阅读说明：本技术 用于热工作机的水基制冷剂和具有这种制冷剂的热工作机 (Water-based refrigerant for hot working machine and hot working machine having the same ) 是由 斯蒂芬·克莱因 拉尔夫·斯蒂芬斯 于 2019-08-23 设计创作，主要内容包括：本发明涉及一种用于热工作机的水基制冷剂。根据本发明的用于热工作机(150)的制冷剂基于水并且具有带有羟基的制冷剂成分,例如具有乙醇形式的制冷剂成分,该热工作机具有蒸发器(A)、冷凝器(B)、压缩机(C-(GL))和节流机构(D)。本发明的其他方面涉及这种混合物作为用于热工作机的制冷剂的用途、具有这种制冷剂的热工作机,以及用于运行具有这种制冷剂的热工作机的方法。(The present invention relates to a water-based refrigerant for a hot working machine. The refrigerant for a hot working machine (150) according to the invention is based on water and has a refrigerant component with hydroxyl groups, for example in the form of ethanol, and has an evaporator (A), a condenser (B), a compressor (C) GL ) And a throttle mechanism (D). Further aspects of the invention relate to the use of such a mixture as a refrigerant for a hot working machine, a hot working machine having such a refrigerant, and a method for operating a hot working machine having such a refrigerantA method.)

1. A water-based refrigerant for a hot working machine (150, 151) having an evaporator (A), a condenser (B), a compressor (C)_GL、C_KL) And a throttle mechanism (D),

it is characterized in that the preparation method is characterized in that,

the refrigerant has a refrigerant component with hydroxyl groups.

2. The refrigerant as set forth in claim 1,

it is characterized in that the preparation method is characterized in that,

the refrigerant component consists of an alcohol, in particular a monohydric alcohol, in particular ethanol or propan-1-ol.

3. The refrigerant according to claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the refrigerant composition is at least 10%, particularly at least 20%, particularly at least 30% of the total refrigerant.

4. The refrigerant according to claim 1, 2 or 3,

it is characterized in that the preparation method is characterized in that,

the height to which the refrigerant composition is highest in the entire refrigerant does not make the refrigerant flammable.

5. Use of a mixture of water and a refrigerant component having hydroxyl groups as a refrigerant for a hot working machine (150, 151) having an evaporator (A), a condenser (B), a compressor (C)_GL、C_KL) And a throttle mechanism (D).

6. A hot working machine having an evaporator (a), a condenser (B), a compressor (C), a throttling mechanism (D) and a refrigerant circuit (152, 153) with a refrigerant according to any of claims 1-4.

7. The thermal working machine according to claim 6,

it is characterized in that the preparation method is characterized in that,

a refrigerant adjusting device (A) is provided, by means of which the refrigerant composition of the refrigerant having hydroxyl groups can be changed during the operation of the hot work machine (150, 151).

8. The thermal working machine according to claim 6 or 7,

it is characterized in that the preparation method is characterized in that,

all electrical components of the hot work machine are designed to be explosion-proof.

9. The thermal working machine according to claim 6, 7 or 8,

it is characterized in that the preparation method is characterized in that,

said pressureShrinking machine (C)_GL) Is designed as a two-shaft rotary extrusion press having a first spindle rotor (3) which can be rotated about a first support shaft (5) and a second spindle rotor (3) which can be rotated about a second support shaft (5), said first and second spindle rotors being supported by means of sliding bearings (6, 7) which are operated with a refrigerant.

10. The thermal working machine according to claim 9,

it is characterized in that the preparation method is characterized in that,

the first spindle rotor (5) is driven by a first drive machine (4), the second spindle rotor (5) is driven by a second drive machine (4), and

the refrigerant is used to cool at least one of the drive machines (4).

11. The thermal working machine according to claim 9 or 10,

it is characterized in that the preparation method is characterized in that,

the compressor (C)_GL) Having at least one pitot tube pump (9) by means of which the compressor (C) is supplied with a supply_GL) The refrigerant is discharged.

12. The thermal working machine according to claim 11,

it is characterized in that the preparation method is characterized in that,

the pitot tube pump (9) is supplied via an accumulation tank (9.s) extending around the respective support shaft (5), said tank being embodied and arranged so as to be present in the compressor (C)_GL) In the compressor (C)_GL) During operation, are collected in an accumulation tank (9. s).

13. The thermal working machine according to claim 6, 7 or 8,

it is characterized in that the preparation method is characterized in that,

the compressor (C)_KL) Is configured as a two-shaft rotary extrusion press having a first spindle rotor (101.R) rotatable about a first support shaft (101) and rotatable about a second support shaft (101)By means of a rolling bearing (102), wherein the rolling bearing (102) is protected from contact with refrigerant by supplying a protective gas.

14. The heat working machine according to claim 13,

it is characterized in that the preparation method is characterized in that,

the compressor (C)_KL) Having an intermediate chamber (108) from which the supplied protective gas is discharged, wherein the evaporated refrigerant is supplied to the intermediate chamber (108) such that a mixture consisting of protective gas and evaporated refrigerant is discharged from the intermediate chamber (108).

15. The thermal working machine according to claim 14,

it is characterized in that the preparation method is characterized in that,

the compressor (C)_KL) Comprises a barrier vapor chamber (117) to which refrigerant is supplied and evaporated at the barrier vapor chamber (117), and the barrier vapor chamber (117) communicates with the intermediate chamber (108).

16. The thermal working machine according to claim 14 or 15,

it is characterized in that the preparation method is characterized in that,

the protective gas is supplied to the intermediate chamber (108) via a flow resistance (118.b) on the side chamber side and/or the evaporated refrigerant is supplied to the intermediate chamber (108) via a flow resistance (118.a) on the working chamber side.

17. The thermal working machine according to claim 14, 15 or 16,

it is characterized in that the preparation method is characterized in that,

a recirculation device (RC) is provided to which the mixture of protective gas and evaporated refrigerant discharged from the intermediate chamber (108) is supplied and which separates the mixture into protective gas and refrigerant.

18. The thermal working machine according to claim 17,

it is characterized in that the preparation method is characterized in that,

the refrigerant generated in the recirculation device (RC) is supplied to the refrigerant circuit (153) again.

19. The evaporator (A), the condenser (B) and the compressor (C) are used for operation_GL、C_KL) A method for operating a thermal working machine of a throttle mechanism (D),

characterized in that the refrigerant according to any one of claims 1 to 4 is used as the refrigerant.

Technical Field

The present invention relates to a water-based refrigerant for a hot-working machine according to the preamble of claim 1, the use of such a refrigerant according to claim 5, a hot-working machine according to claim 6 and a method for operating a hot-working machine according to claim 19.

Background

A thermal working machine (i.e. for example a refrigerator or a heat pump) in which mechanical energy is converted into thermal energy requires a refrigerant which is subjected to temperature and state changes during operation. Due to the good thermodynamic properties of refrigerants, fluorinated hydrocarbons have hitherto often been used, such as tetrafluoroethane, known as refrigerant R134 a. Refrigerants with lower greenhouse potential must be found in the future, mainly due to the effect of refrigerants as so-called greenhouse gases. Here, natural refrigerants are of primary interest, including ammonia, carbon dioxide, air, propane, propylene, and water. The advantages of natural refrigerants are especially their environmentally friendly properties. Natural refrigerants do not cause ozone layer decomposition and do not cause the direct greenhouse effect worth mentioning.

