EXPANSION VALVE FOR A VAPOUR COMPRESSION SYSTEM WITH REVERSIBLE FLUID FLOW

CROSS REFERENCE TO RELATED APPLICATIONS

This application is entitled to the benefit of and incorporates by reference subject matter disclosed in its entirety in International Patent Application No. PCT/DK2012/000019 filed on Mar. 8, 2012 and Danish Patent Application No. PA 2011 00157 filed Mar. 9, 2011.

FIELD OF THE INVENTION

The present invention relates to an expansion valve for a vapour compression system, such as a refrigeration system, an air condition system or a heat pump. The expansion valve of the invention is switchable between a first state and a second state, and is suitable for use in a vapour compression system in which the flow of fluid medium can be reversed, e.g. a vapour compression system which can be switched between an air condition mode and a heat pump mode. The present invention further relates to a vapour compression system comprising such an expansion valve.

BACKGROUND OF THE INVENTION

Vapour compression systems, such as refrigeration systems, air condition systems or heat pumps, normally comprise a compressor, a condenser, an expansion device, e.g. in the form of an expansion valve, and an evaporator arranged along a refrigerant path. Refrigerant circulates the refrigerant path and is alternatingly compressed and expanded. Heat exchange takes place in the condenser and the evaporator, and it is thereby possible to provide cooling or heating to a closed volume, e.g. a room or a refrigerated compartment or box.

In some cases it is desirable that the vapour compression system is capable of selectively operating as an air condition system or as a heat pump. Thereby it is possible to provide cooling to a closed volume during warm or hot seasons, and to provide heating to the closed volume during cold seasons, using the same vapour compression system. Such vapour compression systems comprise two heat exchangers which are both capable of operating as an evaporator and as a condenser, depending on which mode is selected for the vapour compression system. One heat exchanger is arranged to exchange heat with air present in the closed volume while the other heat exchanger is arranged to exchange heat with outside air.

Thus, when an indoor temperature which is lower than the outdoor temperature is desired, the heat exchanger arranged to exchange heat with air in the closed volume operates as an evaporator, and the heat exchanger arranged to exchange heat with the outside air operates as a condenser. Thereby the vapour compression system operates as an air condition system, and cooling is provided for the closed volume. Similarly, when an indoor temperature which is higher than the outdoor temperature is desired, the fluid flow in the vapour compression system is reversed, the heat exchanger arranged to exchange heat with air in the closed volume operates as a condenser, and the heat exchanger arranged to exchange heat with the outside air operates as an evaporator. Thereby the vapour compression system operates as a heat pump, and heating is provided for the closed volume.

In order to allow the vapour compression system to be operated selectively as an air condition system or as a heat pump, it is necessary to design the vapour compression system in such a manner that expanded refrigerant can be selectively supplied to both of the heat exchangers when they operate as evaporators, and in such a manner that refrigerant is allowed to flow substantially unrestricted from both of the heat exchangers when they operate as condensers.

In some prior art vapour compression systems this has been obtained by providing two expansion devices, one for each heat exchanger, and ensuring that a substantially unrestricted refrigerant flow is allowed to pass the expansion devices when the corresponding heat exchanger is operating as a condenser, e.g. by means of bypass flow paths.

In alternative prior art compression systems, a reversible thermostatic expansion valve (TXV) has been provided between the two heat exchangers, the reversible thermostatic expansion valve being capable of supplying expanded refrigerant to each of the heat exchangers. However, a thermostatic expansion valve should preferably be controlled on the basis of the superheat of refrigerant leaving the evaporator. However, since both of the heat exchangers may operate as evaporators, depending on the selected mode of the vapour compression system, it is not possible to arrange a sensor or a bulb for the thermostatic expansion valve in a position which always provides the superheat of refrigerant leaving the evaporator. Accordingly, in these prior art systems, the sensor or bulb is arranged at a non-optimal position which provides a reasonable measure for the superheat, regardless of the mode of the vapour compression system. Thus, the thermostatic expansion valve is controlled in a non-optimal manner.

DESCRIPTION OF THE INVENTION

It is an object of embodiments of the invention to provide an expansion valve for a reversible flow vapour compression system, the expansion valve being easy to control in an accurate manner.

It is a further object of embodiments of the invention to provide a vapour compression system allowing a reversed fluid flow using fewer components than prior art vapour compression systems.

It is an even further object of embodiments of the invention to provide a vapour compression system allowing a reversed fluid flow, while maintaining a simple design of the vapour compression system.

