JPS5952343B2 - heat pump equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat pump, and particularly to a heat pump device suitable for use in air-conditioning and heating systems.

Heat pump devices that transfer heat from low-temperature areas to high-temperature areas are often used as air-conditioning devices.

In other words, in summer, indoor heat is released outdoors for cooling.
In winter, heating is performed by moving heat indoors from outdoors, but this temperature control generally uses a refrigerant such as Freon gas, which takes advantage of the heating effect when it is compressed and the cooling effect when it expands. .

FIG. 1 is an explanatory diagram showing a heat pump device generally used for air conditioning and heating.
,? It is composed of a compressor C1, a throttle valve, etc.

Compressor A takes in the low-pressure refrigerant gas that has become a gas in evaporator B, compresses it to a high temperature and high pressure state, and sends it to condenser C as it is.

The high-temperature, high-pressure refrigerant gas is cooled in the condenser C, liquefies it, releases heat, and heats the surroundings.

The liquefied refrigerant is depressurized by the throttle valve and expands to evaporator B.
It evaporates and becomes a gas again.

At this time, it absorbs heat from the surrounding area and cools the surrounding area.

The evaporated refrigerant gas is sucked into compressor A again to complete the cycle.

During this cycle, the heat released to the outside by the condenser C is used for heating, and the cooling power generated by the evaporator B is used for air conditioning.

At this time, switching between heating and cooling is performed by changing the flow direction of the refrigerant or the circulating fluid heated and cooled by the refrigerant by operating a valve.

Although vapor compression heat pump devices using the above refrigerant are the most widely used, many problems remain with this refrigerant.

In other words, the refrigerants currently in use have poor refrigerating ability, safety,
None of them satisfy all economical requirements and have some drawbacks.

For example, cheap refrigerants with excellent refrigeration ability are toxic, and relatively safe refrigerants are expensive, so this is not a desirable method.

Therefore, complete leakage prevention is required, which not only complicates the structure but also makes the device itself expensive.

On the other hand, a heat pump device that does not use refrigerant and compresses and expands air to perform air conditioning and heating has been considered, but since adiabatic compression and expansion are performed, efficiency is significantly reduced.

Another major drawback is that a large amount of air must be used to perform the necessary heating and cooling, which significantly increases power consumption.

The purpose of the present invention is to solve the above problems,
Using a multi-stage vane type compressor and expander, the gas is heated or cooled through a heat exchanger during the compression and expansion process to perform compression and expansion in a nearly isothermal state, reducing the power required for compression. The present invention aims to provide a heat pump device that effectively recovers power during the expansion process, is highly efficient, and does not require a refrigerant.

Embodiments of the present invention will be described in detail below with reference to the drawings.

FIG. 2 shows a heat pump device composed of a two-stage compression device 1, a two-stage expansion device 2, a drive device 3, and a heat exchange device 4. As shown in FIG.

The compression device 1 includes a first stage compressor 5 and a second stage compressor 6 (second stage compressor 5).
The first stage compressor 5 has a suction port So, and the second stage compressor 6 has a discharge port D.
Each has one O.

The first stage compressor 5 has an intermediate discharge port DI1. DI 2.
DI3, DI4, and the second stage compressor 6 has an intermediate suction port S21. S22. S23. It is equipped with S24.

These mutually adjacent intermediate discharge ports D11 and DI2, D
Between I2 and DI3, DI3 and DI4 and intermediate inlet S
One or more vanes 71 and 72 are always interposed between 21 and S22, S22 and S23, and S23 and S24, and intermediate discharge ports DI1. DI 2. DI3. DI4 and the corresponding intermediate intake port S21. S22. S23. S2
4 is a group of pipes P11 and P interposed in the heat dissipation device 8.
I3. PI3. Linked by PI3.

The expansion device 2 includes a first stage expander 9 and a second stage expander 10 (
The first stage expander 9 has an air supply port Soo, and the second stage expander 10 has one exhaust port Doo.

The first stage expander 9 has an intermediate exhaust port D31. D32, D33
．． D34, and the second stage expander 10 has an intermediate air supply port S41. S42,543. It is equipped with S44.

These mutually adjacent intermediate exhaust ports D31 and D32, D
One or more vanes 73 and 74 are always interposed between 32 and D33, D33 and D34 and between intermediate air supply ports S41 and S42, S42 and S43, S43 and S44,
Also, intermediate exhaust port D31. D32. D33. D34 and the corresponding intermediate air supply port S41. S42. S43, S44
A group of pipes P31. and P31.
P32. P33. Connected by P34.

