JPS61116251A - Absorption type heat pump - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] - The present invention relates to an absorption heat pump, and more particularly to a high-abuse absorption heat pump that can obtain high-temperature heat output using waste heat.

[Conventional technology]

Figure 6 shows the absorption heat pump for this food.
is a generator, 2 is a condenser, 3 is an evaporator, and 4 is an absorber. Inside each container, there are a generated heat exchanger 5, a condensing heat exchanger 6, an evaporative heat exchanger T1, an absorption heat exchanger 8. Each of them is provided. Also, a concentrated solution pipe 3 is connected to the lower part of the generator 1, and the concentrated solution pipe 9 is connected to the absorber 4 via a solution pump 1G, a solution heat exchanger 11, and a first control valve 12t. ing.

Further, a dilute solution pipe 13 is connected to the lower part of the absorber 4, and the dilute solution pipe 13 is connected to the generator 1 via the solution heat exchanger 11 and the second control valve 14t. The generator 1 and condenser 2 as well as the evaporator 3 and absorber 4 are connected by a low-pressure steam pipe 15 and a high-pressure steam pipe 16, respectively, and are connected to the lower part of the condenser 2! The refrigerant liquid pipe 11 is connected to the evaporator 3 via a refrigerant pump 1st.

The seventh row shows the operating state of the conventional heat pump drawn on the temperature-pressure-concentration diagram, and the state points ■ to ■ in the diagram correspond to the operating points ■ to ■ in the sixth factor. Each corresponds to the other.

Next, the operation of the above conventional example will be explained. The dilute solution with a concentration ξl at the state point (2) which exits the solution heat exchanger 11t and whose flow rate t is adjusted by the second control valve 14 is supplied to the generated heat exchanger 5 from a heat source such as exhaust heat (depending on the temperature). heated,
The temperature award, concentration ξ, which releases the refrigerant vapor and is indicated by the state point ■
2. It becomes a concentrated solution with a pressure of 9. This concentrated solution is pressurized to a pressure higher than ``~'' by the solution pump 10, passes through the concentrated solution tube 9, and reaches the solution heat exchanger 11. Here, it passes from the absorber 4 through the dilute solution tube '13t-, and is generated. Return to vessel 1 and exchange heat with the rare #! liquid.

As a result, the temperature changes from the state point ■ in FIG. 7 to the temperature 3 shown by the state point ■. After this concentrated solution exits the solution heat exchanger 11', the flow rate is adjusted by the first control valve 12, and the solution is distributed to the absorption heat exchanger 8 of the absorber 4. The sprayed concentrated solution with a concentration ξ2 absorbs the refrigerant vapor at the state point ■ flowing from the evaporator 3 through the high-pressure steam pipe 16, and becomes a dilute solution at the state point ■ indicated by the concentration ξ1. When transitioning from ■ to state point ■, heat is generated in the temperature range, and this heat heats the water flowing through the absorption heat exchanger aFF3t, which is used for various purposes as steam or hot water. The solution having a concentration of ξ1 flows through the dilute solution tube 13 to the solution heat exchanger 11, where it exchanges heat with the concentrated solution and changes from the temperature 'I'm (state point ■ in Fig. 7). Temperature TM (
It descends to the vicinity of state point (■) in Fig. 7. This dilute solution returns to the generator 1 through the second control valve 14t.