DE 102004001927 a1 describes a hot working machine in the form of a heat pump, in which water is used as refrigerant. The water is referred to as refrigerant R718. It is known that water has the property of freezing, i.e. becoming ice, at 0 ℃. The ice will obstruct and clog the hot working machine. Therefore, a thermal working machine having water as a refrigerant can only be operated at temperatures above the freezing point.

The described limitation of the range of use to temperatures greater than 0 ℃ severely limits the possibilities of use of hot working machines using water as refrigerant. For example, heat pumps for heating rooms cannot be operated with water as a refrigerant in at least central europe, where temperatures below freezing can be expected. Even at ambient temperatures above 0 ℃, it is not possible to cool the room or working refrigerant to temperatures below 0 ℃. The minimum of the lowest ambient temperature and the lowest room temperature or operating refrigerant temperature may be referred to as the lower limit of the usage range of the refrigerant. The maximum ambient temperature and the maximum room temperature or operating refrigerant temperature may be referred to as the upper limit of the usage range of the refrigerant.

Disclosure of Invention

Accordingly, it is an object of the present invention to provide a refrigerant for a hot-working machine and a hot-working machine which have the least negative environmental impact and the greatest possible range of use. This object is achieved by a refrigerant according to claim 1 and a hot working machine according to claim 6.

The refrigerant according to the invention for a hot working machine having an evaporator, a condenser, a compressor and a throttle mechanism is based on water and has a refrigerant composition with hydroxyl groups, i.e. OH groups or hydrogen-oxy groups. Thus, the freezing point, i.e. the temperature at which the refrigerant passes from the liquid state to the solid state, can be shifted into the freezing point of pure water, i.e. into the temperature range below 0 ℃. Thus, the hot working machine can also be advantageously used at temperatures below 0 ℃ and also cool the room or working refrigerant to temperatures below 0 ℃. Therefore, the range of use of water as the refrigerant, that is, the range of use as the refrigerant R718 can be advantageously expanded.

A defined use of the refrigerant according to the invention is therefore to use a mixture of water and a refrigerant component having hydroxyl groups as a refrigerant for a thermal working machine having an evaporator, a condenser, a compressor and a throttle.

A water-based refrigerant is understood to be a refrigerant that contains water at least to a non-negligible extent. The water content is in particular over 50%. However, for certain applications it is also possible that the water content is less than 50%, i.e. for example only 10% or only 1%. The percentage data is stated in terms of the mass of refrigerant as all other following percentage data, i.e. mass percent rather than volume percent.

A thermal machine is understood here to be a machine which converts mechanical energy into thermal energy. The heat working machine is in particular designed as a refrigerating machine, a heat pump or a combination of a refrigerating machine and a heat pump.

The refrigerant according to the present invention may have other components in addition to the refrigerant component having hydroxyl groups.

The range of refrigerant compositions may be matched to the intended application of the refrigerant, i.e. selected specifically according to the application. Here, it is generally specified that the lower limit of the planned usage range of the hot working machine, the larger the range of the refrigerant component having hydroxyl groups.

In one embodiment of the invention, the refrigerant component having hydroxyl groups is composed of an alcohol, in particular a monohydric alcohol, in particular of the formula C₂H₆O or as formula C₂H₅OH as alcohol or as alcohol of the formula C₃H₈O or as formula C₃H₇OH, propane-1-ol. Mixtures of different alcohols are also possible. Alcohols, in particular monohydric alcohols, i.e. alcohols having only one OH group and in particular ethanol and propan-1-ol, have properties which have a positive effect when used as refrigerant components. They have a low freezing point (about-114, 5 ℃ ethanol, -126 ℃ propan-1-ol), are readily soluble in water, are not harmful or only slightly harmful to health, and are not harmful or only slightly harmful to the environment.

In one embodiment of the invention, the refrigerant composition is at least 10%, in particular at least 20%, in particular at least 30%, of the total refrigerant. A particularly advantageous extension of the range of use of the refrigerant can thus be achieved. For example, when ethanol is used, the lower limit of the range of use may be shifted to about-5 ℃ with 10% of the composition, to about-10 ℃ with 20% of the composition, and to about-19 ℃ with 30% of the composition.

As the refrigerant composition is further increased, for example, to 40% or 50%, the lower end of the usage range may be further shifted to lower temperatures. For example, in the case of ethanol the proportion is 40% to about-30 ℃ and the proportion is 50% to about-37 ℃.

In the embodiment of the invention, the refrigerant component having hydroxyl groups in the entire refrigerant does not make the refrigerant flammable at the highest possible height. There is therefore no risk that the refrigerant may ignite, which makes it possible to achieve a particularly safe handling of the refrigerant and to achieve a particularly safe use of the refrigerant. Furthermore, handling of non-combustible substances is significantly simpler and less laborious and therefore less costly than combustible substances.

In particular, the refrigerant is not flammable under the conditions (herrschen) present/prevailing during the operation of the hot working machine, i.e. under the so-called operating conditions. Therefore, there is no danger of refrigerant burning during operation in the hot working machine. The conditions relate in particular to the existing/prevailing (herrschenden) pressure and temperature.

Alternatively or additionally, the refrigerant is non-flammable under standard conditions. Thus, the refrigerant does not burn during transport, storage or introduction into the thermal refrigerator.

The maximum proportion of refrigerant components having hydroxyl groups for complying with the conditions depends on the refrigerant component used, i.e. for example the type of alcohol, and can be determined for example by simple experiments. The largest component when ethanol is used is for example between 40% and 45%. Standard conditions are understood here to be chemical standard conditions, i.e. a temperature of 0 ℃ and a pressure of 1013.25 mbar.

However, the proportion of refrigerant having hydroxyl groups in the entire refrigerant may also be so high that the refrigerant is flammable under standard conditions. Flammability may be acceptable, for example, if the lower end of the range of use is at a very low temperature and the alternative refrigerant has additional or greater disadvantages, such as being explosive. For example, for the lower limit of the use range of-110 ℃, 90% of the ethanol component may be used.

The above object is also achieved by a thermal working machine having an evaporator, a condenser, a compressor, a throttle mechanism, and a refrigerant circuit having the above refrigerant.

In one embodiment of the invention, the hot working machine comprises a refrigerant control device, by means of which the refrigerant composition with the hydroxyl groups of the refrigerant can be changed during operation of the hot working machine. The lower limit of the usage range may be changed during operation as the refrigerant composition having hydroxyl groups in the entire refrigerant, i.e., the composition of the refrigerant having hydroxyl groups, varies. Thus, during operation, it is possible to react to changes in the environmental conditions or boundary conditions of the hot work machine without having to interrupt the operation of the hot work machine. The refrigerant conditioning device is in particular designed such that it supplies pure water, pure refrigerant components with hydroxyl groups or mixtures thereof to the entire refrigerant. The refrigerant conditioning device can have a measuring device, for example a refractometer, by means of which the refrigerant composition having hydroxyl groups can be determined. Thus, a desired refrigerant composition having hydroxyl groups can be adjusted or regulated.

In one embodiment of the invention, all electrical components of the hot working machine are designed to be explosion-proof. This makes particularly safe operation of the hot work machine possible. The electrical components of the hot-working machine are understood here to mean, for example, one or more electric motors, in particular for driving a compressor, necessary wiring, control devices, sensors, etc. Explosion-proof embodiments are understood to mean, in particular, embodiments which comply with the ATEX product code 2014/34/EU. In this case, the motor windings of the electric machine are cast, for example, from plastic and the cable sleeve is designed to be gas-tight, for example, also cast.