The drive device 3 can interlock the first stage compressor 5 and second stage compressor 6 of the compression device 1 with the first stage expander 9 and second stage expander 9 of the expansion device 2 through a drive shaft 12. It is configured to be connected to the main body, and can itself be rotated forward and backward.

The heat exchange device 4 is connected to the discharge port D of the second stage compressor 6 of the compression device 1.
O and the air supply port Soo of the first stage expander 9 of the expansion device 2, and the exhaust port Doo of the second stage expander 10 of the expansion device 2.
and the suction port So of the first stage compressor 5 of the compression device 1, and an independent pipe P
2 and P4 are configured to have heat exchange means only for the two-thread system.

The effects of the heat pump device having the above configuration will be explained.

First, when the drive device 3 rotates in the direction of the arrow, the first stage and second stage expanders 9, 10 and the first stage,
Although the second stage compressors 5 and 6 both start rotating in the direction of the arrow, explanation will be given sequentially starting from the first stage compressor 5.

In the first stage compressor 5 of the compression device 1, gas is sucked in through the suction port SO and compressed sequentially, and the gas in the compression process is transferred to the intermediate discharge port DI1. DI2, DI3. DI4
It is discharged sequentially.

This discharge port DI 1. DI2. DI3. The gas discharged from DI4 has pipe pH, PI3. PI3,
PI3, the heat is released and cooled by the heat dissipation device 8 on the way, and the intermediate suction port D21. D22. D
23. Guided to D24.

At this time, the intermediate discharge ports Dll and DI2 of the first stage compressor 5,
There is always vane 7 between DI2 and DI3, DI3 and DI4.
1, gases with different compression ratios are supplied to the intermediate suction ports S21, S22 . S23. S
24, is further compressed at each compression stage, and is discharged from the discharge port Do.

Also in this second stage compressor 6, intermediate suction ports S21 and S2
2. Since the vane 72 is always interposed between S22 and S23, and between S23 and S24, it is compressed again at each stage and discharges high-pressure compressed gas.

In this way, the gases having different compression ratios compressed in the first stage compressor 5 are each independently guided to the pipes P11 to P14 and pass through the heat radiating device 8 in the middle, so that the cooling effect can be further improved.

In Figure 2, two compressors and one heat dissipation device were used, but
By further increasing the number of compressors and heat dissipation devices, it is possible to perform even more gradual compression, and it is possible to perform compression that is very close to ideal isothermal compression and to improve the heat dissipation effect.

Here, the discharge amount of the second stage compressor 6 is set to be smaller than the suction amount of the first stage compressor 5 by an amount determined by the target compression ratio, so the gas reaches the target pressure. It is compressed and discharged.

The situation of volume change between compressors will be explained with reference to FIG.

In FIG. 2, the two vanes 71 of the first stage compressor 5
The space volume surrounded by the rotor 131 and the casing 141 is maximum when the rotation angle of the drive shaft 12 is 0 (reference), and as the rotation angle increases, the volume changes and becomes compressed as shown by the dotted line in FIG.

Further, the space volume surrounded by the two vanes 72, the rotor 132, and the casing 142 of the second stage compressor 6 is minimum when the rotation angle of the drive shaft 12 is O, and becomes surrounded by solid lines and dotted lines as the rotation angle increases. Volume changes like area.

- Intermediate discharge port DI of first-stage compressor 5 1. DI 2
．． Intermediate suction port S2 between DI3, DI4 and the second stage compressor 6
1, S22. S23. S24 is the pipe group pH.
, P12. P13. Since they are connected by P14, their total volume changes as shown by the solid line in FIG.

Therefore, the entire amount of air that is compressed and taken in from the suction port So of the first stage compressor 5 is discharged from the discharge port DO of the second stage compressor 6.

In this way, the compression is performed relatively slowly as a whole, and therefore the pressure difference between the two sides of the vanes 71 and 72 is not large, and both wear and friction loss can be reduced.

Next, other effects will be explained using the P-v line.

In Figure 4, the vertical axis shows the pressure P at that time, and the horizontal axis shows the total volume V.
It is a PV diagram showing.

The gas sucked up to point a in FIG. 4 by the first stage compressor 5 is sequentially compressed as the rotor 131 rotates, and is supplied to the second stage compressor 6 at each compression stage.

The change in volume and pressure at this time is originally a transition from a to b as shown by the dotted line in Figure 4, but since it is cooled by the heat dissipation device 8 installed midway, it changes as shown by the solid line. The transition is from a to b'.

The power required to compress air in this way is d-a-1)-c in the former case, and d-a-b' in the latter case.
It is represented by the area surrounded by -c.

In the compression device of the present invention, the gas flowing through each pipe is cooled by the heat radiating device 8 in each compression stage, so that the power consumption can be significantly reduced as is clear from FIG. 4.