10,000, the refrigerant vapor generated in the generator 1 is transferred to the low pressure steam pipe 15
The refrigerant flows into the condenser 2, where it is cooled by the condensing heat exchanger 6, condenses and liquefies, resulting in refrigerant disease as indicated by state point (3). This refrigerant liquid is passed through the refrigerant liquid pipe 17 and the refrigerant pump 1
After being pressurized at pMJ by 8, it flows into the evaporator 3. The refrigerant liquid in the evaporator 3 is heated by a heat source such as exhaust heat supplied to the evaporative heat exchanger T, and becomes refrigerant vapor at state point (3). Figure 8 shows another conventional absorption heat pump, which, unlike the heat pump shown in Figure 61, has two absorbers, two evaporators, and two solution heat exchangers. It is a stage absorption type heat pump. In Fig. 8, the symbols 1, 2.5
10, 13, 15, and 1T companies, showing the same or corresponding parts as the apparatus shown in FIG. 8th vA
Inside, 3a is a second evaporator 3b#:l: a first evaporator, which is a refrigerant liquid pipe 1T in which a flow rate control valve 24 is interposed.
connected by. Further, the second evaporator 3a
The absorber 4b is provided in a circle, and the first absorber 4b and the first
The evaporator 3b is connected to the second evaporator 3a by a medium pressure steam pipe 20, and 4& is a second absorber connected to the second evaporator 3a by a high pressure steam pipe 16. A concentrated solution pipe 9 is connected to the lower part of the generator 1, and the concentrated solution pipe 9 is connected to a solution pump 1G,
The first solution heat exchanger 11a1 is connected to the second absorber 4a via the second solution heat exchanger 11b and the third control valve 21t.

Further, an intermediate concentrated bath liquid pipe 19 is connected to the lower part of the second absorber 4&. 1 absorber 4b
It is connected to the. Furthermore, in the lower part of the first absorber 4b,
The dilute solution tube 13 is connected to the first dilute solution tube 13.
It is connected to the generator 1 via the solution heat exchanger 11& and the Wc5 control valve 23t. Also, the condenser 2 and the second evaporator 3
A is connected to the refrigerant pump 18 by a refrigerant liquid pipe 1T. Furthermore, the generated heat exchanger 5 is the generator 1
179, the condensing heat exchanger 6 is provided in the condenser 2, the evaporative heat exchanger T is provided in the first evaporator 3b, and the absorption heat exchanger 8° is provided in the second absorber 4a.

Fig. 9 shows the operating state of the heat pump shown in Fig. 8 drawn on the temperature-pressure-concentration line, and the state points ■ to ■ in the ninth garden are the operating points ■ in the eighth prison. It corresponds to ~0.

Next, the operation of the heat pump shown in the eighth factor will be explained. The dilute solution with a concentration ξ1 at the state point (■) passes through the first solution heat exchanger 11&9, the flow rate is adjusted by the fifth control valve 23, and returns to the generator 1-. is heated by a heat source (temperature [T8)] and releases refrigerant vapor to reach the temperature TI indicated by the state point ■.

It becomes a concentrated solution with a concentration ξ and a pressure PL. This concentrated solution is pressurized to a pressure higher than PH by the solution pump 10, passes through the concentrated solution pipe 9t, and reaches the first solution heat exchanger 11&, where it passes from the first absorber 4b to the dilute solution pipe 13t, and is then passed through the generator. By exchanging heat with the dilute solution that returns to 1, the state of the concentration sum shown by the state point ■ changes from the state point ■ of the ninth prisoner. Furthermore, this concentrated solution is transferred to the second solution heat exchanger 11b, where the second
The intermediate concentration solution flowing through the intermediate concentration solution pipe 19t from the absorber 4& to the first absorber 4b exchanges heat with the intermediate concentration solution, and rises from the temperature (temperature) to the temperature tube (state point ■) in FIG. 9 and the second absorber 41.
It is distributed from the circular concentrated solution tube 9 to the absorption heat exchanger 8.

The sprayed concentrated solution with a concentration ξ5 absorbs the refrigerant vapor indicated by a state point Φ flowing from the second evaporator 3a through the high pressure steam pipe 16t into the second absorber 4a, and reaches the state point indicated by a concentration ξ2. It becomes an intermediate concentration solution of (2). When transitioning from state point (2) to state point (2), heat is generated (temperature TH), and this heat heats water flowing through the absorption heat exchanger and is used for various purposes as steam or hot water.

