EP0641978A1

EP0641978A1 - Improvements in and relating to refrigeration method and apparatus

Info

Publication number: EP0641978A1
Application number: EP94306390A
Authority: EP
Inventors: Stephen Forbes Pearson
Original assignee: Star Refrigeration Ltd
Current assignee: Star Refrigeration Ltd
Priority date: 1993-09-04
Filing date: 1994-08-31
Publication date: 1995-03-08
Anticipated expiration: 2014-08-31
Also published as: EP0641978B1; DE69407699T2; DE641978T1; GB9318385D0; DK0641978T3; DE69407699D1

Abstract

Refrigeration apparatus is capable of operating in i) vapour compression mode or ii) thermosyphon mode. The apparatus defines a refrigerant path includes a compressor (12), a condenser (14), an expansion valve (16) and a chiller (18) where the refrigerant absorbs heat from fluid to be cooled. The refrigeration circuit includes valves (26, 28) configurable for selectively directing refrigerant i) to pass through the compressor (12) and expansion valve (16) or ii) to bypass the compressor and expansion valve. A thermal store (20) is provided and is i) cooled while the apparatus operates in the vapour compression mode and ii) provides a chilling effect during changeover to thermosyphon mode.

Description

This invention relates to a refrigeration apparatus and refrigeration method, and in particular to refrigeration apparatus capable of operating in either a vapour compression mode or a thermosyphon mode.
UK Patent GB 2 233 080 B describes a refrigeration apparatus which may be operated in a mechanical mode, or alternatively in a thermosyphon mode. In the mechanical mode the apparatus operates in a conventional manner utilising a vapour compression cycle, with refrigerant vapour being compressed before being passed through a heat exchanger (condenser) where sensible heat is rejected to the atmosphere from the compressed refrigerant, then passing the resulting condensate through a restriction, typically an expansion valve, and finally passing the expanded and cooled refrigerant to a heat exchanger (evaporator) to absorb heat from a fluid to be chilled. When ambient temperatures are sufficiently low the refrigerant path may be reconfigured to bypass the compressor and the expansion valve such that the only cooling effect experienced by the refrigerant is when the refrigerant is passed through the condenser, the evaporator being located below the condenser such that the refrigerant may circulate without the mechanical assistance normally provided by the compressor. Clearly, operation in the thermosyphon mode is more economical than the mechanical or vapour compression mode.
In a typical refrigerating unit incorporating this feature, several refrigerating systems are arranged so that the fluid to be chilled is passed through the evaporators in series. A number of the systems may cool the fluid by vapour compression operation while other systems operating with warmer inlet fluid may contribute a share of the required cooling by thermosyphon operation. However, such units are expensive and involve high capital costs and in practice are restricted to very large units where stand-by equipment is specified. It has not yet been possible to use an individual two-mode system, as when the system changes from vapour compression refrigeration to thermosyphon refrigeration there is a period of delay while the heat rejection equipment, previously in contact with the compressed (and thus heated) refrigerant, cools to a temperature below that of the fluid being chilled.
It is among the objects of the present invention to provide an apparatus and method which obviate or mitigate this disadvantage.
According to the present invention there is provided refrigeration apparatus capable of operating in i) vapour compression mode or ii) thermosyphon mode, the apparatus defining a refrigerant path comprising:
compression means for compressing a refrigerant;
heat rejection means for cooling the compressed refrigerant;
restriction means for expanding the refrigerant;
chilling means for permitting the absorption of heat by the refrigerant from a fluid to be chilled;
valve means configurable for selectively directing refrigerant i) to pass through the compression means and restriction means or ii) to bypass the compression means and restriction means; and
thermal storage means for i) being cooled while the apparatus operates in the vapour compression mode and ii) providing a chilling effect during changeover to thermosyphon mode.
According to a further aspect of the present invention there is provided a refrigeration method including i) a vapour compression mode or ii) a thermosyphon mode, the method including the steps of:
rejecting heat from a refrigerant;
chilling a fluid with the refrigerant; and

i) when operating in vapour compression mode the method further including the steps of:
- a) compressing the refrigerant;
- b) expanding the refrigerant; and
- c) cooling a thermal storage means; and
ii) when operating in thermosyphon mode the method further including the step of:

The chilled fluid may be the fluid contained within a space to be cooled, for example a refrigerated compartment, but will usually be a liquid, such as water, to be utilised as a cooling medium for a region to be cooled, such as an air conditioned space, which may be remote from the refrigeration apparatus.
Preferably, the thermal storage means i) is cooled by the chilled fluid while the apparatus operates in the vapour compression mode and ii) chills the fluid on changeover to thermosyphon mode.
Preferably also, operation in thermosyphon mode is achieved without any mechanical circulation of the refrigerant, which, in the vapour compression mode, is typically provided by the compression means. In this case the chilling means will be positioned below the heat rejection means. Alternatively, if some other arrangement is desired, refrigerant circulation means may be provided for use in the thermosyphon mode.
Thus, the present invention allows changeover from compression mode to thermosyphon mode without the period of delay that occurs in conventional two-mode systems as the heat rejection means cools to a temperature below that of the fluid being chilled; during this changeover period the present invention provides for chilling of the fluid by the thermal storage means.
In a preferred embodiment, with selection of appropriate thermal storage means, the invention may operate at full capacity in the vapour compression mode irrespective of cooling load, any excess capacity being utilised to cool the thermal storage means. On the thermal storage means reaching a condition where it cannot be cooled further, the fluid temperature will drop sharply, allowing a thermostatic switch to reconfigure the valve means to provide the thermosyphon mode. The thermal storage means then begins to chill the fluid, preventing an immediate rise in temperature of the fluid and allowing time for the apparatus to adjust to thermosyphon mode.
Preferably also, the thermal storage means contains a phase change material which will absorb or reject heat at a substantially constant temperature. Substances suitable for use in such means include acetic acid and lactic acid.
These and other aspects of the present invention will now be described, by way of example, with reference to the accompanying drawing, which illustrates, in schematic form, refrigeration apparatus in accordance with a preferred embodiment of the present invention.
The apparatus includes ducting 10 which partially defines a refrigerant path around which refrigerant is cycled in either i) a mechanical or vapour compression mode or ii) a thermosyphon mode. In vapour compression mode the refrigerant is first subject to compression by a positive displacement compressor 12, from which the high pressure refrigerant passes to heat rejection means in the form of a condenser 14, which is exposed to ambient air. Following condensing and cooling in the condenser 14, the refrigerant passes to restriction means in the form of an expansion valve 16, which causes a sufficient portion of the refrigerant to vaporise to reduce the temperature of the remaining liquid to that consistent with the lower pressure. The expanded and cooled refrigerant is then passed to a heat exchanger in the form of a chiller 18 where the refrigerant absorbs heat from fluid to be cooled. On exit from the chiller 18, the refrigerant, now in the form of low pressure vapour, returns to the compressor 12.
The chiller 18 forms part of a secondary cooling circuit around which a fluid, such as water, is circulated. Following chilling, the water passes through a thermal store 20 which contains a phase change material. The water then passes through a region to be cooled 22, before returning to the chiller 18, circulation of the fluid around the cooling circuit being achieved by means of a fluid pump 24.
The refrigeration circuit includes a three-way valve 26 and a two-way ball valve 28, and for operation in the vapour compression mode the valves 26, 28 are configured such that refrigerant is passed through the compressor 12 and the expansion valve 16. However, when the ambient temperature is particularly low (that is lower than the temperature of the water to be chilled), the valves 26, 28 may be configured to bypass the compressor 12 and valve 16, such that the refrigerant is cooled solely by ambient air as it passes through the condenser 14. Also, the chiller 18 is positioned below the condenser 14 and the ducting 10 is arranged such that the refrigerant will circulate in this thermosyphon mode without mechanical assistance, thus minimising the energy consumption of the apparatus.
While operating in vapour compression mode, the compressor 12 may operate at full capacity, irrespective of the cooling load, any excess cooling of the water being absorbed by the thermal store 20, in which the excess cooling capacity is utilised to solidify a liquid, at constant temperature. When the phase change material has completely solidified there will be a sharp decrease in the temperature of the water, which may be detected by a thermostat 30 which operates to switch the apparatus from vapour compression mode to thermosyphon mode, that is by shutting down the compressor 12 and reconfiguring the valves 26, 28 to bypass the compressor 12 and the expansion valve 16. Initially, on switching from vapour compression mode to thermosyphon mode, the refrigerant in the ducting 10 downstream of the compressor 12 and upstream of the expansion valve 16 will be at a higher temperature than the water and it takes some time for the refrigerant and the condenser hardware and ducting to be cooled to a level where its temperature is lower than that of the water. Also, in order for circulation of refrigerant to take place without mechanical assistance, the temperature of the refrigerant in the condenser 14 must fall below the temperature at the outlet from the chiller 18, the reverse of the situation in the vapour compression mode. During this transition period the water is chilled by the thermal store 20, as the phase change material in the store is melted by the circulating water.
From the above description it will be seem that this embodiment of the invention provides an arrangement in which refrigeration apparatus capable of operating in a thermosyphon mode may be utilised on an individual basis, and not necessarily as part of a larger system. Further, the provision of the thermal store 20 allows the system to be operated at full capacity in vapour compression mode, which is of course more efficient than operating at part capacity.
The present invention may be utilised in a wide variety of applications, but is particularly useful where the cooling load is to be maintained at a relatively high temperature, such as in air conditioning systems for building which chill the ceilings of rooms and corridors. Such air conditioning is particularly suitable for thermosyphon cooling techniques as the chilled ceilings must be kept at a temperature higher than the dew point of the room air. These relatively high temperatures allows the associated refrigeration apparatus to operate in thermosyphon mode for a significant number of hours per year.
It will be clear to those of skill in the art that the above described embodiment is merely exemplary of the present invention and that various modifications and improvements may be made thereto without departing from the scope of the invention.