In one embodiment of the invention, the compressor is designed as a two-shaft rotary extrusion press, which has a first spindle rotor which is rotatable about a first support shaft and a second spindle rotor which is rotatable about a second support shaft, the two spindle rotors being supported by means of slide bearings which are operated by means of a refrigerant. Such a two-shaft rotary extrusion press is described, for example, in the german patent application DE 102018001519.0, which was not published beforehand.

When using refrigerants having a refrigerant component containing hydroxyl groups, very high pressure ratios for the vacuum are required, for example, by having to compress from 2mbar to 200 mbar. Such a compression ratio can be technically realized only by a multi-stage rotary vacuum compressor in practice. The so-called "main shaft compressor" is designed as a two-shaft rotary extruder, which compressor functions as a multistage screw compressor. In this case, the spindle compressor is operated in particular as a so-called "dry pump", in which the working chamber is preferably operated without an operating fluid, in that the contactless connection of the two spindles is generally ensured by an electronic synchronization device. Each spindle rotor has its own drive (motor), which operates precisely electronically, so that the two spindle rotors do not touch during operation.

The mounting of the spindle rotor by means of a sliding bearing operated by means of a refrigerant advantageously enables the elimination of lubricants, in particular of grease or oil, during mounting. Thus, there is no risk of the lubricant being washed off or diluted from the bearing, which may occur, for example, when refrigerant condenses in the bearing area. Such washing or dilution of the bearing lubricant may lead to bearing damage and thus to failure of the compressor and thus of the entire hot-working machine. The use of the sliding bearing thus makes the compressor and therefore the entire hot-working machine operate particularly reliably.

For example, when the spindle rotors are mounted by means of plain bearings, the radial forces at the ends of each spindle rotor are supported in rotation by means of a bushing on a fixed and continuous support shaft having a small support length, and the axial forces of each spindle rotor are likewise carried by this support shaft by means of an axial plain bearing by a support ring fixed relative to the carrier. Each support shaft is fixed to the compressor housing by a shaft support having a cantilever arm. Preferably, the pressure p at the compressor inlet at the continuous support shaft, at the axial refrigerant sliding bearing₁With pressure p at the compressor outlet₂Is subjected to pressure separation so that the higher pressure p₂At a larger radius, and a lower pressure p₁At smaller radii.

For example, the drive for each spindle rotor is implemented as an outer rotor motor as drive motor, preferably as a synchronous motor, for a motor-to-spindle rotor synchronization device. The motor stator of the synchronous machine is likewise mounted with its windings on the support shaft, wherein the motor rotor of the synchronous machine drives the spindle rotor in a rotationally fixed manner by means of a torque, wherein the motor heat loss is forcibly dissipated by means of the shaft coolant cooling.

External rotor electric machine for improving the thermal balance during operation, in particular the pressure p at the compressor inlet₁Lower and motor cable thereof, especially in the hole of the supporting shaftIs directed to the inlet side of the compressor.

Each spindle rotor is designed, in particular, by means of a bearing tube in such a way that the bending stiffness required for the desired high critical speed of bending is achieved, wherein a feed screw rotor having a gas feed external thread is mounted on each bearing tube in a rotationally fixed manner, said feed screw rotor depending on the application-specific (i.e. for specific temperature requirements) being the pressure p at the compressor inlet supplied with refrigerant by means of the feed tube₁The lower is implemented by a cylindrical rotor internal evaporator cooling section and a refrigerant vapor outlet on the inlet side of the compressor.

The outer feed thread of each spindle rotor is designed such that the angle along the rotor shaft at the root circle is in the range 0 ° to preferably less than 8 °.

For each spindle rotor, the support shaft is held in a rotationally fixed manner at each end by a shaft bearing, wherein the axial positioning is preferably achieved by means of a union nut and/or a clamping disk, in particular for targeted adjustment of the gap between the spindle rotor head and the compressor housing working chamber by means of a non-cylindrical spindle rotor profile.

Each spindle rotor is designed in particular as a completely mounted and fully balanced rotary unit, wherein a so-called emergency synchronizing gear is positioned on the outlet side of the compressor.

In one embodiment of the invention, the first spindle rotor is driven by the first drive machine and the second spindle rotor is driven by the second drive machine, and the refrigerant is used for cooling at least one drive machine, in particular for cooling both drive machines. As a result, particularly effective cooling of the drive machine can be achieved without the use of special refrigerants. The refrigerant can also be at least partially evaporated here, which enables a particularly efficient removal of the heat loss of the drive.

In one embodiment of the invention, the compressor has at least one, in particular a plurality of, in particular four, pitot tube pumps, by means of which the refrigerant supplied to the compressor is discharged from the compressor. Therefore, the refrigerant can be simply and efficiently discharged from the compressor. The pitot tube pump may additionally unload the refrigerant pump for producing refrigerant under pressure. Refrigerant under pressure is supplied to the plain bearing to maintain the necessary hydrostatic pressure in the plain bearing. The refrigerant pump is in particular supplied via a collecting container which is arranged geodetically above the refrigerant pump. The backpressure pump conveys the refrigerant discharged from the compressor, in particular, into a collecting container. The collecting container is in particular embodied as a closed container in which a pressure can build up.

The refrigerant pump is specifically regulated in terms of pressure and volume flow and in terms of temperature by the heat exchanger, so that bearing losses are minimized.

Pitot tube pumps have a fixedly disposed pitot tube or also a pitot tube which is immersed in a liquid rotating at high speed (pitot tube pressure principle). When the liquid enters the fixed pitot tube, the velocity can be converted to pressure.

The pitot tube pumps are in particular each supplied via an accumulation tank which extends around the respective support shaft and is embodied and arranged such that the refrigerant present in the compressor collects in the accumulation tank when the compressor is in operation. No further measures are therefore required for conveying the refrigerant into the accumulator tank and the refrigerant can also be discharged particularly efficiently, and the pitot tube pump can build particularly high pressures, which enables particularly good support of the refrigerant pump.

The refrigerant used for cooling may be located in a predetermined region within the compressor. Furthermore, the accumulation tank is arranged radially completely outside, in particular with respect to the respective support shaft, inside said predetermined region, so that the refrigerant put in rotation collects in the cooling tank without further measures.

For example, in each pitot tube, the immersion depth in the refrigerant ring produced by centrifugal force in the accumulation tank is specifically adjusted by the curved tube end of the pitot tube via the rotation of the pitot tube during installation at a gap distance from the bottom of the accumulation tank, so that the amount of refrigerant delivered by the pitot tube pump is always balanced by the number and positioning of the pitot tube pumps, wherein the accumulation tank is filled with the outflowing refrigerant of the refrigerant slide bearings and forms a refrigerant ring in the accumulation tank by centrifugal force, said refrigerant ring having an accumulation tank refrigerant radius on the surface.

In one embodiment of the invention, the compressor is designed as a two-shaft rotary extrusion press, which has a first spindle rotor which is rotatable about a first support shaft and a second spindle rotor which is rotatable about a second support shaft, the first spindle rotor and the second spindle rotor being supported by means of a rolling bearing, wherein the rolling bearing is protected against contact with the refrigerant by a protective gas supply. It is thus advantageously possible to use technically mature and cost-effective rolling bearings without the risk of the lubricant in the form of grease or oil of the rolling bearing being washed off or diluted. For example, nitrogen may be used as the shielding gas.