The solution that has become intermediate concentration ξ2 by absorbing vapor t flows through the intermediate concentration solution pipe 1st to the second solution heat exchanger 11b, where it exchanges heat with the concentrated solution exiting the first solution heat exchanger 11m. Then, the temperature drops to near the temperature TM (state point ■ in FIG. 9). After the flow rate of this solution is controlled by the fourth control valve 22, it is sprayed from the intermediate concentration solution pipe 19 of the first absorber 4bFF3. The sprayed solution with a concentration ξ2 absorbs the refrigerant vapor indicated by state point ■ (9th prisoner) flowing from the first evaporator 3b through the medium pressure steam pipe 20t and into the first absorber 4b, and the concentration ξ
It becomes a (9th-) dilute solution at state point 1. Due to the heat generated (temperature TM) when transitioning from the state point ① to the state point ω, the liquid cooling charge of the second evaporator 3a is heated to generate refrigerant vapor indicated by the state point ω. State point ■ (The dilute solution of the 9th erection is
The dilute solution tube 13t-through the first solution heat exchanger 11 alc flow, where it exchanges heat with the concentrated solution from the generator 1 to bring the temperature TM.
The temperature drops from the temperature to the vicinity of the temperature Ts at the state point (3), and the flow rate is adjusted by the fifth control valve 23 and returns to the generator 1.

The refrigerant vapor generated in the inner generator 1 flows into the condenser 2 through the low-pressure steam pipe 15, where it is cooled by the condensation heat exchanger 6, condenses and liquefies, and becomes the refrigerant liquid indicated by state point ■. Become. This refrigerant liquid passes through the refrigerant liquid pipe 1T, is pressurized to pH (FIG. 9) by the refrigerant pump 18, and flows into the second evaporator 3a of the first absorber 4b. Here, the intermediate concentration solution from the second absorber 4& is heated by the exothermic action when absorbing the refrigerant vapor from the first evaporator 3b, and a part of the refrigerant liquid becomes the vapor refrigerant shown by the state point ■. Second absorber 4
flows into a. In addition, a part of the refrigerant liquid in the second evaporator 3a is
From the high pressure PH second evaporator 3a to the intermediate pressure first evaporator 3
b, but due to the pressure difference (Phi-PM) and the flow control valve 24. A flow rate determined by the opening degree of the valve flows through the refrigerant liquid pipe 17. The refrigerant liquid flowing into this first evaporator 3b is
It is heated by exhaust heat flowing through the evaporative heat exchanger TV'3,
The refrigerant becomes a vapor refrigerant indicated by state point (3) and flows into the first absorber 4b through the intermediate pressure steam pipe 20, but it flows into the first evaporator 3b or the WI2 evaporator 3. & According to the liquid level of the refrigerant liquid at IF3, the valve opening degree of the flow rate control valve 24 is adjusted to adjust the flow rate of the refrigerant liquid.

Fig. 10 shows a further different conventional absorption heat pump, whose main components are the same as the heat pump shown in Fig. 8, especially the condenser, first evaporator, and second evaporator shown in the same figure. The components and the refrigerant system piping connected thereto are the same as those shown in FIG. 10 and are therefore omitted here. Therefore, in Figure 10, only the generator, the first absorber, the second absorber, and the solution piping system connected to these are shown. A generated heat exchanger 5 is provided. A concentrated solution pipe 9 with a solution pump 10 interposed therein is connected to the lower part of the generator 1.
The concentrated solution tube 9 is connected to the second absorber 4aK via the second solution heat exchanger 11e and the sixth control valve 25t, and the first solution heat exchanger 11d and the eighth control valve 27t. It is branched into a concentrated solution pipe 9b which reaches the first absorber 4b through the pipe.