According to a first aspect the invention provides an expansion valve for a vapour compression system, the expansion valve comprising a first valve member, a second valve member and a third valve member, said valve members being arranged in such a manner that relative movements at least between the first valve member and the second valve member, and between the first valve member and the third valve member are possible, the expansion valve being switchable between a first state in which an opening degree of the expansion valve is determined by the relative position of the first valve member and the second valve member, and a second state in which an opening degree of the expansion valve is determined by the relative position of the first valve member and the third valve member, wherein the expansion valve is automatically moved between the first state and the second state in response to a change in direction of fluid flow through the expansion valve, wherein the second valve member defines a first fluid passage, and the third valve member defines a second fluid passage, wherein end portions of the first valve member are arranged adjacent to the fluid passages and are intended for being moved into the first fluid passage and the second fluid passage so that an opening degree of the expansion valve is defined by the fluid passages and the end portions in combination, wherein biasing means are arranged between the first valve member and the second valve member, and between the first valve member and the third valve member, respectively, and wherein the biasing means bias the first valve member in a direction away from the second valve member and in a direction away from the third valve member, and wherein an increase in differential pressure across the expansion valve results in the first valve member, in the first state, being moved towards the second valve member or, in the second state, being moved towards the third valve member, the increase in differential pressure resulting in a larger part of the fluid passages being blocked by the end portions, and in the opening degree of the expansion valve thereby being decreased.

In the present context the term ‘vapour compression system’ should be interpreted to mean any system in which a flow of fluid medium, such as refrigerant, circulates and is alternatingly compressed and expanded, thereby providing either refrigeration or heating of a volume. Thus, the vapour compression system may be a refrigeration system, an air condition system, a heat pump, etc. The vapour compression system, thus, comprises a compressor, an expansion device, e.g. in the form of an expansion valve, and two heat exchangers, one operating as a condenser and one operating as an evaporator, arranged along a refrigerant path.

When arranged in a vapour compression system, the expansion valve is arranged in the refrigerant path immediately upstream relative to the evaporator. Thereby the expansion valve expands the refrigerant and controls the supply of expanded refrigerant to the evaporator.

It should be noted that, even though the expansion valve of the invention is very suitable for use as expansion device in a vapour compression system, it is not ruled out that the expansion valve is used in other systems. For instance, the expansion valve of the invention may be used in an absorption refrigeration system, where the refrigerant is not compressed mechanically. The evaporated, gaseous refrigerant is dissolved in a liquid and pumped into a regenerator, where the refrigerant is thermally separated from the liquid due to the different boiling points between refrigerant and liquid. The gaseous refrigerant is liquefied in a condenser and expanded to a lower pressure by means of throttling devices such as the expansion valve of the invention.

The expansion valve comprises a first valve member, a second valve member and a third valve member. The valve members are arranged in such a manner that relative movements between the first valve member and the second valve member are possible. Furthermore, relative movements between the first valve member and the third valve member are possible. The second valve member and the third valve member may be arranged substantially fixed relative to each other. Alternatively, relative movements between the second valve member and the third valve member may also be possible. The relative movability of the valve members may be obtained by allowing the first valve member to move, while the second valve member and/or the third valve member is/are fixed relative to the remaining parts of the expansion valve. As an alternative, the second valve member and the third valve member may be allowed to move, while the first valve member is arranged substantially fixed relative to the remaining parts of the expansion valve. As another alternative, all three valve members may be allowed to move relative to the remaining parts of the expansion valve, and relative to each other.

The expansion valve is switchable between a first state and a second state. In the first state an opening degree of the expansion valve is determined by the relative position of the first valve member and the second valve member. In the second state an opening degree of the expansion valve is determined by the relative position of the first valve member and the third valve member. Thus, when the expansion valve is in the first state the opening degree of the expansion valve, and thereby mass flow of refrigerant passing through the expansion valve, may be altered when the relative position of the first valve member and the second valve member is changed. Similarly, when the expansion valve is in the second state the opening degree of the expansion valve, and thereby the mass flow of refrigerant passing through the expansion valve, may be altered when the relative position of the first valve member and the third valve member is changed.

The expansion valve is automatically moved between the first state and the second state in response to a change in direction of fluid flow through the expansion valve. Thus, when the fluid flow through the expansion valve is in a first direction, the expansion valve will be in the first state, i.e. the opening degree of the expansion valve is determined by the relative position of the first valve member and the second valve member. If the fluid flow through the expansion valve is reversed, the expansion valve is automatically moved to the second state, and the opening degree of the expansion valve is thereby determined by the relative position of the first valve member and the third valve member.

Accordingly, the expansion valve of the invention is very suitable for being used in a vapour compression system in which the fluid flow is reversible, e.g. a vapour compression system which is selectively operable in an air condition mode or a heat pump mode. As described above, such a vapour compression system normally comprises two heat exchangers, the two heat exchangers each being capable of operating as a condenser or as an evaporator, depending on the operating mode of the vapour compression system. The expansion valve of the invention can be arranged in the vapour compression system in such a manner, that when the fluid flow through the expansion valve is in a first direction, the expansion valve is in the first state, and expanded refrigerant is delivered by the expansion valve to a first heat exchanger. Similarly, when the fluid flow through the expansion valve is in a second, reverse direction, the expansion valve is in the second state, and expanded refrigerant is delivered by the expansion valve to the second heat exchanger. Thus, the heat exchangers ‘switch role’ when the fluid flow through the expansion valve is reversed. Furthermore, this switch is performed automatically in response to the change in direction of the fluid flow through the expansion valve. Thereby it is ensured that the expansion valve is always operated in accordance with the selected mode of the vapour compression system, without requiring complicated control of the expansion valve.

