Compressor assembly for heat pumps, air conditioners, refrigerators, and other applications with gas compression

Abstract

To achieve a more effective compressor design for heat pumps, air conditioners, refrigerators, and other gas-compression applications, it is proposed that the refrigerant (14) be compressed through a membrane tube (7) encased in magnetic ferrofluid (1). A peristaltic, linear motion pattern is generated by the controller (13), which controls the electromagnets (4) and their armatures (6) via changeover switches (5). This results in a linear, direct, quiet, and non-turbulent compression of the refrigerant (14), which increases the efficiency for such an application.

Description

Field of invention:

[0001] The invention relates to a compressor (30) which realizes low-loss thermodynamic processes by using alternating magnetic fields and magnetic forces. Background of the invention:

[0002] The state of the art in heat pumps and thermodynamic compressors is to use piston or scroll compressors to compress the refrigerant. Due to the nature of the system, there are many mechanically moving parts, resulting in losses due to friction, sealing, and mechanical noise. Furthermore, suboptimal flow dynamics due to turbulence and changes in the direction of the refrigerant contribute to these losses. The present invention achieves efficient, linearly guided, and quiet compression with few mechanically moving parts. Lubrication of the components is not required. The seal is effectively ensured by compressing a membrane tube (7).

[0003] The present invention improves the disadvantages of the prior art described above, resulting in increased efficiency. When this compressor (30) is used, e.g., in heat pumps, the COP (coefficient of performance) is improved. The refrigerant (14) is compressed in a membrane tube (7) surrounded by magnetic ferrofluid (1). The controller (13), which actuates the electromagnets (4) with their armatures (6) via changeover switches (5), generates a peristaltic, linear movement pattern that can be easily sealed by the elastic membrane tube (7).

[0004] In the Fig. Figures 5 to 11 illustrate a possible peristaltic, linear movement pattern. The electromagnets (4) with their armatures (6) are located in the ferrofluid (1). At the end of the membrane tube (7), the last opposing electromagnets (4) with their armatures (6) act as a type of valve, allowing the compressed and heated refrigerant (14) to escape in a controlled manner. The magnetic properties of the ferrofluid (1) are utilized, with temporary magnetic solidification occurring due to the magnetic flux (24) in the ferrofluid. This allows the membrane tube (7) to build up the counterforce for compressing the refrigerant (14) via the electromagnets (4) with their armatures (6) due to the temporarily solidifying ferrofluid (1). During compression by the electromagnets (4) with their armatures (6), the control (13) switches on a current pulse from the respective capacitor circuits (31).The use of capacitor circuits (31) is more efficient because the current pulse is only needed during the compression stroke of the armatures (6) and not to hold them. When the opposing armatures (6) are in the closed position, they additionally attract each other, since the remaining air gap is virtually zero due to the ferrofluid (1).

[0005] The compression of the membrane tube (7) can be carried out with a different number of electromagnets (4) with their armatures (6), see Fig. 3. Furthermore, ferrofluids (1) have good thermal conductivity and heat capacity, which increases efficiency in this application, since the heat generated by the ohmic losses of the electromagnets (4) is transferred via the ferrofluid (1) into the coolant (14).

[0006] To better distribute the force on the armatures (6) of the electromagnets (4), a cap (20) is positioned on the armature (6) in the compression direction. The cap (20) is spherically shaped and made of magnetic metal. Due to the shape of the cap (20), the force vectors (23) do not only act perpendicular to the closing direction of the armatures (6), which leads to better force introduction at the armature (6) of the electromagnet (22), see Fig. 4. The magnetic flux is transmitted through the magnetic metal of the cap (20).

[0007] In the Fig. Figure 4 shows that a mechanical air gap is formed between the electromagnet (4) and the armature (6), which is filled with ferrofluid (1). This results in a magnetic air gap of zero, which has a positive effect on the efficiency of the electromagnetic system. A magnetic seal (21) is arranged at the end of the electromagnet (4) to retain the ferrofluid (1). The magnetic seal (21) is formed by an annular bulge in the housing (2), which is filled with ferrofluid and lies in the permanent magnetic field of the armature (6).

[0008] Fig. Figure 1 shows the compressor (30) in a heat pump application. The electromagnets (4), armature (6), membrane hose (7), and ferrofluid (1) are installed in the non-magnetic housing (2). The system pressure P1 is established in the housing (2) via the pressure line (3). The controller (13) is connected to the temperature and pressure sensors (10), the expansion valve (11), and the changeover switches (5) for controlling the heat pump's flow. Heat pipes (8, 9) are used to optimize the heat flow between the heat exchangers (16, 17, 18, 19) at the heat pump's outlet and inlet.

[0009] From the Fig. Figures 5 to 11 illustrate how the compressor (30) can be controlled. The top view shows how multiple compressors (30) can be connected and controlled. In the variant shown here, the pressure increase achieved would be calculated as follows: P1×V1=Pn×Vn Vn=V1×(1−n−1nmax) Pn=P11(1−n−1nmax) nmax=6 P1=1×P1 P2=1.2×P1 P3=1.5×P1 P4=2×P1 P5=5×P1 P6=6×P1 Where: P 1..6 = pressure V 1..6 = Volume of the cavities in the membrane tube n 1..6 = number of compression cycles.