Next, details of the heat dissipation device 8 will be explained.

The compressed gas in each compression stage compressed by the first stage compressor 5 has a different compression ratio, and therefore has a different temperature.

That is, the compressed gas discharged from the intermediate discharge port D11 has a relatively low temperature, but the compressed gas discharged from the intermediate discharge port D11 has a relatively low temperature. The compression ratio of the compressed gas discharged from D14 gradually increases, so the pipe pH
, PI2, PI3. The temperature of the compressed gas flowing through PI3 also increases as it approaches pipe P14.

Therefore, a relatively low temperature pipe P11 is installed at the bottom, P12 and PI3 are installed at the top, and the circulating fluid to be heated is supplied from the lower supply port 15, and heated from the upper drain port 16. Discharging the circulating fluid can increase the effectiveness of heat exchange.

The effects of the expansion device 2 will be explained.

The high-pressure compressed gas discharged from the discharge port Do of the second stage compressor 6 of the compression device 1 described above is transferred to the heat exchange device 4 (
(Details will be described later) and is supplied to the air supply port Soo of the first stage expander 9 of the expansion device 2.

Then the rotor 133, vane 73 and casing 143
The compressed gas surrounded by the space causes the rotor 133 to rotate in the direction of the arrow due to the expansion effect of its volume.

In other words, it applies a rotational force to the drive shaft 12 in the direction of the arrow.

The gas in this expansion process is transferred to the intermediate exhaust port D31. D32.
D33. It is sequentially discharged from D34.

This intermediate exhaust port D31°D32. D33. The gas discharged from D34 is transferred to pipe P31. P32. P3
3. P34, is heated by the heat absorbing device 11 on the way, and is passed through the intermediate air port S41. of the second stage expander 10. S42゜S
43. You will be guided to S44.

At this time, intermediate exhaust ports D31 and D32 of the first stage expander 9.
There is always vane 7 between D32 and D33, D33 and D34.
3, gases with different expansion ratios are supplied to the intermediate air supply ports S41.3 of the second stage expander 10. S42゜S43
．． The fuel is supplied to S44, expands again, and is discharged from the exhaust port Doo at each expansion stage while applying rotational force to the drive shaft 12.

Also in this second stage expander 10, intermediate air supply ports S41 and 5
42, since the vane 74 is always interposed between S42 and S43, and between S43 and S44, the gases at each expansion stage do not mix.

As described above, in the first stage expander 9, gases with different expansion ratios are independently led to the pipes P31 to P34 and pass through the heat absorbing device 11 on the way, so that the temperature decreases during the expansion process of the compressed gas, i.e. This can prevent energy loss due to adiabatic expansion.

In Figure 2, two expanders and one heat absorber were used, but
By further increasing the number of expanders and heat absorption devices, ideal isothermal expansion is approximated, and the compressed air supplied from the discharge port DO of the second stage compressor 6 to the air supply port Soo of the first stage expander 9 is improved. This makes it possible to effectively utilize all of the available energy and to improve the cooling effect.

Next, details of the heat absorbing device 11 will be explained.

The gases at each expansion stage, which have been expanded to some extent in the first stage expander, have different expansion ratios and therefore naturally have different temperatures.

That is, the gas discharged from the intermediate exhaust port D31 has a relatively high temperature, but the gas discharged from the intermediate exhaust port D32. The expansion ratio of the gas discharged from D33°D34 gradually increases, so that the gas discharged from pipe P31. P3
2. P33. The temperature of the gas flowing through P34 also gradually decreases.

Therefore, a relatively high temperature pipe P31 is installed at the top, and the following P32. Install P33 and then P34 at the bottom,
By supplying the circulating fluid to be cooled from the upper supply port 17 and discharging the cooled fluid from the lower discharge port 18, the heat exchange effect can be increased.

The effects of the heat exchange device 4 will be explained.

The high pressure compressed gas discharged from the second stage compressor 6 discharge DO is supplied to the air supply port Soo of the first stage expander 9. The temperature of the compressed gas supplied to this air supply port Soo is It is most desirable that the temperature be equal to the temperature of the gas discharged from the exhaust port Doo of the two-stage expander 10.

Similarly, it is most desirable that the temperature of the gas supplied to the suction port So of the first stage compressor 5 is equal to the temperature of the high pressure compressed gas discharged from the discharge port Do of the second stage compressor 6.

This is to connect the compression process on the high temperature side and the expansion process on the low temperature side while minimizing heat loss, thereby completing a highly efficient thermal cycle.