The protective gas is supplied into the space adjoining the rolling bearing, which space may be referred to as a so-called side chamber.

In one embodiment of the invention, the compressor has an intermediate chamber from which the supplied protective gas is discharged and to which the evaporated refrigerant is supplied, so that a mixture of protective gas and evaporated refrigerant is discharged or drawn off from the intermediate chamber. The supply of vaporized refrigerant causes the pressure of the protective gas-refrigerant-vapor mixture to rise, which results in a small consumption of protective gas.

In one embodiment of the invention, the compressor has a barrier vapor chamber, to which the refrigerant is supplied and evaporated there, which communicates with the intermediate chamber. In the barrier vapor chamber, for example, a brush seal wetted with refrigerant is used, which is wetted in particular with the warmer condensed refrigerant. The thermal energy required for evaporation is generated by the friction of the brushes on the rotating support shaft. Thus, the evaporated refrigerant can be very easily produced to be supplied into the intermediate chamber.

In one embodiment of the invention, the intermediate space is supplied with protective gas by means of a flow resistance on the side chamber side and/or evaporated refrigerant by means of a flow resistance on the working chamber side. Thus, the consumption of protective gas and/or evaporated refrigerant can be advantageously reduced. Flow resistance may also be referred to as a conduction braking system. The conduction braking system can be designed, for example, as a narrow gap, preferably with flow-interrupting resistance, such as a plurality of as sharp grooves as possible in series.

Here, in the side chamber p_SIn the intermediate chamber p_NRelative to the pressure p in the working chamber of the compressor_AIs adjusted so that the following pressure conditions p apply_S＞p_A＞p_N. Maintaining the pressure condition ensures that no refrigerant can enter the side chamber and thus no refrigerant can come into contact with the rolling bearing.

In one embodiment of the invention, the hot working machine has a recirculation device, wherein a mixture of protective gas and evaporated refrigerant discharged from the intermediate space is supplied to the recirculation device, and the recirculation device separates the mixture into protective gas and refrigerant. Thus, the discharged mixture can be reused, enabling low-cost operation of the hot working machine. The mixture is recirculated in a recirculation device, for example by simple condensation, in such a way that the individual constituents can be separated off well due to the distinctly different condensation temperatures. The desired components condense and may deposit depending on the partial pressure. Subsequently, the components can preferably be used further, i.e. in particular the refrigerant produced is returned to the refrigerant circuit again.

The above object is also achieved by a method for operating a hot working machine having an evaporator, a condenser, a compressor, a throttle mechanism, in which method the above-mentioned refrigerant is used as the refrigerant.

Drawings

Further embodiments of the invention emerge from the description and the drawings. Embodiments of the invention are illustrated in simplified form in the accompanying drawings and described in detail in the following description. Wherein:

fig. 1 shows a longitudinal section through a spindle rotor of a two-shaft rotary extrusion press with a sliding bearing;

fig. 2 shows a longitudinal section through the overall system of the displacement compressor and the sliding bearing in the stationary embodiment;

FIG. 3 shows an enlarged view of the inlet area of the two-shaft rotary extruder of FIG. 1;

FIG. 4 shows an enlarged view of the exit region of the two-shaft rotary extruder of FIG. 1;

fig. 5 shows in longitudinal section a part of a spindle rotor of a two-shaft rotary extrusion press with a rolling bearing arrangement;

fig. 6 shows in longitudinal section a part of a spindle rotor of an alternative two-shaft rotary extrusion press with a rolling bearing arrangement;

FIG. 7 shows a schematic view of a hot working machine having a two-shaft rotary extruder with slide bearings; and

fig. 8 shows a schematic representation of a hot working machine with a two-shaft rotary extrusion press with rolling bearings.

Detailed Description

Fig. 1 shows a schematic longitudinal section through the spindle rotors 3, 2 and applies in accordance with a characteristic aspect of the invention to both the 3z spindle rotor 3 and the 2z spindle rotor 2, so that the reference designations 3, 2 are selected on the spindle rotors. Given axial force F_axThe axial force is determined as a pressure difference Δ p ═ p in each spindle rotor during operation by the compressor₂-P₁But is generated and taken up by the axial refrigerant sliding bearing 7. The so-called "bearing gap" as the gap height in the plain bearing gap 6.s is in the range of a few μm, for example in the range of 15 to 35 μm in the case of a plain bearing gap radius of R.A ═ 20 mm. Ceramic is preferably selected as the material for the plain bearing bush 6.b, and the mating surface 6.g on the fixed support shaft is selected so that friction and wear are minimal.

In the illustration shown, the pressure refrigerant inlet 16 on the outlet side flows first to the motor shaft refrigerant cooling 4.a and then via pressure refrigerant supplies 7z and 6z to the axial refrigerant slide bearing 7 and the radial refrigerant slide bearing 6, wherein the amount of refrigerant required for each bearing is obtained by the number and cross section of these supplies. However, for some applications it is of course also possible that the motor refrigerant for the shaft refrigerant cooling 4.a has its own inlet and outlet and that the pressure refrigerant supplies 7z and 6z, for example for the axial refrigerant slide bearing 7 and the radial refrigerant slide bearing 6, are separate if, for example, the refrigerant temperature of the refrigerant slide bearing has to meet certain conditions and the temperature requirements of the motor cooling and the refrigerant slide bearing differ greatly from each other. Accordingly, the illustrations shown are merely exemplary.

The illustrated rotor internal cooling 10 is necessary, depending on the application, only when there are special requirements on the component heat balance, since the part of the rotating inner wall through which the refrigerant flowing from r.m to R.R evaporates already conducts significant heat out of the rotor internal space.

The inlet region is shown in more detail in fig. 3 and the outlet region is shown in more detail in fig. 4.

Fig. 2 shows, by way of example, a longitudinal section through the overall volumetric compressor system in a fixed embodiment with the spindle rotor pairs 2 and 3 in the surrounding compressor housing 1 and the fixed through-running support shaft 5 of each spindle rotor 2, 3, which are supported on both sides both at the inlet 1.1 and at the outlet 1.2 by means of a shaft support 8 on the compressor housing 1.

In the design of the drive motor 4, the aim is always fulfilled that the refrigerant flows to the accumulation tank 9.s due to the centrifugal force, in contrast to the pitot tube 9 of the refrigerant discharge at each spindle rotor end. Therefore, the motor gap radius r.m is always smaller than the radius of the refrigerant to the accumulation tank, i.e.: r.m < R.R, especially throughout the refrigerant flow path. This condition is satisfied in fig. 2 for an exemplary 3-tooth spindle rotor 3, but is not satisfied for the purposes of demonstration on a 2z rotor 2 by showing the following r.m > R.R case there, for example when a very high-power electric motor 4 is required. Then, a corresponding siphon connection 18 is provided for discharging the refrigerant on the motor rotor 4.2, wherein the discharge opening 18 is passed througha ensures that no residual refrigerant collects in the motor gap between the motor stator 4.1 and the motor rotor 4.2 and therefore an inadmissible friction is produced in the motor region by the unavoidable residual refrigerant in the motor region flowing out or partially evaporating via the outlet openings 18 a. The entire electric machine 4 is under pressure p₁And thus a good heat removal is achieved due to the higher evaporation enthalpy, so that the efficiency of the electric machine 4 is improved.

Has the advantages ofIs shown folded to show the cylindrical transition area on the compressor housing 1 and in this preferably cylindrical area on the compressor housing 1 serves for the division between the evaporator chamber 13 and the condenser chamber 14.