[0010] The invention is explained in more detail with reference to the accompanying drawings.

[0011] They show: Fig. 1 shows the compressor (30) in linear section Fig. 2 shows the compressor (30) in section CC top view Fig. 3 shows the cross sections AA, BB from Fig. 1 with different configurations of the electromagnet (4) arrangements Fig. 4 shows the detailed view of the electromagnets (4) Fig. 5 Compaction process; compaction pressure is P1=1×P1 Fig. 6 Compression process; compression pressure is P2=1.2×P1 Fig. 7 Compaction process; compaction pressure is P3=1.5×P1 Fig. 8 Compaction process; compaction pressure is P4=2×P1 Fig. 9 Compaction process; compaction pressure is P5=5×P1 Fig. 10 Compaction process; compaction pressure is P6=6×P1 Fig. 11 Compression process; compression pressure is P6=6×P1 and refrigerant outlet (14) List of reference symbols: 1 Ferrofluid 2 housings 3 pressure line 4 Electromagnet 5 changeover switches 6 armature (permanent magnet) 7 Membrane hose 8 heat pipes (outgoing) 9 Heat Pipe (incoming) 10 Temperature, pressure sensor 11 Expansion valve 12 Electrical connection of the electromagnet connected to the changeover switch of the opposite electromagnets 13 PLC control 14 Refrigerants 15 DC power supply 16 Heat exchanger input (external) 17 Heat exchanger output (external) 18 Heat exchanger inlet (internal) 19 Heat exchanger output (internal) 20 cap 21 Magnetic seal 22 Closing force of the electromagnet 23 force vectors 24 Magnetic flux 25 pressure (P1 ... P6) 26 Outside air - heat source 27 Solar thermal energy - heat source 28 Geothermal energy - heat source 29 Heating 30 compressor 31 Capacitor circuit

Claims

[1] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by that the compression of the refrigerant (14) occurs through a membrane tube (7) surrounded by magnetic ferrofluid (1). A peristaltic, linear movement pattern is generated by the control system (13), which activates the electromagnets (4) with their armatures (6) via changeover switches (5). The electromagnets (4) with their armatures (6) are located in the ferrofluid (1). At the end of the membrane tube (7), the last two opposing electromagnets (4) with their armatures (6) act as a type of valve, allowing the compressed and heated refrigerant (14) to escape in a controlled manner. [2] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized bythat the magnetic properties of the ferrofluid (1) are used to create a temporary magnetic solidification due to the magnetic effect in the ferrofluid (1). This allows the membrane tube (7) to build up the counterforce for compressing the refrigerant (14) via the electromagnets (4) with their armatures (6) due to the temporarily solidifying ferrofluid (1). Furthermore, ferrofluids (1) have good thermal conductivity and heat capacity, which increases efficiency in this application because the heat generated by the ohmic losses of the electromagnets (4) is transferred via the ferrofluid (1) into the refrigerant (14). As an alternative to ferrofluids (1), other magnetic fluids such as liquid metals (at room temperature), liquid metal coated magnetic particles or similar can be used. [3] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized bythat several compressors (30) can be connected to each other and optimally controlled. As an example, Fig. 5 to Fig.

11. [4] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by that a mechanical air gap is formed between the electromagnet (4) and the armature (6), which is filled by the ferrofluid (1). This results in a magnetic air gap of zero, which has a positive effect on the efficiency of the electromagnetic system. [5] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized bythat a magnetic seal (21) is arranged at the end of the electromagnet (4) to retain the ferrofluid (1). The magnetic seal (21) is formed by an annular bulge in the housing (2) that is filled with ferrofluid and held in place by the permanent magnetic field of the armature (6). [6] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by that a cap (20) is positioned on the armature (6) of the electromagnet (4) in the compression direction. The cap (20) is spherically shaped and made of magnetic metal. Due to the shape of the cap (20), the force vectors (23) do not only act perpendicular to the closing direction of the armature (6), which leads to better force introduction at the armature (6) of the electromagnet (22), see Fig.

4. The magnetic flux is transmitted through the magnetic metal of the cap (20). [7] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by that heat pipes (8, 9) are used to optimise the heat flow between the heat exchangers (16, 17, 18, 19) at the outlet and inlet of the heat pump. [8] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by The control system (13) connects a current pulse from the respective capacitor circuits (31) during compression by the electromagnets (4) with their armatures (6). This is more efficient because the current pulse is only needed during the compression stroke of the armatures (6) and not to hold the armatures (6). When the opposing armatures (6) are in the closed position, they additionally attract each other, since the remaining air gap is virtually zero due to the ferrofluid (1). [9] The compressor design for heat pumps, air conditioners, refrigerators, and other gas compression applications is characterized by that the compression of the membrane tube (7) can be carried out with a different number of electromagnets (4) with their armatures (6), see Fig. 3.

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