Therefore, unlike the heat radiating device 8 or the heat absorbing device 11, this heat exchange device 4 is designed to exchange thermal energy between the pipes P2 and P4 while being completely isolated from the outside air by the heat insulating material 27. This makes it possible to significantly improve the thermal efficiency of the heat pump device.

A thermal cycle consisting of the compression process by the compression device 1, the expansion process by the expansion device 2, and the temperature raising and cooling processes by the heat exchange device 4 will be explained using a T-8 diagram.

FIG. 5 is a T-3 diagram showing the absolute temperature T on the vertical axis and the entropy S on the horizontal axis.

The gas sucked into the first stage compressor 5 in the state shown in FIG. It is compressed and becomes state b.

The gas exiting the second-stage compressor 6 exchanges heat with the gas discharged from the second-stage expander 10 in the heat exchange device 4 to be in a cooled C state and is sucked into the first-stage expander 9.

Subsequently, in the process of being sent to the second stage expander 10,
The heat absorption device 11 absorbs heat, prevents the temperature from decreasing, and expands almost isothermally, resulting in the state d, and the second stage expander 1
Discharged from 0.

As described above, the gas exchanges heat with the gas exiting the second stage compressor 6 to raise its temperature, returns to state a, and is sucked into the first stage compressor 5 again.

The amount of heat released to the outside in the above cycle is the area a, b
, b', and a', and the amount of heat absorbed from the outside is shown by areas c, d, d', and c'.

The amount of heat exchanged in the heat exchange device 4 is a, a', d', d, c, c
', b' are almost equal.

Therefore, the power consumed by the drive device 3 is expressed by the area abcd, and the coefficient of performance ε representing the efficiency of the heat pump is expressed by .

Ta is the temperature of the gas at the inlet of the first stage compressor 5, and Td is the temperature of the gas at the outlet of the second stage expander 10.

Therefore, from FIG. 5, it is clear that the heat pump having the above configuration has extremely high efficiency.

Next, the effects of the drive device 3 will be explained.

As mentioned above, the first stage and second stage compressors 5.6 of the compression device 1
is driven via the drive shaft 12, and the compressed gas discharged from the discharge port Do of the second stage compressor 6 and supplied to the air supply port Soo of the first stage expander 9 of the expansion device 2 is , conversely, it applies rotational force to the drive shaft 12.

Therefore, the purpose can be achieved by transmitting a slight driving force equal to the difference between the power consumption of the compression device 1 and the amount of work done by the expansion device 2 mentioned above.

The above explanation describes the first stage disposed in the vane type compression device 1,
The drive shaft 12 of the second stage compressors 5, 6 and the drive shaft 12 of the first stage and second stage expanders 9, 10 disposed in the vane type expansion device 2 are common, that is, four rotors. 131
, 132, 133, and 134 all rotate at the same rotation speed, but the effects when the four rotors rotate at different rotation speeds will be described below.

First, if the rotational speeds of the first and second stage compressors 5.6 in the compression device 1 are the same, the discharge amount of the second stage compressor 6 is greater than the suction amount of the first stage compressor 5. , must be set so that it decreases by an amount determined by the target compression ratio, as described above.

In other words, the compressors from the first stage to the final stage must all have different volumes to achieve their purpose.

However, in the compression device in which the rotational speed of a plurality of compressors is made different in this embodiment, it is not necessarily necessary to make the capacity of the compressors different from the first stage to the final stage, and all the compressors have the same capacity. The purpose can be fully achieved even by using .

In other words, when compressors of the same capacity are used, the (m-1
) The objective can be achieved by rotating the membrane compressor at a rotation speed corresponding to the target compression ratio of the m-th stage compressor.

Being able to use compressors of the same capacity in this way is extremely convenient in terms of replacement of consumable parts and preventive maintenance.

Furthermore, as a method of making the rotational speeds of the plurality of compressors different, it is of course possible to use a plurality of transmission devices for one drive source, or to install a plurality of drive sources.

Moreover, it is also possible to forcibly change the rotation speed without making the first stage expander 9 and the second stage expander 10 of the expansion device 2 coaxial.

That is, in the heat pump device, the optimal values of the compression ratio, expansion ratio, and volume ratio of the compressor and expander change depending on the temperatures of the high heat source and the low heat source of the heat radiating device 8 and the heat absorbing device 11.

Therefore, by changing the rotational speed of the compression device 1 and/or the expansion device 2, the compression ratio, expansion ratio, and volume ratio can be selected to optimal values.

The heat pump device described above has rotors 131°132.
Vane 71 attached to 133, 134, 72, 73,
74 is composed of a compressor and an expander that slide in the radial direction, but if an axially sliding vane type compression/expansion machine is used as shown in Fig. 6, many more excellent effects can be expected. It is something that can be done.