The second absorber 4aP'3 is provided with an absorption heat exchanger 8, and the lower part of the second absorber 41 is provided with a dilute solution pipe 1.
3 m, and this pipe 13 m is connected to the generator 1 via the second solution heat exchanger 11 c and the seventh control valve 26 . Further, a dilute solution pipe 13b is connected to the lower part of the first absorber 4b, and this pipe 13b is connected to the generator 1 via the m1 solution heat exchanger 11'd and the ninth control valve 28. In other words, the heat pump shown in the same figure is different from the heat pump shown in FIG. , a parallel system returns from the generator 1 to the generator 1 via the second absorber 4&, and returns to the generator 1 via the WL1 absorber 4b. Therefore, the concentrated solution leaving the generator 1 is pressurized by the solution pump 10, then divided into streams, heat exchanged by the second solution heat exchanger 11e, and the flow rate is adjusted by the sixth control valve 25. The absorber 4a absorbs the vapor refrigerant and turns it into a dilute solution, which then flows out to the second solution heat exchanger 11.
After exchanging heat at step a, the flow rate is adjusted by the seventh control valve 26 and returns to the generator 1. The other one exchanges heat with the first solution heat exchanger 11d, and after adjusting the flow rate with the eighth control valve 2T, absorbs the vapor refrigerant in the first absorber 4b and becomes a dilute solution9, which then flows out. , after heat exchange in the first solution heat exchanger 11d,
The flow rate is adjusted by the ninth control valve 28 and returns to the generator 1. 1st
Although not shown in Figure 0, in the generator 1, the dilute S liquid is completely heated by the exhaust heat flowing through the generated heat exchanger 5, and the refrigerant vapor is sent to the condenser 2. wV, 2nd absorber 4m. The refrigerant vapor sent from the I generator 3a is absorbed, and this absorption heat is used in processes outside the system via the absorption heat exchanger 8.
Operation IL that absorbs the refrigerant vapor sent from the evaporator 3b and uses this heat to evaporate the refrigerant liquid in the second evaporator 3a, and also The system also operates in the same way as the conventional device shown in Prisoner 8.

[Problem to be Solved by the Invention 3] As explained above, the conventional absorption type heater pump shown in Figs. This will be explained using Figure $6 as an example. When the apparatus is stopped, the solution in a uniform concentration state after the dilution operation is transferred to the generator 1, the absorber A4, and the concentrated solution pipe 9 connecting these.
It exists in the dilute solution tube 13 and the solution heat exchanger 11, and this temperature is considered to be approximately room temperature. Next, when starting up the device i, first a heat source such as exhaust heat is passed through the generating heat exchanger 5 to heat the solution and create a concentrated solution in the generator 1. The refrigerant vapor generated at this time is liquefied by 1114 m in condenser 2 and then liquefied into evaporator 3.
This refrigerant liquid is sent to the evaporative heat exchanger? is heated and becomes steam. In this state, the solution pump 10 is operated, and the concentrated solution g from the generator IFF3 is passed through the solution heat exchanger 11 and the first control valve 12'' through the concentrated solution pipe 9 and into the absorption heat exchanger of 4 yen. 8, at the initial stage of startup, the temperature of the solution existing in the concentrated #rg, tube 9, and solution heat exchanger 11 is lower than the steady-state temperature of the absorber 40, so the refrigerant vapor sent from the evaporator 3 As a result, absorber 4
There is a large amount of low-concentration dilute solution that has absorbed refrigerant vapor in the absorber 4, and the significant absorption prevents the pressure from increasing in the absorber 4. The pressure difference ΔP (
(PM - PL) = ΔP) shown in Fig. 7 cannot be obtained,
Solution distribution could become uneven.

In addition, in order to ensure the pressure difference, the first control valve 12 etc. are adjusted so that llI! flows into the absorber 4! f# Is it possible to reduce the amount of vapor absorbed by reducing the liquid flow rate and maintain the pressure in the absorber 4 at a high level? The existing solution at room temperature would be replaced with a concentrated solution heated by the generator, which caused the problem that it would take a long time to reach a temperature close to steady operating conditions. Cause.

The conventional two-stage absorption heat pump shown in No. 10 also has the problem that it takes a long time to reach a steady state. In particular, in the equipment No. 9 shown in No. 8, the melt is transferred from the generator 1 to the second absorption heat pump. Equation 4a and first absorber 4bt-via generator 1
Since it is a serial piping system that returns to
Furthermore, this affected the generator 1, and it took a long time to start up 9.