The expansion valve may have a first, substantially fixed opening degree when the expansion valve is in the first state, and a second, substantially fixed opening degree when the expansion valve is in the second state, the second opening degree being distinct from the first opening degree. According to this embodiment, the opening degree of the expansion valve is not controlled while the expansion valve is in the first state or the second state. However, since the second opening degree is distinct from the first opening degree, the opening degree of the expansion valve is changed abruptly when the direction of fluid flow through the expansion valve is changed, and the expansion valve is thereby moved from the first state to the second state or from the second state to the first state. Thus, the expansion valve is operated at one, substantially fixed opening degree when the fluid flow through the expansion valve is in a first direction, and at another, substantially fixed opening degree when the fluid flow through the expansion valve is in another, reversed direction.

One or more valve parts may be automatically moved in response to changes in a differential pressure across the expansion valve, the opening degree of the expansion valve thereby being automatically altered in response to changes in the differential pressure across the expansion valve. According to this embodiment, the opening degree of the expansion valve is controlled while the expansion valve is in the first or second state, respectively. Furthermore, the opening degree of the expansion valve is altered automatically in response to changes in the differential pressure across the expansion valve. Thus, when the differential pressure across the expansion valve is changed, one or more valve parts, preferably one or more of the valve members, is/are automatically moved. Thereby the relative position between the first valve member and the second valve member, and/or the relative position between the first valve member and the third valve member is/are changed. Since the opening degree of the expansion valve is determined by the relative position of the first valve member and the second valve member, or the relative position of the first valve member and the third valve member, depending on whether the expansion valve is in the first or the second state, the opening degree of the expansion valve is also altered automatically when the differential pressure across the expansion valve changes.

Thus, the opening degree of the expansion valve is automatically adjusted to correspond to a differential pressure which is presently occurring across the expansion valve. This allows the expansion valve to be operated with one opening degree at low differential pressures and with another opening degree at high differential pressures. This is, e.g., desirable when the expansion valve is arranged in a vapour compression system comprising a compressor being capable of operating at two different capacity levels. The two different capacity levels results in two distinct differential pressure levels across the expansion valve. The opening degree of the expansion valve according to this embodiment of the invention is automatically altered when the compressor capacity is changed, thereby allowing the vapour compression system to be operated in an optimal manner at both compressor capacity levels. Furthermore, since the opening degree of the expansion valve is altered automatically in response to changes in the differential pressure, the adjustment of the opening degree is obtained without the requirement of complicated control of the expansion valve, e.g. of the kind which is used for controlling thermostatic expansion valves. Thereby close to optimal operation of the expansion valve can be obtained at low costs.

The first valve member and the second valve member may in combination form a first expansion valve, and the first valve member and the third valve member may in combination form a second expansion valve. According to this embodiment the expansion valve defines two separate expansion valves, one formed by the first valve member and the second valve member, and one formed by the first valve member and the third valve member. Thus, according to this embodiment, the expansion valve is a double valve. When the expansion valve is in the first state, the opening degree of the expansion valve is determined by the expansion valve formed by the first valve member and the second valve member, and when the expansion valve is in the second state, the opening degree of the expansion valve is determined by the expansion valve formed by the first valve member and the third valve member. For each of the expansion valves, a valve seat may be formed on one valve member and a valve element may be formed on the other valve member. When the valve members are moved relative to each other, the valve seat and the valve element are also moved relative to each other, thereby changing the opening degree of the expansion valve.

The expansion valve comprises biasing means arranged to mechanically bias the first valve member and the second valve member in a direction away from each other, and/or to mechanically bias the first valve member and the third valve member in a direction away from each other. The biasing means may be in the form of mechanical biasing means, such as one or more compressible springs arranged to push the relevant valve members away from each other, or a member made from a resilient material, or any other suitable kind of mechanical biasing means. As an alternative, the biasing means may be magnetic biasing means arranged to push the relevant valve members away from each other. The relevant valve members are moved against the biasing force of the biasing means when they are moved towards each other. In the case that the valve members are automatically moved in response to changes in the differential pressure across the expansion valve as described above, the biasing means may be selected and/or adjusted in such a manner that desired relative movements of the valve members are obtained in response to changes in the differential pressure across the expansion valve during normal operation of the expansion valve, thereby obtaining that the opening degree of the expansion valve is altered in a desired manner.

The second valve member and the third valve member each define a fluid passage, and the first valve member may comprise a first protruding element being arranged in the fluid passage of the second valve member when the expansion valve is in the first state, and a second protruding element being arranged in the fluid passage of the third valve member when the expansion valve is in the second state. According to this embodiment, the fluid passages of the second and third valve members may each form a valve seat, and the protruding elements of the first valve member may each form a valve element, and the valve seats and the valve elements may pair-wise form expansion valves.