Next, other embodiments of the present invention will be described in detail with reference to the drawings.

6 and 7 each show the configuration of an axially sliding vane type multi-stage compression/expansion machine 19, and FIG. 8 shows a cross section of the main part and a gas flow path.

In FIG. 6, the compression/expansion machine 19 is the first stage compression working chamber 2.
0, second stage compression working chamber 21 and first stage expansion working chamber 22
, a second stage expansion chamber 23.

This compression/expansion machine 19 has a rotor 13, which has a drive shaft 12 fixed thereto, disposed within a hollow cylindrical casing 14 so as to be concentric and rotatable.

The vane 7 is mounted on the rotor 13 so as to be able to slide in the axial direction, and rotates while sliding in close contact with the cams 24, 25, 26, and 27.

Therefore, when the drive shaft 12 rotates, the rotor 13 and vane 7
The spatial volume of each of the working chambers 20, 21, 22, 23 surrounded by the cams 24, 25, 26, 27 increases or decreases in volume sequentially, thereby performing a compression or expansion action.

7 and 8, the first stage compression working chamber 20 has a suction port So, an intermediate discharge port Dll, D12°DI3. DI4
The second stage compression working chamber 21 has an intermediate suction port S21. S
22. S23. It has S24 and a discharge port Do.

These intermediate discharge ports D11, DI2. DI 3. DI4 and the corresponding intermediate intake port S21. S22. S23. S
24 is pipe pH, PI3. PI3. They are connected by the PI 3 and a heat dissipation device 8 is installed in the middle.

In addition, the intermediate discharge ports Dll and DI2 of the first stage compression working chamber 20
, the vane 7 is always interposed between DI2 and DI3, and between DI3 and DI4, and the intermediate suction port S21 of the second stage compression working chamber 21
The vane 7 is always interposed between S22 and S22, S22 and S23, and S23 and 824.

Next, the first stage expansion working chamber 22 has an air supply port Soo and an intermediate exhaust port D31. D32. D33. D34, and the second stage expansion working chamber 23 has an intermediate air supply port S41. S42, S43. S44
There is also a note that it has an exhaust port DOo.

This intermediate exhaust port D31. D32. D33°D34 and the corresponding intermediate air supply port S41. S42, S43. S44
is pipe P31. P32゜P33. They are connected by P34, and a heat absorbing device 11 is installed in the middle.

Also, intermediate exhaust ports D31 and D32 of the first stage expansion working chamber 22
, the vane 7 is always interposed between D32 and D33, and between D33 and D34, and the middle peripheral air supply port S41 of the second stage expansion working chamber 23
The vane 7 is always interposed between S42 and S42, S42 and S43, and S43 and 844.

In FIG. 6, the drive device 3 rotates a rotor 13 via a drive shaft 12.

As shown in FIGS. 7 and 8, the heat exchange device 4 has a second
Discharge port Do of stage compression working chamber 21 and first stage expansion working chamber 22
and between the air supply port Soo of the second stage expansion working chamber 23 and the connecting pipes P2 and P4 between the exhaust port Doo of the second stage expansion working chamber 23 and the suction port So of the first stage compression working chamber 20, and an independent pipe P2 and It is configured to have heat exchange means only for the P4 two-thread system.

The effects of the heat pump device having the above configuration will be explained.

First, when the drive device 3 rotates, the rotor 13 starts rotating via the drive shaft 12, and the first stage and second stage compression working chambers 20.2
Compression or expansion starts in the first stage, second stage, and expansion working chambers 22 and 23, respectively, and will be explained sequentially starting from the first stage compression working chamber 20.

In the first stage compression working chamber 20, gas is sucked in from the suction port So and compressed sequentially, and the gas in the compression process is passed through the intermediate discharge port DI1. DI 2. DI3. It is sequentially discharged from DI4.

This discharged gas has pipe pH, PI3. P
I3. It passes through the PI3 and is cooled by discharging heat by the heat dissipation device 8 on the way, and is then transferred to the intermediate suction port S21 of the second stage compression working chamber 21.
゜S22. S23. You will be guided to S24.

At this time, intermediate discharge ports Dll and D of the first stage compression working chamber 20
Since the vane 7 is always interposed between I2, DI2 and DI3, and between DI3 and DI4, gases with different compression ratios are supplied to the intermediate suction ports S21. S22.
S23. It is supplied to S24, further compressed at each compression stage, and discharged from the discharge port DO.

Also in this second stage compression working chamber 21, the intermediate suction port S21
Since the vane 7 is always interposed between S22 and S22, S22 and S23, and S23 and S24, gases with different compression ratios are further compressed at each compression stage, and high-pressure compressed gas is discharged from the discharge port Do. It is something to do.