This development #J was made with the aim of solving the above-mentioned problems, and is intended to provide an absorption heat pump that can shorten the start-up time from startup to steady operation.

[Means for solving inter-group points]

In the absorption heat pump according to the present invention, the solution pump discharged from the generator does not pass through the t-absorber, but only passes through at least one solution heat exchanger and is returned to the generator by bypass. A piping system is provided.

[Effect]

In this invention, the bypass piping system is switched so that the solution coming out of the solution heat exchanger returns to the generator side without going through the absorber, and the room-temperature solution that exists in the solution piping system at the time of startup is (especially the solution in the solution heat exchanger) is preheated by replacing it with the heated solution in the generator.

〔Example〕

An embodiment of the present invention applied to a single-stage absorption heat pump will be described below with full reference to FIG. 1.

In the figure, the same reference numerals as in FIG. 6 indicate the same or corresponding parts. A first on-off valve 29 is provided between the absorber 4 and the solution heat exchanger 11. Further, 30 is a second on-off valve, and one end is connected to the concentrated solution t between the solution heat exchanger 11 and the first control valve 12.
The other end is connected between the solution heat exchanger 11 of the dilute solution 1r13 and the first on-off valve 29.

The following operation will be explained.

The operating points ■ to ■ in FIG. 1 correspond to the state points ■ to ■ in FIG. Therefore, the same solution circulation system as in the apparatus shown in FIG. 6 is formed, and the operation will be the same as that of the conventional apparatus described in Section 6-. Therefore, the explanation is omitted here. At the time of startup, the first on-off valve 29 is closed, the second closing valve 30t is open, the first control valve 12 is closed, and the second control valve 14t is open.

By this operation, when the device is started, the solution heated by putting a heat source into the generated heat exchanger 5 with a generator of 1 yen passes through the concentrated solution tubes 97, is discharged by the solution pump 10, and is discharged from the solution heat exchanger 11.
From there, a closed circuit t-flows back to the generator 1 via the second on-off valve 30, the solution heat exchanger 11 and the second control valve 14, so that when stopped, Il! The room temperature solution remaining in the solution tube 9, solution heat exchanger 11, etc. is replaced with the heated solution. After being replaced, the first on-off valve 29t-open,
The second on-off valve 30t is closed, and the first control valve 12 and the second control valve 14 are in the normal control state, with the tabs open, and steady operation is performed.

Next, an embodiment of the present invention corresponding to the conventional two-stage absorption heat pump shown in FIG. 8 will be described with reference to FIG. 2.

The same reference numerals as in FIG. 3 indicate the same or equivalent parts, and 31 is a third on-off valve, which is provided between the second absorber 4m and the second solution heat exchanger 11b. 32 is a fourth on-off valve, one end of which is connected to the m-solution 1ii9t-branched pipe 19a between the second solution heat exchanger 11b and the third control valve 21, and the other end connected to the second solution of the intermediate concentration solution pipe 19. It is connected between the heat exchanger 11b and the third on-off valve 31. 33 is the fifth
With the on-off valve, the first absorber, 4b and the first solution heat exchanger 11&
The dilute solution tube 13 is interposed between the

Also, 34 is the sixth on-off valve 1, and one end is the first solution heat exchange @1
1a and the fifth on-off valve 33 from the dilute solution pipe 13, and the other end is connected to the 142 solution heat exchanger 11b and the fourth control 419P221. In between! A pipe 19bK* which once branched off from the solution pipe 19 is connected.

Next, the operation will be explained. The operating points ■ to Φ in FIG. 2 correspond to the state points ■ to 0 in FIGS.

During steady operation of the device, each on-off valve is switched to the third on-off valve 3.
1 is opened, the fourth on-off valve 32 is closed, the fifth on-off valve 33 is opened, and the sixth on-off valve 34 is closed.