The adjustment of the pressure and the volume flow at the refrigerant pump 11 is illustrated via arrows extending through the symbol marks for the refrigerant pump. In addition to the pressure and the volume flow, the respective refrigerant flow is then also regulated by the heat exchanger 16.W in terms of the temperature level at each operating point. The following designations apply here:

WL denotes the refrigerant supplied to the refrigerant sliding bearings 6 and 7,

Δ h represents a height difference of the collecting chamber 15 above the refrigerant pump 11.

MK denotes the refrigerant used for the motor cooling 4.a,

S.W denotes the system refrigerant used to accomplish the refrigerant task,

w.i denotes refrigerant for injection into the working chamber,

W.C denotes the condensed refrigerant from the condenser chamber 14.

By using a portion of this condensed refrigerant as "raindrop forest" R.T direct contact condensation after its external heat dissipation in order to maximize surface area, the condensed refrigerant W.C is directed for the generally desired "direct condensation" for dissipating heat to the external heat exchanger 16. C. In this fig. 2, for illustration reasons, the "raindrop forest" R.T in the condenser chamber 14 is shown simplified on one side only, but is implemented well in the entire condenser chamber 14.

The problem of preventing freezing of the condensed refrigerant W.C to be cooled on the external heat exchanger 16.C is preferably solved in that the remaining condensed refrigerant still present in the line in the inoperative state flows back, for example, into the largely frost-resistant inner region and/or a sufficient expansion region is obtained, which does not lead to material damage as a result of ice formation by expansion.

The following applies in principle to the selected names:

an inlet side with a subscript 1 and an outlet side with a subscript 2, and a sequence subscript 2 for a 2z rotor and a sequence subscript 3 for a 3z rotor, whereby the following designations apply for the respective pressure refrigerant delivery of each main shaft rotor and each pressure side:

z.1.2 ═ refrigerant supply to the 2z rotor on the inlet side.

Z.1.3 ═ refrigerant supply to the 3z rotor on the inlet side.

On the outlet side, the supply of 6z refrigerant as a partial flow of the pressure refrigerant 16 is adapted to:

z.2.2 ═ refrigerant supply to the 2z rotor on the outlet side.

Z.2.3 ═ refrigerant supply to the 3z rotor on the outlet side.

In the pressurized refrigerant 16 shown on the outlet side 1.2, each spindle rotor needs to be distinguished by the following names:

16.2 — pressure refrigerant supplied to the 2z rotor 2.

16.3 ═ pressure refrigerant supplied to the 3z rotor 3.

The division between each spindle rotor 7z and 6z is made by the cross section and the number of bores at the time of introduction. By the adjustability of each refrigerant flow with respect to volume flow, pressure and temperature, the most efficient, respectively minimal, overall energy requirement of the operating mode is achieved during operation. In the following fig. 3 and 4, the two main shaft rotor end sections, i.e. the inlet side and the outlet side, are also shown enlarged.

As an exemplary sectional view in fig. 3 of the detail enlargement of fig. 1, a radial refrigerant slide bearing 6.1 with a pressure refrigerant supply 6, z.1 and 6.z is shown in the inlet region 1.1 for the 2z rotor 2 as well as for the 3z rotor 3, which has a slide bearing gap 6.s of a support length a.L of only a few μm thickness, which is at least 3 to 5 times smaller than the slide bearing radius R.A.

Furthermore, a gap distance s.r set at the pitot tube end 9e for pitot tube positioning is shown in order to adjust the conveyed pitot tube refrigerant with respect to pressure and quantity at each pitot tube 9 by means of the immersed cross section with a known rotational speed dependency, wherein each pitot tube 9.s is preferably immersed in a plurality of pitot tubes 9 on the circumference.

The distance Δ from the dripping nose 8.n ensures that the leakage refrigerant is again supplied to the accumulation tank 9.s, depending on the installation orientation of the compressor_。

As is shown in fig. 4 by way of example as an enlarged view in fig. 1 for the outlet region 1.2, the supplied pressure refrigerant 16 flows first to the motor shaft refrigerant cooling 4.a and then as the pressure refrigerant supply 7z to the axial refrigerant slide bearing 7 and as the pressure refrigerant supply 6z to the radial refrigerant slide bearing 6.2 on the outlet side.

The axial refrigerant sliding main bearing 7.1 bears an axial force F with a bearing seat 7.2 by means of a bearing ring 7.3 which is fixed in position and fixed to a support_axTo fix the axial position of each spindle rotor in the longitudinal axial direction of the rotor.

The motor shaft refrigerant cooling 4.a can of course alternatively also be embodied as a separate circuit by an additional inner tube for separate introduction and removal, and the pressure refrigerant supply 6z and 7z for the axial refrigerant slide bearing and the radial refrigerant slide bearing on the outlet side can be carried out separately, independently of the motor shaft refrigerant cooling 4.a, for example if special temperature requirements are to be met.

In addition to the description of fig. 1 to 4, the following reference number list and reference number list contain further explanations of the individual components:

list of reference numerals of figures 1-4:

1 compressor housing having a pressure p₁1.1 and with a pressure p₂Outlet side 1.2.

At the inlet side, the distance between the axes of the spindle rotors is at least 15% greater than at the outlet side, wherein,

the compressor housing will preferably have a pressure p at the same time₁And evaporation temperature t₀And an evaporator chamber 13 having a pressure p₂And a condensation temperature t_cThrough the condenser chamber 14, which is preferably cylindrical in this regionThe shell shape is divided, wherein the compressor shell cooled by the cooling flow 1.K for some applications is preferably provided with a partition 1.i with respect to the condenser chamber 14.

1.1 pressure p in operation₁Lower compressor inlet side

1.2 pressure p in operation₂Lower compressor outlet side

K shell cooling flow

I housing partition

2 spindle rotor, preferably with a two-tooth gas-conveying external thread, preferably made of aluminium alloy, abbreviated to "2 z rotor" and supported at each outer end on its own support shaft 5 by means of a refrigerant slide bearing bush 6.

A 3-spindle rotor, preferably with a three-tooth gas-conveying external thread, preferably made of aluminium alloy, abbreviated to "3 z rotor" for short, and supported at each outer end on its own support shaft 5 by means of a refrigerant plain bearing bush 6.

An external rotor motor 4, which is designed as a drive for each spindle rotor and is preferably designed as a synchronous motor, is positioned between two spindle rotor bearings 6 in the rotor interior below the gas feed external thread root circle, wherein the motor cable 4.K is led out of the compressor via a central bore in the support shaft 5, and also via an electronic motor pair synchronization device 20 for the contactless operation of the spindle rotor pair during operation

4.1 Motor stator comprising a motor cable 4.K and a preferably cast motor winding, wherein the stator laminations are rotatably and positionally fixedly mounted on each support shaft 5, preferably under a pressure p₁And the motor loss heat is removed by the motor shaft cooling 4.a through the pressurized refrigerant flow 16.

4.2 electric machine rotors, which are connected in a rotationally fixed manner to the respective spindle rotor 2, 3, are preferably designed with permanent magnets, which have an inner radius r.m and accordingly ensure a centrifugal force.

A motor shaft refrigerant cooling part

K motor cable

5 support fixed/fixed support shafts which are fixed continuously over the entire rotor length for each spindle rotor and are fixed on each side by shaft mounts 8.1 and 8.2 which are supported on the compressor housing 1, wherein, for targeted gap adjustment, locking nuts 5.W on each end of the support shafts 5 and/or clamping disks between the shaft mounts 8 and the compressor housing 1 are preferredS achieve axial positioning of each spindle rotor in the compressor housing.