The first protruding element and/or the second protruding element may have a geometry which provides an opening degree of the expansion valve which is a known function of the relative position of the first valve member and the second and/or third valve member. According to this embodiment, a given relative position of the first valve member and the second and/or third valve member results in a well defined and known opening degree of the expansion valve. Thereby the control of the expansion valve can easily be performed in an accurate manner.

Alternatively or additionally, the first protruding element and/or the second protruding element may have a substantially conical shape. According to this embodiment, the opening degree of the expansion valve is gradually decreased as a protruding element is moved further into a corresponding fluid passage. Similarly, the opening degree of the expansion valve is increased as a protruding element is moved further outwards relative to a corresponding fluid passage.

Alternatively or additionally, the first protruding element and/or the second protruding element may be provided with one or more grooves, at least one groove defining a dimension which varies along a longitudinal direction of the protruding element. Since at least one groove defines a dimension which varies along a longitudinal direction of the protruding element, the part of the corresponding fluid passage being blocked by the protruding element is determined by the position of the protruding element relative to the fluid passage along the longitudinal direction. This is an advantageous embodiment because it is relatively easy to provide such grooves with high accuracy, and thereby the correspondence between the relative position of the valve members and the opening degree of the expansion valve is determined with high accuracy. The varying dimension may, e.g., be the depth or the width of the groove.

The second protruding element may be arranged outside the fluid passage of the third valve member when the expansion valve is in the first state and/or the first protruding element may be arranged outside the fluid passage of the second valve member when the expansion valve is in the second state. When a protruding element is arranged outside a corresponding fluid passage, fluid is allowed to flow substantially unrestricted through the fluid passage. Thus, according to this embodiment, when the expansion valve is in the first state, fluid is allowed to flow substantially unrestricted through the fluid passage of the third valve member, while the fluid passage of the second valve member and the first protruding element in combination control the fluid flow through the expansion valve and ensure that the refrigerant is expanded. Alternatively or additionally, when the expansion valve is in the second state, fluid is allowed to flow substantially unrestricted through the fluid passage of the second valve member, while the fluid passage of the third valve member and the second protruding element in combination control the fluid flow through the expansion valve and ensure that the refrigerant is expanded.

As an alternative, the first valve member may be provided with a first fluid passage and a second fluid passage, and the second valve member and the third valve member may each be provided with a protruding element, each protruding element being adapted to be arranged in a fluid passage of the first valve member, similarly to the situation described above. As another alternative, the first valve member may be provided with a fluid passage and a protruding element, while the second/third valve member is provided with a protruding element and the third/second valve member is provided with a fluid passage. In this case the protruding element of the second/third valve member is adapted to be arranged in the fluid opening of the first valve member, and the protruding element of the first valve member is adapted to be arranged in the fluid passage of the third/second valve member, similarly to the situation described above.

According to a second aspect the invention provides a vapour compression system comprising a compressor, a first heat exchanger, a second heat exchanger and an expansion valve according to the first aspect of the invention, the compressor the first heat exchanger, the expansion valve and the second heat exchanger being arranged along a refrigerant path.

It should be noted that a person skilled in the art would readily recognise that any feature described in combination with the first aspect of the invention could also be combined with the second aspect of the invention and vice versa.

The first heat exchanger may operate as an evaporator and the second heat exchanger as a condenser when the expansion valve is in the first state, and the first heat exchanger may operate as a condenser and the second heat exchanger as an evaporator when the expansion valve is in the second state. According to this embodiment the two heat exchangers ‘switch role’ when the expansion valve is switched between the first state and the second state. Accordingly, the vapour compression system is of the kind which is capable of selective operating in an air condition mode or a heat pump mode, and the expansion valve is adapted to deliver expanded refrigerant to both of the heat exchangers, depending on which mode is selected. Thereby, the vapour compression system is capable of being selectively operated in air condition mode or in heat pump mode, without the requirement of two separate expansion valves, and while maintaining a simple structure and design of the vapour compression system.

Thus, the expansion valve may be arranged to supply expanded refrigerant to the first heat exchanger when the expansion valve is in the first state, and to supply expanded refrigerant to the second heat exchanger when the expansion valve is in the second state.

According to one embodiment, at least the first heat exchanger, the second heat exchanger and the expansion valve may be arranged in a compact unit. Arranging the heat exchangers close to each other in the compact unit allows the expansion valve to be arranged in such a manner that it is capable of supplying expanded refrigerant directly to both of the heat exchangers.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described in further detail with reference to the accompanying drawings in which

FIGS. 1
a-3b are diagrammatic views of various prior art vapour compression systems,

FIGS. 4
a and 4b are diagrammatic views of a vapour compression system according to an embodiment of the invention,

FIGS. 5-11 illustrate an expansion valve according to a first embodiment of the invention, and

FIGS. 12-18 illustrate an expansion valve according to a second embodiment of the invention.