In this way, the gases with different compression ratios compressed in the first stage compression working chamber 20 are independently adjusted to the pipe pH, PI3. P
Since the heat is guided by I3 and PI3 and passes through the heat dissipation device 8 on the way, the heat dissipation cooling effect can be further improved.

In Figures 6 to 8, two stages of compression working chambers and one heat dissipation device are used, but by further increasing the number of compression working chambers and heat dissipation devices, even gentler compression becomes possible, making it ideal. It is possible to perform compression very similar to isothermal compression and to improve the effect of heat dissipation.

Here, the discharge amount of the second stage compression working chamber 21 is set to be smaller than the suction amount of the first stage compression working chamber 20 by an amount determined by the target compression ratio, so that the gas reaches the target pressure. It is compressed and discharged.

The situation of volume change between the first stage and second stage compression working chambers 20 and 21 is as described above with reference to FIG.

Furthermore, the effect of reducing consumption activity "'f5-cb" is similar to the effect described above according to the PV diagram in FIG. 4.

Next, details of the heat dissipation device 8 will be explained.

In FIG. 8, the compressed gas in each compression stage compressed by the first stage compression working chamber 20 has a different compression ratio, so it naturally has a different temperature.

That is, the compressed gas discharged from the intermediate discharge port D11 has a relatively low temperature, but at DI2. DI3. Since the compression ratio of the compressed gas discharged from DI4 gradually increases, the pipe pH, PI3. PI3. The temperature of the compressed gas flowing through the PI3 also increases as it approaches the PI3.

Therefore, a relatively low temperature pipe pH is installed at the bottom, and the following P12. P13 Then, by installing PI3 at the top, supplying the circulating fluid to be heated from the lower supply port 15, and discharging the heated circulating fluid from the upper discharge port 16, the heat exchange effect can be increased. be.

The high-pressure compressed gas discharged from the discharge port Do of the second stage compression working chamber 21 is supplied to the air supply port Soo of the first stage expansion device via the heat exchange device 4.

Rotor 13, vane 7, and cams 24, 25, 26, 27
The compressed gas surrounded by the compressed gas gives a rotational force to the drive shaft 12 via the rotor 13 due to the expansion of its volume.

The gas in this expansion process is transferred to the intermediate exhaust port D31. D32.
D33. It is sequentially discharged from D34.

This discharged gas is transferred to each pipe P31. P32
．． P33. P34, is heated by the heat absorbing device 11 on the way, and is passed through the intermediate air supply port S41. of the second stage expansion working chamber 23.
S42°S43. You will be guided to S44.

At this time, the intermediate exhaust ports D31 and D of the first stage expansion working chamber 22
32, since the vane 7 is always interposed between D32 and D33, and between D33 and D34, gases with different expansion ratios are supplied to the intermediate air supply ports S41 and S42 of the second stage expansion working chamber 23.
．． S43. The fuel is supplied to S44, expands again, and is discharged from the exhaust port Doo while applying rotational force to the drive shaft 12.

In this way, the intermediate exhaust port D31 of the first stage expansion working chamber 22.
D32. D33. Gases with different expansion ratios are independently piped from D34 to pipe P31. P32, P33. Since the gas is guided to P34 and passes through the heat absorbing device 11 on the way, it is possible to prevent a temperature drop during the expansion process of the compressed gas, that is, loss of energy due to adiabatic expansion.

In Figures 6 to 8, two stages of expansion working chambers and one heat absorbing device are used, but by further increasing the number of expansion working chambers and heat absorbing devices, even more gradual expansion is possible and ideal isothermal It is possible to perform an expansion that is very similar to the expansion.

Therefore, it is possible to effectively utilize all the energy of the compressed gas supplied from the discharge port Do of the second stage compression working chamber 21 to the air supply port Soo of the first stage expansion working chamber 22, and to increase the cooling effect. can.

Next, details of the heat absorbing device 11 will be explained.

The gas in each expansion stage, which has been expanded to a certain extent in the first stage expansion working chamber 22, has a different expansion ratio, so it naturally has a different temperature.

That is, the air discharged from the intermediate exhaust port D31 has a relatively high temperature, but the DBP.

D33. Since the expansion ratio of the gas discharged from D34 gradually increases, the gas discharged from pipe P31. P32. The temperature of the gas flowing through P33 and P34 also gradually decreases.

Therefore, a relatively high temperature pipe P31 is installed at the top, and the following P32. P33 and then P34 are installed at the bottom, supplying the circulating fluid to be cooled from the upper supply port 17 and discharging the cooled fluid from the lower exhaust port 18, the effect of heat exchange can be increased. It is something.

