide space and the suction mouth is brought and maintained as close as possible to the saturated steam temperature of the pressure prevailing in the condenser. This becomes energy/heat coupled from the steam flow via the material or the wall of the suction port and the guide space. The one that is brought up to the suction mouth and the control room Water, if water is used as the working liquid, which is the case in preferred embodiments, then begins to boil and thus releases the energy again.
  • control space and the suction port are thus kept very close to the saturated steam temperature of the steam pressure, which is first sucked in by the radial impeller via the suction port and from there is fed into the control space.
  • the working vapor is then compressed to its intended liquefier or condenser pressure.
  • the cooling of the control space and the suction mouth prevents the working medium vapor from being overheated too much. This means that when the working medium vapor enters the condenser, it no longer has to reduce the overheating in order to be able to condense easily. Instead, the working medium vapor can condense directly in the condenser without any further loss of time, volume or travel distance.
  • an efficient condenser can be achieved even if the condenser volume is made smaller, compared to an embodiment in which adequate plenum and suction mouth cooling would not have been employed.
  • the conducting space is formed from a material with good thermal conductivity.
  • the guide space thus extracts energy from the steam flowing past it and transfers it directly to the cooling water which flows around the guide space and the suction mouth. In this way, the guide space is kept even better at the saturated steam temperature of the steam pressure.
  • liquefaction in the guide space is avoided due to the remaining thermal resistance of the material of the guide space, since the overheating is not reduced completely, but only to a large extent. However, this residual overheating ensures that condensation does not already take place in the control room, but only then in the condenser, where it then takes place particularly efficiently.
  • the cooling liquid for the control chamber is conducted beforehand through an engine ball bearing and/or through an open engine cooling system that is also preferably used. Due to the open engine cooling, the coolant cools down again to saturated steam temperature through partial evaporation. In the cascade of ball bearing cooling and motor cooling, the cooling liquid in the motor cooling already releases the energy absorbed by the ball bearing cooling. This means that an optimally tempered liquid medium is available for open duct cooling.
  • the upper part of the outside of the duct is first filled with liquid.
  • the working liquid will then simply overflow, which is unproblematic and even desirable, because the working liquid then simply runs into the condenser, into which working liquid is introduced anyway in preferred embodiments of the present invention in the form of a "shower".
  • the cooling liquid is also conducted from the upper guide space cooling system, ie from the cooling of the upper side of the guide space, into an additional lower guide space and suction mouth cooling system. At the end of the control room there is an open area with an overflow. The working fluid constantly cools itself down to the saturation temperature by evaporation.
  • the working liquid also overflows and flows easily into the condenser volume, in order to be further processed there.
  • the working liquid can also be a working liquid that is not the working liquid of the heat pump, especially since the working liquid does not necessarily have to come into contact with the compressed working vapor, depending on the implementation.
  • the present invention is also advantageous in that the guide chamber cooling and the suction mouth cooling, which typically occupy relatively large surfaces in a heat pump, which are arranged close to the compressor, thermal component loads are further reduced. Due to the liquid cooling used, which preferably takes place at the pressure level prevailing in the condenser, highly efficient evaporative cooling is achieved. This evaporative cooling allows the entire compressor to be kept close to the saturated steam temperature. In preferred exemplary embodiments, engine losses, bearing losses and overheating during compression are essentially reduced via the evaporation in order to achieve not only a highly efficient heat pump, but also a heat pump that is safe and stable in operation.
  • the heat pump includes special convective wave cooling.
  • This heat pump has a condenser with a condenser housing, a compressor motor attached to the condenser housing and having a rotor and a stator, the rotor having a motor shaft on which is attached a radial impeller extending into an evaporator zone, and a plenum , which is designed to receive compressed steam by the radial impeller and to guide it into the condenser.
  • this heat pump has a motor housing which encloses the compressor motor and is preferably designed to hold a pressure at least equal to the pressure in the condenser. However, a pressure that is greater than the pressure behind the radial impeller is also sufficient.
  • this pressure adjusts itself to a pressure which is midway between the condenser pressure and the evaporator pressure.
  • a steam supply is provided in the motor housing for supplying steam in the motor housing to a motor gap between the stator and the motor shaft.
  • the motor is designed such that a further gap extends from the motor gap between the stator and the motor shaft along the radial wheel to the guide space.
  • This pressure which is equal to the mean pressure from the condenser and the evaporator, exists due to the fact that the impeller, when compressing the vapor from the evaporator, has a high pressure area in front of the impeller and a low pressure or negative pressure area behind it radial wheel generated.
  • the area with high pressure in front of the radial impeller is still smaller than the high pressure in the condenser and the low pressure "behind" the radial impeller is still smaller than the high pressure at the outlet of the radial impeller.
  • the high condenser pressure only exists at the outlet of the guide chamber.
  • This pressure gradient which is "coupled” to the engine gap, ensures that working steam is drawn from the engine housing via the steam supply along the engine gap and the further gap into the condenser.
  • This vapor is at or above the temperature level of the condenser working fluid.
  • this is precisely an advantage because it avoids all condensation problems inside the motor and in particular inside the motor shaft, which would promote corrosion etc.
  • Adequate convective wave cooling is thus achieved. This prevents excessive temperatures in the motor shaft and the associated signs of wear. In addition, this effectively prevents condensation from occurring in the motor, for example when the heat pump is at a standstill. This also effectively eliminates any operational safety problems and corrosion problems that would be associated with such condensation. According to the aspect of convective wave cooling, the example leads to a significantly more reliable heat pump.
  • the heat pump in another aspect relating to a motor-cooled heat pump, includes a condenser having a condenser housing, a compressor motor attached to the condenser housing and having a rotor and a stator.
  • the rotor includes a motor shaft to which a compressor wheel is attached for compressing working fluid vapor.
  • the compressor motor has a motor wall.
  • the heat pump includes a motor housing that surrounds the compressor motor and is preferably configured to maintain a pressure at least equal to the pressure in the condenser and that has a working fluid inlet to direct liquid working fluid from the condenser to the motor wall for cooling the motor .
  • the pressure in the motor housing can also be lower here, since heat is dissipated from the motor housing by boiling or evaporation.
  • the heat energy at the engine wall is carried away from the engine wall primarily by the steam, which heated steam is then discharged, such as into the condenser.
  • the steam from the engine cooling can also be brought into the evaporator or to the outside.
  • water cooling in which an engine is cooled by water flowing past, the cooling in this aspect of the invention takes place by evaporation, so that the heat energy to be transported away is removed by the vapor removal provided.
  • An advantage is that less liquid is needed for cooling and the vapor can simply be channeled away, e.g. B. automatically into the condenser, in which the vapor then condenses again and the heat output of the engine is thus released to the condenser liquid.