Claims

Refrigeration apparatus capable of operating in i) vapour compression mode or ii) thermosyphon mode, the apparatus defining a refrigerant path comprising:
compression means (12) for compressing a refrigerant;
heat rejection means (14) for cooling the compressed refrigerant;
restriction means (16) for expanding the refrigerant;
chilling means (18) for permitting the absorption of heat by the refrigerant from a fluid to be chilled;
valve means (26, 28) configurable for selectively directing refrigerant i) to pass through the compression means (12) and restriction means (16) or ii) to bypass the compression means (12) and restriction means (16); and
thermal storage means (20) for i) being cooled while the apparatus operates in the vapour compression mode and ii) providing a chilling effect during changeover to thermosyphon mode.
The apparatus of claim 1 in which the chilled fluid is a cooling medium for a region (22) to be cooled.
The apparatus of claim 1 or claim 2 in which the thermal storage means (20) is i) arranged to be cooled by the chilled fluid while the apparatus operates in the vapour compression mode and ii) arranged to chill the fluid during changeover to thermosyphon mode.
The apparatus of claims 1, 2 or 3 in which the chilling means (20) is positioned below the heat rejection means (14 ) to allow operation in thermosyphon mode without any mechanical circulation.
The apparatus of claims 1, 2 or 3 wherein refrigerant circulation means is provided for use in the thermosyphon mode.
The apparatus of any one of the preceding claims wherein the thermal storage means (20) is arranged such that the apparatus is operable at full capacity in the vapour compression mode irrespective of cooling load, any excess capacity being utilised to cool the thermal storage means (20).
The apparatus of claim 6 further comprising a thermostatic switch (30) to reconfigure the valve means (26, 28) from the vapour compression mode to the thermosyphon mode on the thermal storage means (20) reaching a condition where it cannot be cooled further.
The apparatus of any one of the preceding claims wherein the thermal storage means (20) contains a phase change material which will absorb or reject heat at a substantially constant temperature.
The apparatus of claim 8 wherein the phase change material is one of acetic acid or lactic acid.
A refrigeration method including i) a vapour compression mode or ii) a thermosyphon mode, the method including the steps of:
rejecting heat from a refrigerant;
chilling a fluid with the refrigerant; and
i) when operating in vapour compression mode the method further including the steps of:
a) compressing the refrigerant;

b) expanding the refrigerant; and

c) cooling a thermal storage means; and

ii) when operating in thermosyphon mode the method further including the step of:
a) providing a chilling effect using the thermal storage means, at least during initial changeover from vapour compression mode to thermosyphon mode.
The method of claim 10 wherein the chilled fluid provides a cooling medium for a region to be cooled.
The method of claim 10 or claim 11 wherein the thermal storage means is i) cooled by the chilled fluid in vapour compression mode and ii) chills the fluid during changeover to thermosyphon mode.
The method of claim 10, 11 or 12 in which, in the thermosyphon mode, the refrigerant circulates without any mechanical circulation.
The method of any one of claims 10 to 13 wherein operation in vapour compression mode is at full capacity irrespective of cooling load, any excess capacity being utilised to cool the thermal storage means.
The method of claim 14 wherein the mode of operation changes from i) vapour compression mode to ii) thermosyphon mode on the thermal storage means reaching a condition where it cannot be cooled further.
The method of any one of claims 10 to 15 wherein the thermal storage means absorbs or rejects heat at substantially constant temperature.