S clamping disk

5.W lock nut

A radial refrigerant slide bearing as a slide bearing with process refrigerant as a lubricating medium for absorbing axial forces of the spindle rotor, wherein the rotor-fixed rotary slide bearing shell 6.b has a shorter support length a.L, wherein "shorter" means smaller than the sliding bearing radius R.A in the case of a slide bearing gap 6.s and thus preferably approximately at least 3 to 5 times smaller, and preferably has a specially adapted mating surface 6.g on the support shaft 5 and a pressure refrigerant supply 6.z, wherein preferably a ceramic material is selected as the slide bearing material.

6.1 radial refrigerant sliding bearing, which is located on the compressor inlet side 1.1 at a pressure p1,

6.2 radial refrigerant sliding bearing, which is located on the compressor outlet side 1.2 at a pressure p2,

b plain bearing shoes arranged rotationally fixed on each end of the respective spindle rotor 2, 3

G fitting surface on support shaft 5 fixed to the support

S sliding bearing gap between the sliding bearing shell 6.b and the mating surface 6.g

Z pressure refrigerant supply to radial refrigerant slide bearing

7 axial refrigerant sliding bearing for absorbing axial force of each main shaft rotor

7.1 axial refrigerant sliding main bearing for absorbing axial forces which are generated during operation of the compressor due to the pressure difference Δ p2-p1 and by gravity in accordance with the stationary/flat installation of the compressor.

7.2 axial refrigerant sliding bearing for axial rotor relative positioning and as bearing for axial refrigerant sliding main bearing 7.1, wherein pressure p1 is exerted at this bearing location on the smaller inner diameter and pressure p2 is obtained on the outer diameter, i.e. the necessary pressure separation is achieved with a preferably continuous support shaft 5.

7.3 a support ring fixedly connected to the support shaft, which support ring has a pressure refrigerant supply 7.z to each axial plain bearing face, wherein the respective amount of pressure refrigerant is adjusted in a specific manner for each refrigerant plain bearing by the cross section and the number of these supplies.

Z pressure refrigerant supply for axial refrigerant sliding bearing

8 serve to fix and accommodate the shaft support of each support shaft end, wherein the support 8.2 is formed on the compressor housing 1 on the outlet side of the support shaft end and 8.1 is formed on the inlet side by a bracket 8.K, in order to achieve a passage for the transport medium, in particular at the inlet 1.1.

K cantilever

8.1 Inlet side cantilever

8.2 outlet side cantilever

N dropping nose

9 pitot tube with an accumulation groove 9.s for returning 9.r bearing lubrication refrigerant discharged from the plain bearing for collecting refrigerant through a through-flow opening 9.d, which through-flow opening 9.d passes refrigerant and refrigerant vapor from the rotor inner shaft space, which pitot tube is constructed with a centrifugal refrigerant ring into which a curved pitot tube end 9.e is purposefully sunk, wherein the amount 9.r of refrigerant to be returned to the collecting container 15 is adjusted by the number, cross section and corresponding immersion depth of the pitot tube, wherein furthermore leakage refrigerant is supplied to the drip nose of the accumulation groove 9.s by a distance Δ and the amount of refrigerant to be supplied is adjusted by immersion of different depths and corresponding cross-sectional designs, wherein the curved pitot tube end 9.e is particularly capable of being mounted and positioned, in particular, immersion depths with a gap distance s.r from the bottom of the tank can be achieved in a targeted manner.

D through-flow opening

End of e-skin pipe

R refrigerant return through pitot tube

S 9.s accumulation tank

10 rotor interior evaporator cooling for all applications with special temperature requirements, which is designed in a cylindrical manner at a pressure p1 with a targeted refrigerant supply 10 via a supply pipe 10.r and a steam outlet 10.d on the inlet side 1.1.

D steam outlet

R supply pipe

Z refrigerant supply section

The at least one refrigerant pump 11 is adjusted externally solely by means of a pressurized refrigerant in terms of pressure and volume flow, for example at 7bar at 6 liters/min, in order to supply the plain bearings, wherein usually the axial plain bearings 7 require more refrigerant than the radial plain bearings 6, which is achieved by a design in terms of the diameter and number of the supply openings 6.z and 7.z, wherein the refrigerant pump 11 first supplies the refrigerant plain bearings 6 and 7 with the amount of refrigerant required for the so-called "hydrostatic" lubrication film configuration, in particular at the start-up of the compressor, which is important for radial bearings with stationary shaft and rotating bearing shell, in particular at the start-up, since the dynamic hydraulic lubrication film is built up by the rotary movement, in contrast to the central rotary shaft. The refrigerant pump 11 uses a collecting container 15 which is arranged geodetically above the refrigerant pump 11 with a height difference 6.h, wherein the refrigerant pump 11 is unloaded by the pitot tube pump 9 as the compressor speed increases in such a way that the pitot tube pump 9 builds up more refrigerant pressure as a function of the speed.

The bearing tube for producing the required bending stiffness is selected, in particular, by selecting the material for each spindle rotor rotary unit, for example, as stainless steel, wherein the spindle rotor outer thread, preferably made of an aluminum alloy, bears on the bearing tube on the outside in a rotationally fixed manner and on the inside holds both the refrigerant slide bearing and the motor rotor 4.2 for introducing the drive power into the spindle rotor in order to complete the compressor task.

13 evaporator chamber which is at a pressure p during operation₁And in order to pass the preferredIs held by a compressor cover 13.h on the compressor housing 1 and is provided with insulation 13.i.

H evaporator chamber tank cover

I evaporator compartment insulation

14 condenser chamber which is under pressure p during operation₂And in order to pass the preferredThe manner in which the compressor housing design of (1) is sealed in this area is maintained by a can 14.h on the compressor housing 1.

H condenser chamber pot cover

15 for the process refrigerant, which is geodetically located at Δ h above the refrigerant pump 11, preferably not only for the return refrigerant 9.r, but also for the system refrigerant S.W.

16, delivered by the refrigerant pump 11, and is supplied centrally on the outlet-side end to each support shaft 5, wherein the refrigerant preferably flows first through the motor shaft cooling 4a and then through the supply 7.z to the axial refrigerant slide bearing 7 and through the supply 6.z to the radial refrigerant slide bearing 6.2 on the outlet side on each spindle rotor, wherein on the inlet-side end of each support shaft the refrigerant supply 6, likewise regulated by the refrigerant pump, is provided at the required pressure and volume flow, wherein, depending on the application, the refrigerant temperature of each partial flow is regulated in a targeted manner by the heat exchanger 16.W in order to optimize the power, and wherein, in addition, the refrigerant pump also takes on the refrigerant jet W.i formed by the spray in the compressor working chamber in order to increase the compressor efficiency, wherein the refrigerant pump 11 can be supplied in a targeted manner through the arrows in the symbol for different operating conditions in a volumetric flow, in order to increase the compressor efficiency The quantities and resulting pressures are adjusted, with each heat exchanger 16W in each of the noted pressure refrigerant splits adjusting the refrigerant temperature in each operating point to achieve the minimum total energy requirement.

C heat exchanger for external heat rejection by cooling of condensed refrigerant W.C when "directly condensed", which condensed refrigerant W.C is then returned as "raindrop forest" R.T for direct contact condensation in condenser chamber 14.