  • the motor housing is therefore designed to form a vapor space when the heat pump is in operation, in which space the working medium located due to nucleate boiling or evaporation is located.
  • the motor housing is also designed to discharge the vapor from the vapor space in the motor housing through a vapor vent. This discharge preferably takes place into the condenser, so that the vapor discharge is achieved through a gas-permeable connection between the condenser and the motor housing.
  • the motor housing is preferably also designed to keep a maximum level of liquid working medium in the motor housing when the heat pump is in operation, and also to form a vapor space above the maximum level.
  • the motor housing is also configured to direct working fluid into the condenser above the maximum level. This design allows cooling by steam generation very robust to keep as the level of working liquid always ensures there is enough working liquid at the motor wall for nucleate boiling.
  • working liquid can also be sprayed onto the engine wall. The sprayed liquid is then dosed in such a way that it vaporizes on contact with the engine wall and thus achieves the cooling capacity for the engine.
  • the engine is thus effectively cooled on its engine wall with liquid working medium.
  • this liquid working medium is not the cold working medium from the evaporator, but the warm working medium from the condenser.
  • Using the warm working fluid from the condenser still provides adequate engine cooling.
  • the motor is not cooled too much and in particular is not cooled down to the point that it is the coldest part in the condenser or on the condenser housing. This would lead to the working medium vapor condensing on the outside of the motor housing when the motor is at a standstill, for example, but also during operation, which would lead to corrosion and other problems.
  • it is ensured that the motor is well cooled, but at the same time is always the warmest part of the heat pump, to the extent that condensation, which always takes place at the coldest "end", does not take place precisely on the compressor motor.
  • the liquid working medium in the motor housing is kept at almost the same pressure as the condenser. This results in the working fluid that cools the engine being close to its boiling point since this working fluid is condenser working fluid and is at a similar temperature to that in the condenser. If the engine wall is now heated due to friction due to engine operation, the thermal energy is transferred to the liquid working medium. Due to the fact that the liquid working medium is close to the boiling point, nucleate boiling now starts in the motor casing in the liquid working medium filling the motor casing to the maximum level.
  • This nucleate boiling enables extremely efficient cooling due to the very strong mixing of the volume of liquid working medium in the motor housing.
  • This boiling-assisted cooling can also be significantly assisted by a preferably provided convection element, so that in the end a very efficient engine cooling with a relatively small volume or no stagnant at all Volume of liquid working medium, which also does not have to be further controlled because it is self-controlling, is reached. Efficient motor cooling is thus achieved with little technical effort, which in turn makes a significant contribution to the operational reliability of the heat pump.
  • the heat pump also includes a condenser for condensing evaporated working fluid in a condenser chamber 104, which is delimited by a condenser base 106.
  • a condenser for condensing evaporated working fluid in a condenser chamber 104, which is delimited by a condenser base 106.
  • the evaporator space 102 is at least partially surrounded by the condenser space 104 .
  • the evaporator chamber 102 is separated from the condenser chamber 104 by the condenser base 106 .
  • the condenser base is connected to an evaporator base 108 to define the evaporator space 102 .
  • a compressor 110 is provided above the evaporator space 102 or elsewhere, which is in 1 is not explained in more detail, but which is designed in principle to compress evaporated working liquid and to conduct it as compressed vapor 112 into the condenser space 104 .
  • the condenser space is also delimited towards the outside by a condenser wall 114 .
  • the condenser wall 114 is fastened to the evaporator base 108 .
  • the dimensioning of the condenser base 106 in the area that forms the interface to the evaporator base 108 is such that the condenser base in 1 shown embodiment is completely surrounded by the condenser chamber wall 114. This means that the condenser room, as shown in 1 as shown, extends to the bottom of the evaporator, and at the same time the evaporator space extends very far upwards, typically almost through almost the entire condenser space 104 .
  • This "interlocked" or interlocking arrangement of condenser and evaporator which is characterized by the fact that the condenser base is connected to the evaporator base, provides a particularly high heat pump efficiency and therefore allows a particularly compact heat pump design.
  • the dimensioning of the heat pump for example in a cylindrical shape, is such that the condenser wall 114 represents a cylinder with a diameter between 30 and 90 cm and a height between 40 and 100 cm.
  • the dimensioning can be selected depending on the required performance class of the heat pump, but preferably takes place in the dimensions mentioned.
  • the operating direction of the heat pump is as shown in 1 is shown.
  • the evaporator bottom defines the lower section of the heat pump, but apart from connection lines to other heat pumps or to corresponding pump units.
  • the vapor generated in the evaporator space rises and is deflected by the motor and fed into the condenser space from the top down, and the condenser liquid is passed up from the bottom and then fed into the condenser space from the top and then flows from top to bottom in the condenser space, such as through individual droplets or through small streams of liquid, to react with the preferably cross-fed compressed vapor for purposes of condensation.
  • This "interleaved" arrangement to the effect that the evaporator is arranged almost completely or even completely inside the condenser, enables a very efficient design of the heat pump with optimum space utilization. Since the condenser space extends to the bottom of the evaporator, the condenser space is formed within the entire "height" of the heat pump, or at least within a substantial portion of the heat pump. At the same time, however, the evaporator space is as large as possible, because it also extends almost over the entire Height of the heat pump extends.
  • the interlocking arrangement in contrast to an arrangement in which the evaporator is arranged below the condenser, means that the space is used optimally.
  • each functional space is given the large volume where this functional space also requires the large volume.
  • the evaporator room has the large volume at the bottom while the condenser room has the large volume at the top. Nevertheless, the corresponding small volume that remains for the respective functional space where the other functional space has the large volume contributes to an increase in efficiency compared to a heat pump in which the two functional elements are arranged one above the other, as is the case, for example, in WO 2014072239 A1 the case is.
  • the compressor is arranged on the upper side of the condenser space in such a way that the compressed vapor is deflected by the compressor on the one hand and at the same time fed into an edge gap of the condenser space. Condensation with a particularly high efficiency is thus achieved because a cross-flow direction of the vapor to a condensation liquid flowing down is achieved. This cross-flow condensation is particularly effective in the upper area, where the evaporator space is large, and does not require a particularly large area in the lower area, where the condenser space is small in favor of the evaporator space, in order to still allow condensation of vapor particles that have penetrated to this area allow.
  • An evaporator base which is connected to the condenser base, is preferably designed in such a way that it has the condenser inlet and outlet and the evaporator inlet and outlet absorbs itself, with certain bushings for sensors in the evaporator or in the condenser also being able to be present. This means that there is no need to feed through lines for the condenser inlet and outlet through the evaporator, which is almost under vacuum. This makes the entire heat pump less prone to failure as any passage through the evaporator would present an opportunity for a leak.
  • the condenser base is provided with a respective recess at the points where the condenser inlets and outlets are, to the effect that no condenser inlets and outlets run in the evaporator space defined by the condenser base.