DETAILED DESCRIPTION

FIGS. 1
a and 1b are diagrammatic views of a first prior art vapour compression system 1. The vapour compression system 1 comprises a compressor 2, a first heat exchanger 3 and a second heat exchanger 4. A reversible thermostatic expansion valve 5 is arranged between the heat exchangers 3, 4 in such a manner that the thermostatic expansion valve 5 is capable of supplying expanded refrigerant to both of the heat exchangers 3, 4, depending on the direction of fluid flow in the vapour compression system 1. A four way valve 6 is operable to control the direction of the fluid flow in the vapour compression system 1.

Thus, when the four way valve 6 is in a first position, illustrated in FIG. 1a, refrigerant is compressed by the compressor 2. The compressed refrigerant is supplied to the second heat exchanger 4, which in this case operates as a condenser. Accordingly, the refrigerant is at least partly condensed in the second heat exchanger 4, the refrigerant leaving the second heat exchanger 4 being at least partly in a liquid state. The refrigerant is then supplied to the reversible thermostatic expansion valve 5, where it is expanded before being supplied to the first heat exchanger 3, which in this case operates as an evaporator. Accordingly, the refrigerant is at least partly evaporated in the first heat exchanger 3, the refrigerant leaving the first heat exchanger 3 being in a substantially gaseous state. Finally, the refrigerant is supplied to the compressor 2, and the cycle is repeated.

Similarly, when the four way valve 6 is in a second position, illustrated in FIG. 1b, the fluid flow in the vapour compression system 1 is reversed. Accordingly, refrigerant delivered by the compressor 2 is supplied to the first heat exchanger 3, which in this case operates as a condenser, and refrigerant delivered by the reversible thermostatic expansion valve 5 is supplied to the second heat exchanger 4, which in this case operates as an evaporator.

When a thermostatic expansion valve is used in a vapour compression system 1 for expanding refrigerant before supplying the refrigerant to an evaporator, it is desirable to operate the thermostatic expansion valve in such a manner that an minimal superheat of the refrigerant leaving the evaporator is obtained. The superheat is defined as the difference between the temperature of the refrigerant leaving the evaporator and the dew point of the refrigerant leaving the evaporator. Thus, a high superheat indicates that all of the refrigerant was evaporated in the evaporator, and that energy has been used for heating the evaporated, gaseous refrigerant. Thus, the potential refrigerating capacity of the evaporator is not utilised in an optimal manner in this case. On the other hand, a superheat which is zero indicates that liquid refrigerant may be passing through the evaporator and entering the suction line. Liquid refrigerant in the suction line introduces the risk that liquid refrigerant reaches the compressor 2. This may cause damage to the compressor 2 and is therefore undesirable. Accordingly, it is normally attempted to operate the thermostatic expansion valve in such a manner that a low, but positive, superheat is obtained. To this end, the superheat of refrigerant leaving the evaporator is often monitored and used as a control parameter for the thermostatic expansion valve. The superheat is often measured by means of one or more sensors arranged immediately downstream relative to the evaporator.

As described above, in the vapour compression system 1 of FIGS. 1a and 1b, the first heat exchanger 3 as well as the second heat exchanger 4 may operate as an evaporator, depending on the position of the four way valve 6. Therefore, the reversible thermostatic expansion valve 5 is operated on the basis of superheat measurements performed by one or more sensors 7 arranged in the refrigerant path between the four way valve 6 and the compressor 2. Accordingly, the measurements performed by the sensor(s) 7 represent the superheat of refrigerant flowing in the suction line, regardless of whether the first heat exchanger 3 or the second heat exchanger 4 operates as an evaporator. However, this has the consequence that the sensor(s) is/are arranged relatively far from the outlet of the evaporator, and the obtained superheat value therefore does not reflect the superheat of the refrigerant leaving the evaporator in an accurate manner. Therefore the control of the reversible thermostatic expansion valve 5 is not very accurate, and the vapour compression system 1 is not controlled in an optimal manner, since the superheat measured by the sensor(s) 7 is influenced by heat flux from the four way valve 6.

FIGS. 2
a and 2b are diagrammatic views of a second prior art vapour compression system 1. The vapour compression system 1 of FIGS. 2a and 2b is very similar to the vapour compression system 1 of FIGS. 1a and 1b, and it will therefore not be described in detail here. Contrary to the vapour compression system of FIGS. 1a and 1b, the vapour compression system 1 of FIGS. 2a and 2b does not comprise a reversible thermostatic expansion valve 5. Instead the vapour compression system 1 of FIGS. 2a and 2b comprises a fixed orifice expansion valve 9 arranged to supply expanded refrigerant to the first heat exchanger 3 and a thermostatic expansion valve 10 arranged to supply expanded refrigerant to the second heat exchanger 4. The opening degree of the thermostatic expansion valve 10 is controlled on the basis of measurements performed by sensor(s) 7 in order to obtain an optimal superheat value when the second heat exchanger 4 operates as an evaporator. The fixed orifice expansion valve 9 is not controlled.