W leads in the pressure refrigerant supply to the heat exchanger at:

pressure refrigerant inlet 6, z.1 on the inlet side to radial refrigerant sliding bearing 6.1

Pressure refrigerant inlet 6, z.2 on the outlet side to radial refrigerant sliding bearing 6.2

Pressure refrigerant inlet 7.z to axial refrigerant sliding bearing 7

Pressure refrigerant inlet 16 to the motor shaft refrigerant cooling section

A pressurized refrigerant inlet W.i for injection into the compressor working chamber and also, in a specific application, by means of a targeted cooling refrigerant cooling, to the following locations:

rotor internal cooling unit 10

Housing cooling section 1.K

An emergency synchromesh 17, which, for example, when the power supply is interrupted, although the electric motor-to-spindle rotor synchronizer initially enters into generator mode operation in order to specifically synchronize the lowering between the spindle rotors without mechanical contact, but at lower rotational speeds the kinetic energy is no longer sufficient for supplying power, is responsible for avoiding critical contact between the working chamber flanks of the gas supply external threads of the two spindle rotors 2 and 3, wherein, in the design of the electric motor-to-spindle rotor synchronizer 20, there is also the solution of eliminating, i.e., not completely eliminating, the emergency synchromesh.

A siphon connection 18 is provided for circulating the refrigerant through the motor 4 when the motor is designed to be large, i.e. when r.m > R.R, via the outlet opening 18 to the inlet side. However, in particular in the case of motor designs, the following objectives are preferably achieved: R.M < R.R

19 have a corresponding refrigerant-vapor-compatible vacuum pump for generating a low pressure in the refrigerant system, in particular for evacuating the external gas entering the refrigerant system again when it is not in operation as an evacuation process.

An electronic motor-spindle rotor synchronization device is shown at 20 as a block-shaped cartridge with μ C +2FU, wherein a microcontroller is shown as μ C, which controls two frequency converters known as FUs in a regulated manner for the drive motor 4 for each spindle rotor 2 and 3, so that the two spindle rotors operate in counter-rotation without contact during operation.

List of labels of fig. 1-4:

diameter on the compressor housing 1, preferably in the cylindrical separating region of the evaporator chamber 13 and the condenser chamber 14

a.L between the sliding bearing shell 6.b and the shaft support 8, wherein the value a.L is preferably at least 3 to 5 times smaller than the sliding bearing clearance radius R.A

Δ drip the distance between the nose 8.n and the accumulation tank 9.s in order to supply the accumulation tank 9.s with upright or lying leakage refrigerant depending on the installation direction of the compressor

Δ h geodetically, by which the collecting container 15 is located above the refrigerant pump 11

F_axDue to p₂And p₁The pressure difference between and the more axial force generated by each screw rotor depending on the compressor installation (i.e. perpendicular or coincident with the rotor gravity)

R.A radius in the plain bearing gap 6.s on the radial refrigerant plain bearing 6

R.m inner radius is also the air gap radius of the motor rotor 4.2, which is preferably always smaller than the accumulator tank maximum refrigerant radius R.R

R.R, wherein R.R is preferably no less than r.m, relative to the radius of the accumulator tank refrigerant delivered by the pitot tubes 9 as return 9.r, so that in the motor area the refrigerant is driven under centrifugal force towards each accumulator tank 9.s at the end of each spindle rotor

R.T raindrop forest, surface maximization for direct contact condensation in condenser chamber 14

s.r clearance distance between each pitot tube end 9.e and the bottom of the accumulator tank 9.r

S.W for meeting the core duty of the refrigerant compressor system:

by applying a pressure p₁Lower part absorbs heat in the evaporator chamber 13 to evaporate

In a compressor with two counter-rotating spindle rotors 2 and 3, the refrigerant is brought from a pressure p₁Is compressed to a pressure p₂

Condensation, preferably designed at a pressure p₂Lower in the condenser chamber 14The "direct condensation" of the heat dissipation in (1),

W.C for "direct condensation", is cooled via the external heat exchanger 16.c and subsequently used as a "raindrop forest" R.T in the condenser chamber 14 for the pressure p₂Direct contact condensation of

W.i is injected into the compressor working chamber, preferably as a fine spray and in the region of approximately half the rotor length in the range of + -30%.

Fig. 5 shows an exemplary working chamber shaft sleeve 114, as a so-called "floating" rotor bearing in the case of a single-sided spindle rotor bearing, which is inserted into the spindle rotor body 101, R, preferably via a bearing sleeve 119, in order to increase the critical speed of rotation for bending. In this embodiment, the known rolling bearing 102 is used for a rotor support device, and grease lubrication or oil lubrication of the rolling bearing generally must be protected from a refrigerant having a refrigerant component with a hydroxyl group. For this purpose, except with a pressure p_NIn addition to the intermediate chamber 108, the following components are present:

on the one hand, there is a workspace-side conduction brake system 118.a, in which the leakage refrigerant flow L to be minimized_KMFlows from compressor workspace 110 at pressure pA at shaft sleeve 114, and

in another example, a side-chamber-side conduction brake system 118.b is present, wherein a side-chamber leakage flow L_MSFlowing through the side chamber 104, the pressure p of the side chamber_SBy supplying PG_iAnd adjusted.

By targeted extraction of PG from the intermediate chamber 108 and regulated delivery of PG_iInput into the side chamber 104, the following pressure conditions are continuously satisfied:

p_S＞P_A＞P_N.

in order to make the leakage refrigerant flow L_KMDesirably minimizing, preferably or optionally establishing a KM DEG C in the cabin side conduction brake system 118.a_zA barrier vapor chamber 117 is provided, wherein KM DEG is passed_zThe regulation of the supply quantity makes it possible to specifically regulate the leakage refrigerant flow L_KMThe amount of (c). The barrier vapor chamber 117 is shown in more detail in fig. 6.

Fig. 6 shows an exemplary illustration of a simple working chamber shaft sleeve 114 in the case of a spindle rotor bearing with a grease-lubricated or oil-lubricated double-sided roller bearing 102, wherein a brush seal 112 with KM ° is shown in greater detail in a barrier steam chamber 117_zSupply and leakage refrigerant flow L_KM. In this case, the KM DEG is supplied in a targeted manner_zThe volume increase by evaporation is rapid, in that the thermal energy required for evaporation is generated by the friction of the brushes and a corresponding pressure increase is brought about by blocking the limited volume of the steam chamber 117, controlled utilization of the leakage flow L in the sense of a reduction or minimization_KMThe desired occlusion effect.

Leaking refrigerant flow L_KMIt is required to be minimized because the loss of the refrigerant KM for the processes of fig. 7 and 8 is thereby minimized. The shielding 116 upstream of the shaft sleeve in the barrier vapor chamber 117 ensures that the excess, not yet evaporated and therefore still liquid refrigerant is sufficiently and simply removed from the shaft sleeve and therefore the evaporation process in the barrier vapor chamber 117 is continued.

Fig. 7 shows a simple illustration of a hot working machine 150 with a KM circuit 152, which has a positive displacement compressor C with plain bearings according to fig. 1 to 4_GLAnd is therefore the simplest design solution with the least expense, in that for C_GLSliding bearing for a compressor of the type having a refrigerant of a refrigerant component with hydroxyl groups as operating refrigerant, also via the refrigerant substream KM_BFor these compressor bearings. In the case of the percentage composition of the refrigerant composition with hydroxyl groups, the adaptation to the application-specific refrigerant is shown greatly simplified by the incoming and outgoing refrigerant partial flows KM% to the refrigerant conditioning device% a, the same being shown in fig. 8.