  • the condenser space is delimited by a condenser wall, which can also be attached to the evaporator bottom.
  • the evaporator base thus has an interface for both the condenser wall and the condenser base and also has all the liquid feeds for both the evaporator and the condenser.
  • the evaporator bottom is designed to have fittings for the individual feeds that have a cross section that differs from a cross section of the opening on the other side of the evaporator bottom.
  • the shape of the individual connection pieces is then designed in such a way that the shape or cross-sectional shape changes over the length of the connection piece, but the pipe diameter, which plays a role in the flow rate, is almost the same with a tolerance of ⁇ 10%. This prevents the water flowing through the connection piece from starting to cavitate. Due to the good flow conditions obtained through the shaping of the connecting piece, it is thus ensured that the corresponding pipes/lines can be made as short as possible, which in turn contributes to a compact design of the entire heat pump.
  • the condenser feed is divided into a two- or multi-part stream almost in the form of "glasses". With this, it is possible to feed the condenser liquid in the condenser at its upper portion at two or more points at the same time. This achieves a strong and at the same time particularly uniform condenser flow from top to bottom, which enables highly efficient condensation of the vapor that is also introduced into the condenser from above to be achieved.
  • a further, smaller-sized supply line in the evaporator bottom for condenser water can also be provided in order to connect a hose to it, which supplies cooling liquid to the compressor motor of the heat pump, with the cold liquid fed to the evaporator not being used for cooling, but the warmer liquid fed to the condenser Liquid that is still cool enough, however, in typical operating situations to cool the heat pump motor.
  • the evaporator bottom is characterized by having a combination functionality. On the one hand, it ensures that no condenser feed lines have to be routed through the evaporator, which is under very low pressure. On the other hand, it represents an interface to the outside, which preferably has a circular shape, since as much evaporator surface area as possible remains with a circular shape. All incoming and outgoing lines lead through one evaporator floor and run from there into either the evaporator room or the condenser room. In particular, manufacturing the evaporator base from plastic injection molding is particularly advantageous because the advantageous, relatively complicated shapes of the inlet/outlet connections can be easily and inexpensively implemented in plastic injection molding. On the other hand, due to the design of the evaporator bottom as an easily accessible workpiece, it is easily possible to produce the evaporator bottom with sufficient structural stability so that it can easily withstand the low evaporator pressure in particular.
  • FIG. 2 shows a heat pump according to the present invention, either, which is preferred, in conjunction with the respect of 1 described interlaced arrangement is implemented, which, however, can alternatively be implemented in a different than the interlaced arrangement as shown schematically in 2 is shown.
  • the heat pump includes an evaporator 90 for evaporating working fluid.
  • the heat pump includes a condenser or condenser 114 for condensing vaporized and compressed working fluid.
  • the heat pump further includes a centrifugal impeller compressor motor 110, 304 coupled to a suction port 92 to convey a working vapor vaporized in the evaporator 90 through the suction port.
  • the heat pump includes a Guide chamber 302, which is arranged in order to guide a working steam conveyed by the radial impeller into the condenser 114.
  • the working steam evaporated in the evaporator 90 is indicated schematically at 314
  • the working steam 112 conveyed into the guide space, which arrives compressed in the condenser 114 is shown schematically at 112 .
  • the heat pump includes a cooling device 420 which is designed to cool the guide space 302 and the suction mouth 92 with a liquid.
  • the cooling device 420 comprises, not according to the invention, a liquid line 421 to the suction mouth 92 and a liquid line 422 to the guide space 302.
  • a single liquid line is present to sequentially fill the guide space and the suction mouth with cooling liquid take care of.
  • the cooling device is also designed to direct the liquid via lines 421, 422 or, according to the invention, sequentially via a line to an outside of the guide space 302 or the suction mouth 92, the outside not being in contact with the working vapor 314, 112 , while the inside of the guide space 302 or the suction mouth 92 is in contact with this working vapor 314 or 112, respectively.
  • Water is preferably used as the working liquid, and in particular condenser water, ie working liquid which is the same as the working liquid of the heat pump.
  • the liquid vapor is thus the same vapor as the working medium vapor 314, 112, so that an open concept is obtained.
  • a closed concept with cooling liquid can also be used, to the effect that the cooling liquid is treated separately from the working liquid.
  • the cooling device 420 would then be designed to also have a return flow of the cooling liquid, with the return heated cooling liquid also having to be cooled separately in order to then supply a cooled cooling liquid again to the guide space or the suction mouth.
  • open plenum/suction port cooling is preferred.
  • FIG. 1 shows a heat pump with a condenser with a condenser housing 114 comprising a condenser space 104.
  • FIG. Also attached is the compressor motor, which is represented schematically by the stator 308 in 4 is shown.
  • This compressor motor is on in 3 attached to the condenser housing 114 in a manner not shown and includes the stator and a rotor 306, the rotor 306 being a motor shaft on which is mounted a radial impeller 304 extending into an evaporator zone.
  • the heat pump includes a guide chamber 302 which is designed to receive the steam compressed by the radial impeller and to guide it into the condenser, as is shown schematically at 112 .
  • the motor further includes a motor housing 300 which encloses the compressor motor and is preferably adapted to hold a pressure at least equal to the pressure in the condenser.
  • the motor housing is designed to hold a pressure that is higher than an average pressure from the evaporator and the condenser, or higher than the pressure in the further gap 313 between the radial wheel and the guide space 302, or greater or is equal to the pressure in the condenser.
  • the motor housing is designed in such a way that there is a pressure drop from the motor housing along the motor shaft in the direction of the guide chamber, through which the working steam is drawn past the motor shaft through the motor gap and the further gap in order to cool the shaft.
  • a vapor supply 310 is formed to supply vapor in the motor housing 300 to a motor gap 311 existing between the stator 308 and the shaft 306 .
  • the motor also includes a further gap 313 which extends from the motor gap 311 along the radial wheel to the guide space 302 .
  • This vapor flow takes working vapor from the motor housing past the motor shaft into the condenser.
  • This steam flow provides for the convective wave cooling of the motor shaft through the motor gap 311 and the further gap 313, which adjoins the motor gap 311.
  • the radial impeller thus sucks steam out downwards, past the motor shaft.
  • This steam is via the steam supply, typically are implemented as specially designed bores drawn into the motor gap.
  • convective shaft cooling on the one hand and motor cooling on the other hand are also used separately from one another.
  • Motor cooling without special, separate convective shaft cooling already leads to significantly increased operational reliability.
  • convective motor shaft cooling without the additional motor cooling leads to increased operational reliability of the heat pump.
  • the two aspects can, however, as explained below in 3 is shown, can be connected to one another in a particularly favorable manner in order to implement both the convective shaft cooling and the motor cooling with a particularly advantageous construction of the motor housing and the compressor motor, which can additionally be supplemented in a further preferred exemplary embodiment either individually or jointly by a special ball bearing cooling system.