Since the vapour compression system 1 of FIGS. 2a and 2b comprises two expansion valves 9, 10, one for each heat exchanger 3, 4, the component count of the vapour compression system 1 is increased as compared to the vapour compression system 1 of FIGS. 1a and 1b. This increases the manufacturing costs and the complexity of the vapour compression system 1. Since a fixed orifice expansion valve is normally cheaper than a thermostatic expansion valve, using the fixed orifice valve 9 for supplying expanded refrigerant to the first heat exchanger 3 reduces the costs a bit. However, this has the consequence that the supply of refrigerant to the second heat exchanger 3 is not controllable when the first heat exchanger 3 operates as an evaporator.

The vapour compression system 1 of FIGS. 2a and 2b may advantageously be operated in air condition mode when the second heat exchanger 4 operates as an evaporator, i.e. the situation illustrated in FIG. 2b, and in heat pump mode when the first heat exchanger 3 operates as an evaporator, i.e. the situation illustrated in FIG. 2a. This is because it is normally more important to fully utilise the potential refrigeration capacity of the evaporator when the vapour compression system 1 is operated in air condition mode than when the vapour compression system 1 is operated in heat pump mode.

FIGS. 3
a and 3b are diagrammatic views of a third prior art vapour compression system 1. The vapour compression system 1 of FIGS. 3a and 3b is very similar to the vapour compression system 1 of FIGS. 2a and 2b, and will therefore not be described in detail here. However, in the vapour compression system 1 of FIGS. 3a and 3b an additional thermostatic expansion valve 13 is arranged to supply expanded refrigerant to the first heat exchanger 3 when it operates as an evaporator. The thermostatic expansion valve 13 is controlled on the basis of a measured superheat which is obtained by means of one or more sensors 14.

Thus, in the vapour compression system 1 of FIGS. 3a and 3b it is possible to control the supply of refrigerant to both of the heat exchangers in order to obtain a minimal superheat, regardless of the direction of fluid flow in the vapour compression system 1. However, the manufacturing costs of the vapour compression system 1 of FIGS. 3a and 3b are higher than the manufacturing costs of the vapour compression system 1 of FIGS. 2a and 2b.

FIGS. 4
a and 4b are diagrammatic views of a vapour compression system 1 according to an embodiment of the invention. The vapour compression system 1 comprises a compressor 2, a first heat exchanger 3 and a second heat exchanger 4. A four way valve 6 is arranged to control the direction of fluid flow of the vapour compression system 1 in the manner described above with reference to FIGS. 1a and 1b.

An expansion valve 16 is arranged in the refrigerant path between the first heat exchanger 3 and the second heat exchanger 4. Thus, the expansion valve 16 is adapted to supply expanded refrigerant to the first heat exchanger 3 as well as to the second heat exchanger 4, depending the direction of fluid flow in the vapour compression system 1. The expansion valve 16 is of a kind according to an embodiment of the invention, and it could, e.g., be the expansion valve 16 illustrated in FIGS. 5-11 or the expansion valve 16 illustrated in FIGS. 12-18. Accordingly, the expansion valve 16 is switchable between a first state in which the opening degree of the expansion valve 16 is determined by a relative position between a first valve member and a second valve member, and a second state in which the opening degree of the expansion valve 16 is determined by a relative position between the first valve member and a third valve member. The expansion valve 16 is automatically moved between the first state and the second state in response to a change in direction of fluid flow through the expansion valve 16.

Thus, if the direction of fluid flow in the vapour compression system 1 is such that the first heat exchanger 3 operates as an evaporator, i.e. the situation illustrated in FIG. 4a, then the expansion valve 16 is automatically in a state where refrigerant is expanded and supplied to the first heat exchanger 3. Similarly, if the direction of fluid flow in the vapour compression system 1 is such that the second heat exchanger 4 operates as an evaporator, i.e. the situation illustrated in FIG. 4b, then the expansion valve 16 is automatically in a state where refrigerant is expanded and supplied to the second heat exchanger 4. Accordingly, expanded refrigerant can be supplied to both of the heat exchangers 3, 4 using only one expansion valve 16, and it is always ensured that the expansion valve 16 is in the correct state.

Furthermore, the expansion valve 16 may advantageously be of a kind where the opening degree is automatically altered in response to changes in a differential pressure across the expansion valve 16. In this case the opening degree of the expansion valve 16 is controlled in order to obtain an optimal utilisation of the potential refrigeration capacity of the heat exchanger 3, 4 which operates as an evaporator, without the requirement of obtaining a measure for the superheat of the refrigerant leaving the evaporator. Thus, the disadvantages described above with reference to FIG. 1, relating to the position of the sensor(s) 7 are avoided.

It is clear from FIGS. 4a and 4b that the expansion valve 16 of the invention provides a vapour compression system 1 which is much simpler and with fewer components than the prior art vapour compression systems 1 shown in FIGS. 1a-3b.

FIG. 5 is a side view of a first valve member 17 for an expansion valve according to a first embodiment of the invention. The end portions 18 of the first valve member 17 define a substantially conical shape. However, the outermost tips of the end portions 18 are substantially cylindrical.