Fig. 8 shows a simple illustration of a hot working machine 151 with a KM circuit 153, which has a positive displacement compressor C with a rolling bearing_KL. Shown on this compressor type CKL for protectionThe measures required for the components in the side chamber 4, in particular the bearing 2:

-a supply of PGi of said liquid,

-optionally supplying KM °_z

-pumping of PG ·.

Thus, due to the closed side chamber, KM DEG is evaporated in the barrier vapor chamber 117_zAnd may be PGi minimized to be supplied to each side chamber 104. In this case, the pressure p in the side chamber 104 is first monitored_SIn that PG is conducted out, i.e. sucked out, and the pressure conditions are met in the compressor:

p_S＞P_A＞P_N.

the pumped refrigerant component can be condensed in a targeted manner from the PG mixture and used further by means of the recirculation device RC, in that the PG mixture is supplied again to the refrigerant circuit as KMi flow, for example in the region of the throttle device D, if the costs are justified. Similarly, in particular in the case of oil lubrication, it is also possible for the bearing 102 to run with sucked-out lubricant particles, which leak in the side chamber through the flow L_MSIs carried along and after condensation is supplied again to the bearing lubrication in the side chamber 104.

In the hot working machine or refrigerant circuit of fig. 7 and 8, a water-based refrigerant KM is used, which contains a refrigerant component having hydroxyl groups, in particular ethanol. The refrigerant composition is, for example, 30%, but may be lower or higher depending on the application. Instead of ethanol, it is also possible to use other alcohols, in particular monohydric alcohols, such as propane-1-ol.

Therefore, the refrigerant made of a mixture of water and a refrigerant component having hydroxyl groups is used as a refrigerant of a thermal working machine having an evaporator, a condenser, a compressor, and a throttle mechanism.

The hot working machine shown in fig. 7 and 8 is thus a hot working machine with an evaporator, a condenser, a compressor, a throttle mechanism and a refrigerant circuit with a mixture of water and a refrigerant component with hydroxyl groups.

Therefore, in the operation of the hot working machine shown in fig. 7 and 8, a method for operating a hot working machine having an evaporator, a condenser, a compressor, a throttle mechanism is carried out, wherein a refrigerant consisting of a mixture of water and a refrigerant component having hydroxyl groups is used as the refrigerant

In addition to the description of fig. 5 to 8, the following reference number list and reference number list contain further explanations of the individual components:

list of reference numerals of fig. 5-8:

101 has support shafts for rotating the main shaft rotor 101.R of the compressor for compressing refrigerant in the compressor working chamber 110 at respective shaft sleeve 114 at respective working chamber pressure pA

101.R A spindle rotor with a feed external thread, which is fixed as a rotary compressor body on the support shaft 101 in a rotationally fixed manner

102 bearing device for supporting a shaft, for example in the form of a hybrid rolling bearing device, but preferably in the form of a refrigerant sliding bearing device

103 for supporting the shaft 101 with a sensor S for electronic motor-pair synchronization, the motor windings of the stator of the drive motor preferably being cast

104 has a pressure p_SIs closed in a gas-tight manner by the housing component 105 and is connected to the compressor working chamber 110 only by the shaft sleeve 114, wherein at least the bearing arrangement 102 is present in the side chamber, and for each support shaft 101 the drive motor 103 also has a sensor S in the case of an electronic motor-pair synchronization arrangement

105 housing member to air-tightly enclose the side chamber 104

106 for preventing harmful gas from flowing through the bypass holes of the supporting device 102

107 cable sleeves, air-tight

108 has a pressure p between the side chamber 104 and the compressor working chamber 110_NFor discharging PG

109 supply a shielding gas probe. As PG_iBy blowing airPreferably into the bypass aperture 106

110 compressor working chamber of rotary compressor for compressing refrigerant

Discharge of 111PG so that leakage refrigerant flow L_KMIs regulated

112 shaft seal, preferably as a brush seal, for sealing shaft bushing 114 between working chamber 110 and side chamber 104, with the purpose of minimizing leakage refrigerant flow

113 KM °_zPreferably as pure water to the barrier vapor chamber 117

114 shaft sleeve supporting shaft 101 as a connection between side chamber 104 and compressor working chamber 110

115, in particular in the barrier vapor chamber 117_KM

116 shielding means as multiple protection of the supporting means against possible liquid fraction and suppressing influence from KM ° at the shaft sleeve_zExcess, i.e. not yet evaporated, refrigerant of the supply

117 for L_KMAttenuated at KM °_zThe supplied barrier steam chamber is, for example, specifically realized by the shaft seal 112 using the volume increase due to limited space, i.e. evaporation in the barrier steam chamber

118 the conduction braking system or the flow resistance for increasing the flow resistance of the shaft sleeve can be implemented, for example, as narrow gaps, preferably with flow-interrupting resistance, such as connecting a plurality of grooves as sharply as possible in series, blocking steam chambers, piston rings, thread seals up to centrifugal seals

A conducting braking system or flow resistance work Ra

118.b flow resistance of the conduction brake system or side chamber side

119 bearing sleeve for accommodating the bearing 102 in the spindle rotor 101.R in the case of a so-called "floating" spindle rotor bearing

The label lists of fig. 5-8:

KM refrigerant, where n ═ is at the following positions in the circuit as indicated by the usual directional arrows:

a KM after leaving evaporator A before entering compressor C

B KM after leaving compressor C and before entering condenser B

c KM after leaving condenser B before entering throttle D

D after leaving the throttle D before entering the evaporator a

A at the process temperature T₀Having heat absorptionEvaporator of

B at a process temperature T_CLower has an exothermCondenser of

C compressor, preferably embodied as a positive displacement compressor, in which the power consumption P is_anAs follows:

C_GLpositive displacement compressor with sliding bearing

C_KLPositive displacement compressor with rolling bearing, grease lubrication or oil lubrication

At the following pressure values in the compressor C:

p_Apressure in front of the respective shaft sleeve leading to the side chamber 4 in the working chamber 10

p_NThe pressure of each working chamber shaft sleeve 14 in the intermediate chamber 8

p_SPressure in the compressor-side chamber 4

D throttling mechanism

% A KM control device for percentage refrigerant compositions in such a way that the refrigerant components having hydroxyl groups are adapted to the respective requirements and conditions in a specific manner according to the application

PG_iA purge gas inlet as a supply PG for protective gas for elements in the side chamber 4, as a virtually permanent suction process, the bleed being regulated by means of a quantity regulation of the purge gas outletLeakage flow L_KMPreferably via KM °_zThe supply quantity is adapted to the evaporation in the barrier steam chamber 17 and thus to the flow resistance

PG degree circulation gas outlet

L_KMLeakage refrigerant flow through the service compartment side conduction brake system 18

L_MSSide chamber leakage flow through side chamber side conduction brake system 18

KM_BRefrigerant split supply part for compressor C with sliding bearing device_GLKM provisioning of

KM°_zA supply, preferably water, to the barrier steam chamber 17

KMi supply of refrigerant KM, e.g. near throttle D, is primarily as a leakage refrigerant flow L out of each shaft sleeve 14_KMIs compensated for

A KM% refrigerant split stream for adjusting percent refrigerant composition by supplying and returning to KM adjusting device

RC is used for recycling the extracted PG mixture by condensing out the components

The S-electron motor is coupled to a sensor in the synchronization device.