  • FIG. 3 shows an embodiment with combined use of convective shaft cooling and engine cooling, wherein in the in 3 shown embodiment, the evaporator zone is shown at 102 .
  • the evaporator zone is separated from the condenser zone, ie from the condenser area 104 , by the condenser base 106 .
  • Working vapor shown schematically at 314, is drawn in by the rotating radial impeller 304, shown schematically and in section, and "forced" into conduit 302.
  • the route 302 is at the in 3
  • the embodiment shown is designed in such a way that its cross-section increases slightly towards the outside, so that the kinetic energy still present in the working steam can be converted into pressure without the flow detaching from the wall and losses occurring as a result of turbulence.
  • FIG. 3 also shows the vapor supply openings 320, which are located in a schematically illustrated engine wall 309 in 3 are executed.
  • This motor wall 309 has at the in 3
  • the exemplary embodiment shown has holes for the steam supply openings 320 in the upper area, although these holes can be made at any desired location at which steam can penetrate into the motor gap 311 and thus also into the further motor gap 313.
  • the resulting steam flow 310 leads to the desired effect of convective wave cooling.
  • the exemplary embodiment shown also includes a working fluid inlet 330 for implementing the engine cooling, which is designed to carry liquid working fluid from the condenser to the engine wall for engine cooling.
  • the motor housing is designed to maintain a maximum liquid level 322 of liquid working medium when the heat pump is in operation.
  • the motor housing 300 is also designed to form a vapor space 323 above the maximum level.
  • the motor housing has provision for directing liquid working medium into the condenser 104 above the maximum level. This version is used in the in 3 shown embodiment by a z. B. shallow channel-shaped weir 324 forming the vapor discharge and is located somewhere in the upper condenser wall and has a length that defines the maximum level 322.
  • the overflow also occurs with the in 3 shown passive arrangement, which can alternatively be a tube with a corresponding length, for example, a pressure equalization between the motor housing and in particular the vapor space 323 of the motor housing and the condenser interior 104 ago.
  • the pressure in the vapor space 323 of the motor housing is therefore always almost the same or at most slightly higher than the pressure in the condenser due to a pressure loss along the overflow.
  • the boiling point of the liquid 328 in the motor housing will be similar to the boiling point in the condenser housing.
  • heating of the motor wall 309 due to power loss generated in the motor leads to nucleate boiling taking place in the liquid volume 328, which will be explained later.
  • FIG. 3 also shows various seals in schematic form at reference number 326 and at similar locations between the motor housing and the condenser housing on the one hand or else between the motor wall 309 and the condenser housing 114 on the other hand. These seals are intended to symbolize that there should be a liquid and pressure-tight connection here.
  • a separate space is defined by the motor housing, but it represents nearly the same pressure area as the capacitor. Due to the heating of the motor and the energy released as a result at the motor wall 309, this supports nucleate boiling in the liquid volume 328, which in turn results in a particularly efficient distribution of the working medium in the volume 328 and thus particularly good cooling with a small volume of cooling liquid. Furthermore, it is ensured that cooling is carried out with the working medium that is at the most favorable temperature, namely the warmest temperature in the heat pump. This ensures that all condensation problems, which always occur on cold surfaces, are ruled out both for the motor wall and for the motor shaft and the areas in the motor gap 311 and the further gap 313.
  • the working medium vapor 310 used for the convective shaft cooling is vapor that is otherwise in the vapor space 323 of the motor housing. Like the liquid 328, this vapor also has the optimal (warm) temperature. Furthermore, the overflow 324 ensures that the pressure in the area 323 cannot rise above the condenser pressure due to the nucleate boiling caused by the motor cooling or the motor wall 309 . Furthermore, the heat energy due to the engine cooling is removed by the vapor discharge. This means that convective wave cooling will always work in the same way. If the pressure were to increase too much, too much working medium vapor could be pressed through the motor gap 311 and the further gap 313 .
  • the steam delivery bores 320 will typically be formed in an array, which may be regular or irregular.
  • the individual bores are no larger than 5 mm in diameter and can be as small as 1 mm.
  • FIG. 3 also shows the liquid lines 421 and 422 to the guide chamber 302 and to the suction mouth 92, via which the radial impeller 304 draws in vapor from the evaporator 102 and discharges it into the guide chamber 302.
  • the schematic ducts 421, 422 are designed to lead the liquid directly onto the surface of the respective elements. Like it still referring to 10 or. 11 shown, these lines can also be implemented in a single line, such that a sequential liquid supply the top of the plenum 302 (in 10 , not according to the invention), the suction mouth and the underside of the duct 302 (in Fig.11 , according to the invention) takes place.
  • conduits 422 may be implemented as channels that are rigid or as flexible conduits such as tubing members.
  • Figure 4a 12 shows a plan view of the duct 302 of FIG 3 or to the control room 302 of 10 or from 11 .
  • the guide chamber 302 includes an opening 374 for receiving the motor axle in a plan view from above, the axle extending from the motor into the guide chamber through this opening 374 in order to carry the radial wheel 304 there, which is also rotated by rotation of the motor axle is transferred.
  • the guide space includes a recessed area 372, which is designed for liquid accumulation and in 11 is shown in cross section.
  • the upper end of the guide space 302, as is shown, for example, in 3 is shown, provided with an upstanding edge, so that in the recessed area that extends over the entire guide space, liquid can accumulate and thus to a certain extent liquid "stands", the z. B. has been supplied via a liquid supply line 422, which is in 11 for example, as the through hole 372 from the engine compartment, and which is then continued via a flow area 376 over which the liquid then flows into the recessed area 372 .
  • the recessed area has a discharge line 373 or a connection area 373, to which a hose-like discharge line 378 is then connected, which is also in 11 is shown.
  • FIG. 14 shows a bottom view of the suction mouth 92 and duct 302 combination element.
  • the suction mouth opening is in the middle of FIG Figure 4b shown.
  • Adjacent to the suction mouth opening is the bottom 380 of a cooling channel 379 (in 11 shown), into the cooling liquid via the discharge line 378, which is in 11 is shown is fed. Due to the height difference of the reservoir in the depressed area 372, the cooling liquid in the cooling channel flows past the outside of the suction mouth 92 and also the lower outside of the guide space 302.
  • the end of the lower guide space 381 is dotted in Figure 4b shown. This is to clarify that this line is not visible in the bottom view because it is obscured by the lower end 382 of the cooling duct.
  • line 381 and line 382 in Figure 4b formed the spill-board route which has an open area of liquid that protrudes directly into the vapor channel and that is covered at the top by the upper outside of the duct 302.
  • the ledge 382 protrudes enough to form a certain level. Excess working liquid then simply runs down this board into the condenser or into the condenser volume.