The effects of the heat exchange device N4 will be explained.

The high-pressure compressed gas discharged from the discharge port Do of the second stage compression working chamber 21 is supplied to the air supply port Soo of the first stage expansion working chamber 22.

It is most desirable that the temperature of the compressed gas supplied to the air supply port Soo is equal to the temperature of the gas discharged from the exhaust port Doo of the second stage expansion working chamber 23.

Similarly, it is most desirable that the temperature of the gas supplied to the suction port SO of the first stage compression working chamber 20 is equal to the temperature of the high pressure compressed gas discharged from the discharge port Do of the second stage compression working chamber 21.

This aims to connect the temperature rise in the compression process on the high temperature side and the expansion process on the low temperature side while minimizing heat loss, thereby completing a highly efficient thermal cycle.

Therefore, the heat exchange device 4 is either the heat radiating device 8 or the heat absorbing device 1.
1, the thermal efficiency of the heat pump device can be significantly increased by exchanging the thermal energy of each pipe P2 and P4 with the heat insulating material 27 completely blocking the outside air. be.

Next, the effects of the drive device 3 will be explained.

As is clear from FIG. 6, one rotor 13 is driven by one drive shaft 12, and two rotors are driven by one vane 7.
Stage compression working chamber 20.21 and second stage expansion working chamber 22
．． 23 are configured.

The compression working chambers 20 and 21 consume power, but the expansion working chambers 22 and 23 conversely provide rotational force to the drive shaft 12.

Therefore, as mentioned above, the purpose can be achieved by transmitting a small driving force equal to the difference between the power consumption of the compression working chamber and the amount of work done by the expansion working chamber.

As explained above in FIG. 6, the air is compressed and expanded by the multi-stage working chambers of the axial sliding type, so that the heat pump device itself can be made into an extremely compact device.

Further, the same purpose can be achieved even with an apparatus constructed of a parallel multistage type of diametrical slider type as shown in FIG.

In all the heat pump devices described above, by making the drive device 3 capable of both forward and reverse rotation, the functions of all the devices can be operated in the opposite direction.

That is, a compression device is converted into an expansion device, an expansion device is converted into a compression device, a heat dissipation device is converted into a heat absorption device, and a heat absorption device is converted into a heat dissipation device.

Therefore, it is possible to easily switch to cooling in the summer and heating in the winter.

The following is a summary of the features of each of the compression device 1, expansion device 2, drive device 3, and heat exchange device 4 that constitute the heat pump device of the present invention.

Compressed gases having different compression ratios are repeatedly compressed in multiple stages in the compression device 1, and the heat is radiated and cooled by a heat radiating device 8 installed in the middle.

Therefore, it is possible to perform gentle compression that is very similar to isothermal compression, thereby significantly reducing power consumption, obtaining high-pressure compressed gas, and effectively dissipating heat.

In the expansion device 2, air having different expansion ratios undergoes multiple expansions at each stage, and is heated by absorbing heat by an endothermic device 11 installed in the middle.

Therefore, gradual expansion very close to isothermal expansion is possible, and all of the energy of the supplied compressed gas can be effectively utilized, significantly reducing power consumption.

Regarding the heat exchange device 4, the energy of the gas supplied from the compression device 1 to the expansion device 2 and from the expansion device 2 to the compression device 1 is isolated from the atmosphere and heat exchange is performed with each other.

Therefore, a cycle of high thermal efficiency of the heat pump device can be completed.

Regarding the drive device 3, the power consumption of the compression device 1 is significantly reduced, and the expansion device 2 effectively utilizes all the energy of the supplied compressed gas and converts it into rotational force.

Therefore, the heat pump device can be operated with a small driving force.

The heat pump device of the present invention, which includes devices having many excellent features as its main components, has the following effects.

(1) Since no refrigerant is used, it is safe and clean throughout the period of manufacture, use, and disposal.

(2) It is economical because no expensive refrigerant is used.

(3) There are no expansion valves or switching valves, so the structure is simple and there are fewer failures.

(4) Since any gas can be selected as the working gas, there is no restriction on the operating temperature.

(5) High efficiency reduces operating costs.

(6) Since the entire device is compact, it occupies a small area and can be mounted on a vehicle.

(7) It is possible to switch between air conditioning and heating simply by switching the rotation direction, and the operation is simple.

As is clear from the above description, the heat pump device according to the present invention has novel functions not found in conventional products, and can achieve significant effects.