FIG. 6 is a cross sectional view of the first valve member 17 of FIG. 8 along the line H-H indicated in FIG. 5. The conical shapes of the end portions 18 are clearly visible.

FIG. 7 is a cross sectional view of an expansion valve 16 according to a first embodiment of the invention. The first valve member 17 of FIGS. 5 and 6 is arranged movably inside a cylindrical tube 19. A second valve member 20 and a third valve member 21 are also arranged inside the cylindrical tube 19. The second valve member 20 and the third valve member 21 are not movable relative to the cylindrical tube 19.

The second valve member 20 defines a first fluid passage 22, and the third valve member 21 defines a second fluid passage 23. The end portions 18 of the first valve member 17 are arranged adjacent to the fluid passages 22, 23.

Two compressible springs 24 are arranged between the first valve member 17 and the second valve member 20, and between the first valve member 17 and the third valve member 21, respectively. The compressible springs 24 bias the first valve member 17 in a direction away from the second valve member 20 and in a direction away from the third valve member 21. In FIG. 7 the expansion valve 16 is shown in a rest position where there is no fluid flow through the expansion valve 16. Accordingly, the spring forces of the compressible springs 24 balance out, and the first valve member 17 is arranged at substantially equal distance to the second valve member 20 and the third valve member 21.

FIG. 8 is a cross sectional view of the expansion valve 16 of FIG. 7. In FIG. 8 a fluid flow has been introduced in the expansion valve 16 along a direction from the second valve member 20 towards the third valve member 21, as indicated by arrow 25. Thereby a differential pressure across the expansion valve 16 has been introduced, the pressure at the second valve member 20 being higher than the pressure at the third valve member 21. This has caused the first valve member 17 to be moved in a direction towards the third valve member 21, against the spring force of the compressible spring 24b arranged between the first valve member 17 and the third valve member 21. Thereby the cylindrical part of one of the end portions 18b has been moved into the fluid passage 23 of the third valve member 21, while the other end portion 18a has been moved further away from the second valve member 20. Thereby the cylindrical part of the end portion 18b blocks a part of the fluid passage 23 of the third valve member 21. Accordingly, the fluid flow through the fluid passage 23 is restricted, and the opening degree of the expansion valve 16 is defined by the fluid passage 23 and the end portion 18b in combination.

Small variations in the differential pressure across the expansion valve 16 will result in small movements of the first valve member 17. Thereby the end portion 18b will perform small movements inside the fluid passage 23. However, since the part of the end portion 18b which is arranged in the fluid passage 23 is the cylindrical part, such small movements do not result in changes in the opening degree of the expansion valve 16.

FIG. 9 is a cross sectional view of the expansion valve 16 of FIGS. 7 and 8. In FIG. 9 the differential pressure across the expansion valve 16 has been increased as compared to the situation illustrated in FIG. 8. Thereby the first valve member 17 has been moved even further towards the third valve member 21, and the conical part of the end portion 18b is arranged in the fluid passage 23. Accordingly, a larger part of the fluid passage 23 is blocked by the end portion 18b, i.e. the opening degrblockee of the expansion valve 16 has been decreased.

Since the conical part of the end portion 18b is arranged in the fluid passage, variations in the differential pressure across the expansion valve 16, and thereby movements of the first valve member 17 relative to the third valve member 21, results in changes in the opening degree of the expansion valve 16. Accordingly, in the situation illustrated in FIG. 9, the opening degree of the expansion valve 16 is automatically altered in response to changes in the differential pressure across the expansion valve 16.

FIG. 10 is a cross sectional view of the expansion valve 16 of FIGS. 7-9. In FIG. 10 the fluid flow through the expansion valve 16 has been reversed as compared to the situations illustrated on FIGS. 8 and 9. Thus, in FIG. 10 refrigerant flows through the expansion valve 16 in a direction from the third valve member 21 towards the second valve member 20, as illustrated by arrow 25. Similarly to the situation illustrated in FIG. 8, a differential pressure is thereby introduced across the expansion valve 16. However, in this case the pressure at the third valve member 21 is higher than the pressure at the second valve member 20. This has caused the first valve member 17 to be moved in a direction towards the second valve member 20, against the spring force of the compressible spring 24a arranged between the first valve member 17 and the second valve member 20. Thereby the cylindrical part of the end portion 18a has been positioned in the fluid passage 22 of the second valve member 20, similarly to the situation illustrated in FIG. 8. Thus, the opening degree of the expansion valve 16 is, in this case, determined by the fluid passage 22 and the end portion 18a in combination.

FIG. 11 is a cross sectional view of the expansion valve 16 of FIGS. 7-10. In FIG. 11 the differential pressure across the expansion valve 16 has been increased as compared to the situation illustrated in FIG. 10. Thereby the conical part of the end portion 18a has been moved into the fluid passage 22, similar to the situation illustrated in FIG. 9.