  • Figures 4a and 4b are not drawn to scale, but merely show a schematic of a preferred embodiment of the guide chamber 302, whereby in this application, depending on the explanation, the guide chamber means the guide chamber in the guide chamber housing or the housing of the guide chamber itself, i.e. the housing surrounding the steam duct, as in Figure 4a as upper control room housing and in Figure 4b is shown as the lower control chamber housing.
  • FIG. 6 shows a condenser from the prior art, the condenser in 6 a vapor introduction zone 102 extending completely around the condensation zone 100.
  • a part of a condenser is shown, which has a condenser bottom 200 .
  • a condenser housing section 202 is arranged on the condenser floor, which due to the illustration in 6 is drawn transparent, which does not necessarily have to be transparent in nature, but can be made of plastic, die-cast aluminum or something similar, for example.
  • the lateral housing part 202 rests on a sealing rubber 201 in order to achieve a good seal with the floor 200.
  • the condenser comprises a liquid outlet 203 and a liquid inlet 204 as well as a vapor feed 205 which is arranged centrally in the condenser and extends from bottom to top in 6 tapered.
  • 6 represents the actually desired installation direction of a heat pump and a condenser of this heat pump, with this installation direction in 6 the evaporator of a heat pump is located below the condenser.
  • the condensation zone 100 is bounded on the outside by a basket-like boundary object 207 which, like the outer housing part 202, is shown as transparent and is normally constructed like a basket.
  • a lattice 209 is arranged, which is formed around fillers, which in 6 are not shown to wear. like it out 6
  • the basket 207 only extends downwards to a certain point.
  • the basket 207 is vapor-permeable, to hold packing, such as so-called pall rings.
  • These packings are introduced into the condensation zone, only inside the basket 207, but not in the steam introduction zone 102. However, the packings are also filled in so high outside of the basket 207 that the height of the packings either reaches the lower limit of the basket 207 or slightly above.
  • the liquefier of 6 includes a working liquid feeder, which is in particular through the working liquid feed 204, which, as in 6 is shown wound around the steam supply in the form of an ascending coil, is formed by a liquid transport area 210 and by a liquid distributor element 212, which is preferably designed as a perforated plate.
  • the working liquid feeder is thus designed to feed the working liquid into the condensation zone.
  • a steam feeder is also provided, which, as shown in 6 is shown, preferably composed of the funnel-shaped tapering feed area 205 and the upper vapor guide area 213.
  • An impeller of a radial compressor is preferably used in the steam line area 213 and the radial compression means that steam is sucked in from the bottom upwards through the inlet 205 and is then already deflected to a certain extent 90 degrees outwards due to the radial compression by the radial impeller, i.e. from a bottom-up flow to a center-out flow in 6 regarding element 213.
  • a further deflector which deflects the steam, which has already been deflected outwards, again by 90 degrees in order to then direct it from above into the gap 215, which to a certain extent represents the beginning of the steam introduction zone, which extends laterally around the condensation zone.
  • the vapor feeder is therefore preferably ring-shaped and provided with an annular gap for feeding in the vapor to be condensed, the working liquid feed being formed within the annular gap.
  • Fig. 12 shows a view of the "top area" of the condenser of Fig 6 from underneath.
  • the perforated plate 212 which acts as a liquid distribution element, is shown schematically from below.
  • the steam inlet gap 215 is drawn schematically and it appears from FIG 7 that the steam inlet gap is only ring-shaped, such that in the condensation zone no steam to be condensed is fed in directly from above or directly from below, but only from the side.
  • only liquid flows through the holes in the distributor plate 212, but no steam.
  • the vapor is first "sucked in” laterally into the condensation zone, specifically because of the liquid that has passed through the perforated plate 212 .
  • the liquid distribution plate can be made of metal, plastic or a similar material and can be designed with different hole patterns. Further, it will, as in 6 as shown, it is preferable to provide a lateral restriction for liquid flowing out of the element 210, this lateral restriction being denoted by 217. This ensures that liquid, which exits element 210 with a twist due to the curved feed 204 and is distributed from the inside outwards on the liquid distributor, does not splash over the edge into the vapor introduction zone, unless the liquid has already passed through the Holes of the liquid distribution plate has dripped and condensed with steam.
  • figure 5 shows a complete heat pump in a sectional view, which includes both the evaporator base 108 and the condenser base 106 .
  • the condenser bottom 106 has a tapering cross section from an inlet for the working liquid to be evaporated to a suction opening 115, which is coupled to the compressor or motor 110, where the preferably used radial impeller of the motor sucks off the vapor generated in the evaporator chamber 102 .
  • figure 5 shows a cross section through the entire heat pump.
  • a droplet separator 404 is arranged inside the condenser base.
  • This eliminator comprises individual vanes 405. In order to keep the eliminator in place, these vanes are inserted in corresponding grooves 406, which are figure 5 are shown. These grooves are arranged in the condenser bottom in an area directed towards the evaporator bottom, in the inside of the evaporator bottom.
  • the condenser base also has various guide features that can be designed as rods or tongues to hold hoses that are provided for condenser water guidance, for example, which are therefore attached to corresponding sections and couple the feed points of the condenser water supply.
  • this condenser water supply 402 can be designed as shown in FIGS 6 and 7 as shown at reference numerals 102, 207-250.
  • the condenser preferably has a condenser liquid distribution arrangement which has two or more feed points. A first entry point is therefore connected to a first section of a condenser inlet. A second feed point is connected to a second section of the condenser inlet. If there are more feed points for the condenser liquid distribution system, the condenser feed will be divided into further sections.
  • the upper area of the heat pump from figure 5 can therefore be used in the same way as the upper area in 6 be designed to the effect that the condenser water supply through the perforated plate of 6 and 7 takes place, so that condenser water 408 trickling downwards is obtained, into which the working vapor 112 is preferably introduced laterally, so that the cross-flow condensation, which allows a particularly high efficiency, can be obtained.
  • the condensation zone can be provided with an only optional filling, in which the edge 207, which is also denoted by 409, remains free of packing or similar things, to the effect that the working vapor 112 not only above but also below can penetrate laterally into the condensation zone.
  • the imaginary boundary line 410 should figure 5 illustrate.
  • the entire area of the condenser is designed with its own condenser base 200, which is arranged above an evaporator base.
  • Figure 1 shows a preferred embodiment of a heat pump not in accordance with the invention, and in particular a heat pump section comprising the "top" portion of the heat pump such as that shown in figure 5 shown shows.
  • the engine corresponds to M 110 of figure 5
  • the area surrounded by a motor wall 309 shown in the cross-sectional view in 10 is preferably formed with cooling ribs on the outside in the liquid area 328 in order to enlarge the surface of the motor wall 309 .
  • the area of the motor housing corresponds to 300 in 4 the corresponding area 300 in figure 5 .