[Brief explanation of drawings]

Fig. 1 is a route diagram of a conventional heat pump device, Fig. 2 is a route diagram showing an embodiment of the present invention, Fig. 3 is an explanatory diagram of volume change of compressed air, Fig. 4 is a PV diagram, Figure 5 is the T-8 diagram, No. 6
The figure is a longitudinal cross-sectional view of an axial sliding type compression/expansion machine, Figure 7 is a cross-sectional view of the same essential parts, Figure 8 is a route diagram of the same, and Figure 9 is a diametrical sliding type parallel multi-stage compression/expansion machine. FIG. 1: Compression device, 2: Expansion device, 3: Drive device, 4: Heat exchange device, 5: First stage compressor, 6: Second stage compressor, 7: Vane, 8: Heat radiation device, 9: First stage expander, 10: second stage expander, 11: heat absorption device, 12: drive shaft, 13: rotor, 14: casing, 20: first stage compression working chamber, 21
: 2nd stage compression working chamber, 22: 1st stage expansion working chamber, 23:
Second stage expansion working chamber.

Claims (1)

[Claims] 1. Consisting of a compression device, an expansion device, a drive device, and a heat exchange device, the compression device is provided with a plurality of vane type compressors constituting the first stage to the final stage, and The stage compressor is provided with one or more suction ports, and the final stage compressor is provided with one or more discharge ports,
The m-th stage compressor is provided with a plurality of intermediate discharge ports, and the (m+1)th membrane compressor is provided with a plurality of intermediate suction ports (m is an integer of 1, 2, etc.), and the intermediate discharge ports that are adjacent to each other are provided. One or more vanes are always interposed between the intermediate discharge port and the corresponding intermediate suction port, and the intermediate discharge port and the corresponding intermediate suction port are connected by a group of pipes each interposed in a heat dissipation device. configure,
The above expansion device is equipped with a plurality of vane type expanders constituting the first stage to the final stage, the first stage expander has an air supply port, and the final stage expander has one or more exhaust ports each. The n-th stage expander is provided with a plurality of intermediate exhaust ports, and the (n+1)-th stage expander is provided with a plurality of intermediate air supply ports (n is an integer of 1, 2, etc.). One or more vanes are always interposed between the intermediate exhaust ports and between the intermediate air supply ports, and the intermediate exhaust ports and the corresponding intermediate air supply ports are connected by a group of pipes each interposed in a heat absorbing device. The drive device is configured by linking the compression device and the expansion device in an interlocking manner, and the heat exchange device is arranged between the discharge port of the compression device and the air supply port of the expansion device and the expansion device. A heat pump device characterized in that it has an independent heat exchange means only between one system, which is interposed in a connecting means between an exhaust port of the device and an inlet of a compression device. 2. A heat pump device according to claim 1, characterized in that the rotation speeds of the compression device and/or the expansion device are different. 3. A heat pump device according to claim 1, characterized in that either the compression device or the expansion device has a common drive shaft. 4. A heat pump device according to any one of claims 1 to 3, characterized in that the compression device and/or the expansion device are of the axial sliding type. 5. Consisting of a compression device, an expansion device, a drive device, and a heat exchange device, the compression device is equipped with a multi-stage compressor having a plurality of vane-type working chambers constituting the first stage to the final stage,
The first stage working chamber has an inlet and the final stage working chamber has one discharge port.The first stage working chamber has an intermediate discharge port,
A plurality of intermediate suction ports are provided in each of the m+1) stage working chambers (m+1).
is an integer of 1, 2...), one or more vanes are always interposed between the intermediate discharge ports and the fellow suction ports that are adjacent to each other, and the intermediate discharge ports and the corresponding intermediate suction ports The expansion device comprises a vane type multi-stage expander having a plurality of vane type working chambers constituting the first stage to the final stage. The first stage working chamber is provided with an air supply port, the final stage working chamber is provided with at least one exhaust port, the nth stage working chamber is provided with an intermediate exhaust port, and the (n+1)th stage working chamber is provided with an intermediate exhaust port, and the Each chamber is provided with a plurality of intermediate air supply ports (n is an integer of 1, 2, etc.), and one or more vanes are interposed between the mutually adjacent intermediate exhaust ports and between the fellow air supply ports. , the intermediate exhaust port and the corresponding intermediate air supply port are connected by a group of pipes each interposed in a heat absorption device, and the drive device is capable of interlocking the compression device and the expansion device. The heat exchange device is connected to a connecting means between the discharge port of the compression device and the air supply port of the expansion device and between the exhaust port of the expansion device and the suction port of the compression device. 1. A heat pump device characterized in that it is configured to have heat exchange means between only one independent system. 6. The heat pump device according to claim 5, wherein the compression device and/or the expansion device are axially sliding blade chambers.