It is clear from FIGS. 7-11 and from the description above, that a change in direction of the fluid flow through the expansion valve 16 automatically results in expansion valve 16 being switched between a state in which the opening degree of the expansion valve 16 is determined by the relative position of the first valve member 17 and the second valve member 20, and a state in which the opening degree of the expansion valve 16 is determined by the relative position of the first valve member 17 and the third valve member 21.

FIG. 12 is a side view of a first valve member 17 for an expansion valve according to a second embodiment of the invention. Each of the end portions 18 of the first valve member 17 is provided with a groove 26. This will be explained in further detail below.

FIG. 13 is a cross sectional view of the first valve member 17 of FIG. 12 along the line H-H indicated in FIG. 12. In FIG. 13 it can be seen that the grooves 26 are tapered along a longitudinal direction of the first valve member 17. Accordingly, the grooves 26 are deepest at a position near the tips of the first valve member 17.

FIG. 14 is a cross sectional view of an expansion valve 16 according to a second embodiment of the invention. The expansion valve 16 of FIG. 14 is similar to the expansion valve 16 of FIGS. 7-11, and it will therefore not be described in detail here. In the expansion valve 16 of FIG. 14, the first valve member 17 arranged inside the cylindrical tube 19 is of the kind shown in FIGS. 12 and 13.

In FIG. 14 the expansion valve 16 is shown in a rest position where there is no fluid flow through the expansion valve 16, similarly to the situation illustrated in FIG. 7. Accordingly, the spring forces of the compressible springs 24 balance out, and the first valve member 17 is arranged at substantially equal distance to the second valve member 20 and the third valve member 21.

FIG. 15 is a cross sectional view of the expansion valve 16 of FIG. 14. In FIG. 15 a fluid flow has been introduced in the expansion valve 16 along a direction from the second valve member 20 towards the third valve member 21, as indicated by arrow 25, similarly to the situation illustrated in FIG. 8. Thus, similarly to what is described above, a differential pressure has been introduced across the expansion valve 16, moving the first valve member 17 in a direction towards the third valve member 21, against the spring force of compressible spring 24b. Thereby the end portion 18b has been introduced into the fluid passage 23 of the third valve member 21, and the fluid flow through the fluid passage 23 has been limited. The fluid flow through the fluid passage 23, and thereby the opening degree of the expansion valve 16, is defined by the dimensions of the groove 26b at the position of the fluid passage 23. As described above, variations in the differential pressure across the expansion valve 16 results in movements of the first valve member 17. Since the groove 26b is tapered along the direction of movements of the first valve member 17, such movements result in changes in the opening degree of the expansion valve 16.

FIG. 16 is a cross sectional view of the expansion valve 16 of FIGS. 14 and 15. In FIG. 16 the differential pressure across the expansion valve 16 has been increased as compared to the situation illustrated in FIG. 15, thereby moving the end portion 18b further into the fluid passage 23. It is clear from FIG. 16 that the groove 26b is now positioned relative to the fluid passage 23 in such a manner that the opening degree of the expansion valve 16 is reduced as compared to the situation illustrated in FIG. 15.

FIG. 17 is a cross sectional view of the expansion valve 16 of FIGS. 14-16. In FIG. 17 the fluid flow through the expansion valve 16 has been reversed, so that fluid flows in a direction from the third valve member 21 towards the second valve member 20, as illustrated by arrow 25. As a consequence, the first valve member 17 has been moved towards the second valve member 20, against the spring force of the compressible spring 24a arranged between the first valve member 17 and the second valve member 20. This has caused a part of the end portion 18a to be introduced into the fluid passage 22 of the second valve member 20. Similarly to the situation described above with reference to FIG. 15, the fluid flow through the expansion valve 16 is thereby restricted, the fluid flow, and thereby the opening degree of the expansion valve 16, thereby being defined by the relative position of the groove 26a and the fluid passage 22.

FIG. 18 is a cross sectional view of the expansion valve 16 of FIGS. 14-17. In FIG. 18, the differential pressure across the expansion valve 16 has been increased as compared to the situation illustrated in FIG. 17, thereby moving the end portion 18a further into the fluid passage 22 and further reducing the opening degree of the expansion valve 16.

It is clear from FIGS. 14-18 and from the description above, that a change in direction of the fluid flow through the expansion valve 16 automatically results in expansion valve 16 being switched between a state in which the opening degree of the expansion valve 16 is determined by the relative position of the first valve member 17 and the second valve member 20, and a state in which the opening degree of the expansion valve 16 is determined by the relative position of the first valve member 17 and the third valve member 21.

It is an advantage that the opening degree of the expansion valve 16 is automatically altered in response to changes in the differential pressure across the expansion valve, due to the tapered grooves 26 provided at the end portions 18 of the first valve member 17, because such grooves can be provided with high accuracy. Accordingly, the opening degree of the expansion valve 16 can easily be controlled in an accurate manner.

EXPANSION VALVE FOR A VAPOUR COMPRESSION SYSTEM WITH REVERSIBLE FLUID FLOW

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CPC

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