  • the radial wheel 304 is also shown in a more detailed cross section.
  • the radial wheel 304 is attached to the motor shaft 306 in a fastening area which is forked in cross-section.
  • the motor shaft 306 has a rotor 307 opposed to the stator 308 .
  • the rotor 307 comprises schematically in 10 shown permanent magnets.
  • the motor gap 311 extends between the rotor and the stator and opens into the further gap 313, which runs along the fastening area of the shaft 306, which is fork-shaped in cross section, to the guide chamber 302, as is also shown at 346.
  • an emergency bearing 344 which does not support the shaft during normal operation. Instead, the shaft is supported by the bearing portion shown at 343.
  • the emergency bearing 344 is only present to store the shaft and thus the radial wheel in the event of damage, so that the rapidly rotating radial wheel cannot cause any major damage in the heat pump in the event of damage.
  • 10 also shows various fastening elements such as screws, nuts, etc. and various seals in the form of various O-rings.
  • an additional convection element 342 to which reference will be made later 10 is received.
  • FIG. 12 also shows a splash guard 360 in the vapor space above the maximum volume in the motor housing that is normally filled with liquid working fluid.
  • This splash guard is designed to intercept drops of liquid thrown into the vapor space during nucleate boiling.
  • the vapor path 310 is preferably designed in such a way that it benefits from the splash guard 360, ie due to the flow into the motor gap and the further gap only working medium vapor but not liquid droplets due to the boiling in the motor housing are sucked in.
  • the convective shaft cooling type heat pump preferably has a steam inlet formed so that steam flow through the motor gap and the other gap does not pass through a bearing portion formed to support the motor shaft with respect to the stator.
  • the bearing section 343, which in the present case comprises two ball bearings, is sealed off from the motor gap, e.g. B. through O-rings 351.
  • the working steam can only, as shown by the path 310, enter through the steam supply into an area within the motor wall 309, run from there in a free space down and on the rotor 307 along pass through the motor gap 311 into the further gap 313.
  • the advantage of this is that steam does not flow around the ball bearings, so that bearing lubrication remains in the sealed ball bearings and is not drawn through the motor gap. Furthermore, it is also ensured that the ball bearing is not moistened, but always remains in the defined condition during installation.
  • the motor housing in the operating position of the heat pump, is mounted on top of the condenser housing 114 so that the stator is above the impeller and the vapor flow 310 is top to bottom through the motor gap and the further gap.
  • the heat pump includes the bearing portion 343, which is designed to support the motor shaft with respect to the stator.
  • the bearing section is arranged in such a way that the rotor 307 and the stator 308 are arranged between the bearing section and the radial wheel 304 .
  • This has the advantage that the bearing section 343 can be arranged in the steam area inside the motor housing and the rotor/stator, where the greatest power loss occurs, below the maximum liquid level 322 ( 3 ) can be arranged.
  • the motor housing also includes the working medium inlet 330 to lead liquid working medium from the condenser to a wall of the compressor motor for motor cooling.
  • This working medium inlet 362 runs into a closed volume 364, which represents a ball bearing cooling system.
  • a duct emerges from the ball bearing cooling system and comprises a tube 366 which does not contain the working medium on top of the working medium volume 328, as in FIG 3 shown, leads, but that leads the working medium down to the wall of the engine, ie the element 309.
  • the tube 366 is designed to be arranged inside the convection element 342, which is arranged around the motor wall 309, at a certain distance so that inside the convection element 342 and outside the convection element 342 within the motor housing 300 a volume liquid working fluid exists.
  • a convection zone 367 is created within the volume of working liquid 328 due to nucleate boiling due to the working medium that is in contact with the motor wall 309, particularly in the lower area where the fresh working medium inlet 366 ends.
  • the nucleate boiling pulls the boiling bubbles from bottom to top . This results in an ongoing "agitation” in that hot working fluid is brought up from below.
  • the energy from nucleate boiling then goes into the vapor bubble, which then ends up in vapor volume 323 above liquid volume 328 .
  • the resulting pressure is brought directly through the overflow 324, the overflow extension 340 and the outlet 342 in the condenser. With it There is a constant heat transfer from the engine to the condenser, which is primarily due to the removal of vapor and not the removal of heated liquid.
  • the heat which is actually the engine's waste heat, gets through the steam removal to where it is supposed to go, namely in the condenser water that is to be heated.
  • the heat dissipation from the engine to the condenser is also favorable for cooling applications of the heat pump, because the condenser is typically coupled with an efficient heat dissipation, e.g. in the form of a heat exchanger or a direct heat dissipation in the area to be heated. It is therefore not necessary to create a separate engine waste heat device, but the heat dissipation from the condenser to the outside that already exists from the heat pump is to a certain extent “also used” by the engine cooling.
  • the motor housing is also designed to maintain the maximum level of liquid working medium when the heat pump is in operation and to create the vapor space 323 above the level of liquid working medium.
  • the steam supply is also designed in such a way that it communicates with the steam space, so that the steam in the steam space for convective wave cooling through the engine gap and the other gap in 4 is conducted.
  • the outflow is arranged as an overflow in the motor housing in order to conduct liquid working fluid above the level into the condenser and also to create a vapor path between the vapor space and the condenser.
  • drain 324 is both an overflow and a vapor path.
  • these functionalities can also be implemented using different elements by means of an alternative design of the overflow on the one hand and a vapor space on the other hand.
  • the heat pump includes in the in 10 shown embodiment, a special ball bearing cooling, which is formed in particular in that the sealed volume 364 is formed with liquid working medium around the bearing section 343.
  • the inlet 362 enters this volume and the volume has an outlet 366 from the ball bearing cooling into the working medium volume for motor cooling.
  • This will create a separate Ball bearing cooling created, which, however, runs around the outside of the ball bearing and not inside the bearing, so that although this ball bearing cooling is efficiently cooled, the lubricating filling of the bearing is not impaired.
  • the working medium inlet 362 includes in particular the line section 366, which extends almost to the bottom of the motor housing 300 or to the bottom of the liquid working medium 328 in the motor housing or at least to an area below the maximum level, in particular to liquid working medium out of the ball bearing cooling system and supply the liquid working medium to the engine wall.
  • the convection element which is arranged in the liquid working medium at a distance from the wall of the compressor motor 309, and which is more permeable to the liquid working medium in a lower region than in an upper region.
  • the convection element is designed in the embodiment in the form of a "crown" which is placed upside down in the volume of liquid. This allows the convection zone 367 to be formed, as shown in 10 is shown.
  • alternative convection elements 342 that are in some way less permeable at the top than at the bottom may be used.
  • a convection element could be taken that has holes at the bottom that have a larger passage cross section in terms of shape or number than holes in the upper area.
  • Alternative elements for generating the convection current 367 as shown in 10 shown are also usable.
  • the emergency bearing 344 which is designed to secure the motor shaft 306 between the rotor 370 and the radial wheel 304 , is provided to secure the motor in the event of a bearing problem.
  • the further gap 313 extends through a bearing gap of the emergency bearing or preferably through holes intentionally made in the emergency bearing.
  • the emergency bearing is provided with a large number of bores, so that the emergency bearing itself represents the lowest possible flow resistance for the steam flow 10 for the purposes of convective wave cooling.
  • Motor shaft 306 includes a shaded core as shown in FIG 12 is shown in its upper portion, which is the storage portion 343 is supported by preferably two ball bearings 398 and 399.
  • the rotor with permanent magnets 307 is formed further down on the shaft 306 .
  • These permanent magnets are placed on the motor shaft 306 and are held in place at the top and bottom by stabilizing bandages 397, which are preferably made of carbon.
  • the permanent magnets are held by a stabilizing sleeve 396, which is also preferably designed as a carbon sleeve. This securing or stabilizing sleeve ensures that the permanent magnets remain securely on the shaft 306 and cannot become detached from the shaft due to the very strong centrifugal forces due to the high speed of the shaft.
  • the shaft is formed of aluminum and has a forked cross-sectional mounting portion 395 which provides support for the radial wheel 304 when the radial wheel 304 and the motor shaft are not formed as a single piece, but rather as two elements. If the radial wheel 304 is designed in one piece with the motor shaft 306, the wheel mounting section 395 is not present, but instead the radial wheel 304 then connects directly to the motor shaft. In the area of the wheel mount 395 is also located how it looks 10 can be seen, the emergency bearing 344, which is preferably also made of metal and in particular aluminum.
  • the motor housing 300 is off 10 , that also in 3 is designed to obtain a pressure which is at most 20% greater than the pressure in the condenser housing in operation of the heat pump. Furthermore, the motor housing 300 can be designed to obtain a pressure that is so low that when the motor wall 309 heats up as a result of the operation of the motor, nucleate boiling takes place in the liquid working medium 328 and in the motor housing 300 .
  • the bearing section 343 is preferably arranged above the maximum liquid level, so that even if there is a leak in the motor wall 309, no liquid working medium can get into the bearing section.
  • the area of the motor which at least partially includes the rotor and the stator, is below the maximum level, since the greatest power loss typically occurs in the bearing area on the one hand, but also between the rotor and stator on the other hand, and can be optimally transported away by the convective nucleate boiling .
  • the passage 377 is provided, which is formed in the top plate of the condenser volume and which, depending on the implementation, may comprise a single channel on one side or two channels on both sides or even sector-shaped channels in order to allow as much overflow as possible of the working liquid flowing over the inlet 362 is fed to the ball bearing cooling system and is fed from the ball bearing cooling system 366 to the motor wall, as shown by the arrows 367.
  • the liquid medium then runs out into the area of the engine cooling and then, when a certain level is reached, out via the inlet 324 .
  • the outflow 324 can also be contained in the volume of the engine cooling system, ie in the area in which the convection element 342 is also arranged.
  • Figure 12 illustrates an implementation where, not in accordance with the invention, only the top of the plenum is cooled, in which case the special shaping of the outer portion of the plenum to create the recessed portion 362 is not required.
  • the resource flow 324 is alternative to 4 or 10 educated.
  • the drain does not necessarily have to be a passive drain, but can also be an active drain, controlled by a pump or other element, for example, and depending on a level detection of the level 322 draws some working fluid from the motor housing 300 .
  • tubular drain 324 there could be a resealable opening at the bottom of motor housing 300 to allow a controlled amount of working fluid to drain from the motor housing into the condenser by momentarily opening the resealable opening.
  • FIG. 9 also shows the area to be heated or a heat exchanger 391, from which a condenser inlet 204 runs into the condenser and from which a condenser outlet 203 exits.
  • a pump 392 is also provided in order to drive the circulation of condenser inlet 204 and condenser outlet 203 .
  • This pump 392 preferably has a branch to the inlet 362 as shown schematically. This means that no separate pump is required, but the pump for the condenser discharge, which is present anyway, also drives a small part of the condenser discharge into the inlet line 362 and thus into the liquid volume 328.
  • FIG. 9 further shows the overflow 324 as an alternative implementation in which liquid e.g. B. can be actively sucked off and fed directly to the guide chamber 302 or the suction mouth 92, again via lines 421, 422.
  • liquid e.g. B. can be actively sucked off and fed directly to the guide chamber 302 or the suction mouth 92, again via lines 421, 422.
  • preferably heated liquid from the condenser outflow 203 is used as cooling liquid.
  • FIG 12 shows a preferred embodiment according to the invention, which combines the functionalities of various other illustrated embodiments.
  • Working liquid or cooling liquid which is preferably water
  • is fed via the inlet 330 or 362, as shown in 9 is shown, first supplied to the ball bearing cooling, which is shown as a closed volume 364.
  • Cooling liquid that has entered the closed volume 364 flows past the ball bearing surrounded by the closed volume and exits the ball bearing.
  • the cooling liquid flows via the connecting line or tube 366 into the engine cooling space, which is maintained at a level 322 of working liquid.
  • the level 322 is held by a wall 321 here.
  • the working liquid is preferably fed via line 366 down into the area within wall 321, as also shown in FIG 10 is shown.
  • a good convection zone is thus obtained, with nucleate boiling taking place in particular on the heated engine wall.
  • the working fluid also overflows the wall as shown at 324 .
  • 324 may represent a channel overflow, but may also be a free overflow.
  • the liquid then runs down the outside of the wall 321 and then via the lead-through area or opening 377 onto the flow area 376. It then flows down from this flow area 376 to finally land on top of the duct in the recessed area.
  • 11 thus shows an embodiment in which, with the same liquid flow, ball bearing cooling, motor cooling, cooling of the upper side of the duct, cooling of the suction mouth and cooling of the lower side of the duct, as well as open cooling of the vapor flow through the overflow-board section between the end of element 381 and element 382, this open area preferably extending circularly.
  • the course of the cooling liquid is thus via the feed line 422, 324, 377, 376 to the upper outer side 372 of the guide space 302. From there the liquid runs via the discharge line 378 from the outside of the guide space 302 to the outside of the suction mouth 92. It runs from there the liquid via the cooling channel 379 along the outside of the suction mouth to the lower outside of the plenum and along the lower outside of the plenum to the overflow 382 and from there down into the condenser.
  • the result is that, after compression, the severe overheating of the water vapor that would otherwise occur in the uncooled guide space is avoided. Part of the pressure build-up takes place in the guide chamber, in which overheating is also reduced by cooling, which increases the efficiency and quality of the compression process.
  • Superheated steam has a higher viscosity and therefore greater flow resistance than saturated steam. Superheated water vapor must therefore first reduce overheating in order to be able to condense easily.
  • the guide space 302 and also the suction mouth 92 are preferably made of a material with good thermal conductivity, such as metal. The heat from the steam flow can then be dissipated particularly well, although good results can also be achieved with poorly heat-conducting materials. By removing the superheat from the steam flow, the flow resistance decreases and the condensing ability of the compressed steam improves.
  • the control space In order to keep the temperature of the control space as close as possible to the saturated steam temperature of the pressure prevailing in the condenser, the control space is made of metal and surrounded by liquid, such as water, which equalizes the pressure with the condenser. If energy/heat from the steam flow is coupled in, the surrounding water starts to boil and releases the energy again. As a result, the guide space is kept very close to the saturated steam temperature of the steam pressure. Liquefaction in the duct is prevented by the remaining thermal resistance of the materials and the resulting slight overheating.
  • the cooling water for the control room is first routed through the bearings and also open engine cooling. Due to the open engine cooling, the water cools down again to the saturated steam temperature through partial evaporation and is available for the open guide space cooling. First, the upper control room part is filled with water. With a one-sided guide space cooling the water would just overflow like it did with the in 10 shown
  • Embodiment is the case, which therefore does not correspond to the invention.
  • the water from the upper guide space cooling is, however, in an embodiment that in 11 is shown, directed into the lower guide space and suction mouth cooling.
  • At the end of the control room there is an open area with an overflow. Through evaporation, the water constantly cools itself to saturated steam temperature. The remaining water overflows and flows into a catch basin.
  • a balance between the condenser 114 and the evaporator 90 can be used as shown in 2 is shown, take place via a throttle 91. With an open system, however, a choke is not necessary either.
  • the reduced thermal load on the components is another advantage. Due to the evaporative cooling, the entire compressor can be kept close to the saturated steam temperature despite losses. Motor losses and bearing losses during compression are reduced via evaporation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Motor Or Generator Cooling System (AREA)
EP18759919.6A 2017-08-29 2018-08-21 Wärmepumpe mit einer kühlvorrichtung zum kühlen eines leitraums und eines saugmunds Active EP3676544B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017215085.8A DE102017215085A1 (de) 2017-08-29 2017-08-29 Wärmepumpe mit einer Kühlvorrichtung zum Kühlen eines Leitraums oder eines Saugmunds
PCT/EP2018/072548 WO2019042825A2 (de) 2017-08-29 2018-08-21 Wärmepumpe mit einer kühlvorrichtung zum kühlen eines leitraums oder eines saugmunds

Publications (2)

Publication Number Publication Date
EP3676544A2 EP3676544A2 (de) 2020-07-08
EP3676544B1 true EP3676544B1 (de) 2023-05-24

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EP18759919.6A Active EP3676544B1 (de) 2017-08-29 2018-08-21 Wärmepumpe mit einer kühlvorrichtung zum kühlen eines leitraums und eines saugmunds

Country Status (6)

Country Link
US (1) US11754325B2 (ja)
EP (1) EP3676544B1 (ja)
JP (1) JP6985502B2 (ja)
CN (1) CN111094874B (ja)
DE (1) DE102017215085A1 (ja)
WO (1) WO2019042825A2 (ja)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019210039B4 (de) * 2019-07-08 2022-08-11 Efficient Energy Gmbh Kühlgerät, Verfahren zum Herstellen eines Kühlgeräts und Transportgerät mit einem Kühlgerät
CN115055770B (zh) * 2022-06-25 2024-08-13 湖北欧米隆精密机械有限公司 一种电火花成型机油槽用放油机构

Family Cites Families (18)

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Publication number Priority date Publication date Assignee Title
DE2604942A1 (de) * 1976-02-09 1977-08-11 Karl Dr Ing Schmidt Waermepumpe
US5200008A (en) 1991-02-07 1993-04-06 Michelin Recherche Et Technique Radial tire tread and method of mounting a tire with said tread
IL106945A (en) 1993-09-08 1997-04-15 Ide Technologies Ltd Centrifugal compressor and heat pump containing it
JP2002005089A (ja) * 2000-06-20 2002-01-09 Mitsubishi Heavy Ind Ltd ターボ形圧縮機及びそれを備えた冷凍装置
JP2008531965A (ja) * 2005-02-23 2008-08-14 アイ・ディ・イー・テクノロジーズ・リミテッド 冷媒として水を使用する小型ヒートポンプ
DE202006005461U1 (de) 2006-04-04 2007-08-16 Sedlak, Holger Vorrichtung zum Pumpen von Wärme
JP2009150594A (ja) * 2007-12-19 2009-07-09 Mitsubishi Heavy Ind Ltd 冷凍装置
DE102008016664A1 (de) * 2008-04-01 2009-10-29 Efficient Energy Gmbh Vertikal angeordnete Wärmepumpe und Verfahren zum Herstellen der vertikal angeordneten Wärmepumpe
DE102008016663A1 (de) 2008-04-01 2009-10-08 Efficient Energy Gmbh Verflüssiger für eine Wärmepumpe und Wärmepumpe
KR101212698B1 (ko) 2010-11-01 2013-03-13 엘지전자 주식회사 히트 펌프식 급탕장치
JP5920110B2 (ja) * 2012-02-02 2016-05-18 株式会社デンソー エジェクタ
JP5941297B2 (ja) * 2012-02-23 2016-06-29 川崎重工業株式会社 冷凍機
DE102012220199A1 (de) 2012-11-06 2014-05-08 Efficient Energy Gmbh Verflüssiger, Verfahren zum Verflüssigen und Wärmepumpe
GB2524421B (en) * 2012-12-07 2017-04-12 Trane Int Inc Motor cooling system for chillers
CN106133461B (zh) * 2014-03-28 2019-04-09 开利公司 带挤压膜阻尼器的制冷压缩机滚动轴承
CN104457027A (zh) * 2014-12-02 2015-03-25 苟仲武 一种改进的压缩式热泵工作方法及其装置
CN106996391A (zh) * 2016-01-25 2017-08-01 松下知识产权经营株式会社 叶轮、离心压缩机以及制冷循环装置
DE102016203407A1 (de) * 2016-03-02 2017-09-07 Efficient Energy Gmbh Wärmepumpe mit konvektiver Wellenkühlung

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US20200200447A1 (en) 2020-06-25
JP6985502B2 (ja) 2021-12-22
DE102017215085A1 (de) 2019-02-28
EP3676544A2 (de) 2020-07-08
WO2019042825A2 (de) 2019-03-07
JP2020531786A (ja) 2020-11-05
WO2019042825A3 (de) 2019-04-25
US11754325B2 (en) 2023-09-12
CN111094874B (zh) 2022-04-12
CN111094874A (zh) 2020-05-01

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