At this time, each control valve is in a state where it can fully control the solution flow rate, as in FIG. The solution flow path thus formed is similar to that shown in FIG. 8, and the operation is also realized as shown in FIG. 9.

At startup, each on-off valve is closed, the third on-off valve 31 is closed,
The fourth on-off valve 32 is opened, the fifth on-off valve 33 is closed, and the sixth on-off valve 34 is opened. Further, each control valve is operated so that the third control valve 21 and the fourth control valve 22 are closed, and the fifth control valve 23 is opened. By these operations, at startup, the solution heated in the generated heat exchanger 5 passes through the concentrated solution tube 97 and is discharged by the solution pump 1.0, and is transferred to the first solution heat exchanger 11m.
From there, it passes through the second solution heat exchanger 11b and the fourth on-off valve 32t to reach the intermediate concentration solution pipe 19. This solution further enters the dilute solution pipe 13 from the second solution heat exchanger 11b through the sixth on-off valve 34, and returns to the generator 1 through the first solution heat exchanger 111 and the fifth control valve 23. circuit, that is, the circuit that bypasses the second absorber 4a and the first r& The room temperature solution is replaced with a heated solution. After the replacement, the third on-off valve 31 and the fifth on-off valve 33' are opened, and the fourth on-off valve 32 and the sixth on-off valve 34t are brought into a closed state. Furthermore, each control valve is returned to its normal control state and steady operation is performed.

Next, an embodiment of the present invention corresponding to the conventional apparatus shown in FIG. 10 will be described with reference to FIG. In Fig. 3, the symbols are 1.4m, 4b, 5.8~1G.

11 e, 11 d, 13 m, 13 b, 25 to 28 are
No. 101 shows the same parts as the conventional device. A seventh on-off valve 35 is provided between the second absorber 4a and the second solution heat exchanger 11a to which a 1.3 m dilute solution pipe is connected. 36 is an eighth on-off valve, one end of which is connected to the concentrated solution pipe 9 between the second solution heat exchanger 11.4 and the sixth control valve 25.
It is connected to the ai branched pipe, and the other end is connected to the dilute solution pipe 13m between the second solution heat exchanger 11C and the seventh on-off valve 35.

3T is the ninth on-off valve, which connects the coil 1 absorber 4b of the dilute solution pipe 13b.
and the first solution heat exchanger 11d. Also 3
8 is a tenth on-off valve, one end of which is connected to the first solution heat exchanger 11d;
and the eighth control valve 2T, the other end is connected to the first solution heat exchanger 11d of the dilute solution pipe 13b.
and the ninth on-off valve 37 to the dilute solution pipe 13b.

Next, the production will be explained. During steady operation of the device, each of the on-off valves is operated so that the seventh on-off valve 35 is open, the eighth on-off valve 36 is closed, the ninth on-off valve 3T is open, and the tenth on-off valve 38 is closed. At this time, each control valve is in a state where it can fully control the flow rate of the solution, as in the conventional device shown in FIG. equal.

At the time of startup, the respective on-off valves are operated so that the seventh on-off valve 35 is closed, the eighth on-off valve 36 is open, the ninth on-off valve 3γ is closed, and the tenth on-off valve 38 is open. Further, all control valves, the sixth control valve 25 and the eighth control valve 27 are closed, and the seventh control valve 26 and the ninth control valve 27 are closed.
The control valve 28 is operated to an open state. Through these operations, the heat generated during startup of the device and the solution heated in the exchanger 5 are
The concentrated solution is discharged by the solution pump 10 through the concentrated solution t9, passes through the concentrated solution tube 9a from the second solution heat exchanger 11C, exits from the eighth opening/closing valve 36t, and flows through the dilute solution tube t3a to the second solution heat exchanger. 11C and a flow path returning to the generator 1 via the seventh control valve 26, and a concentrated solution pipe 9bt-through from the first bath liquid heat exchanger 11d,
No. 10 on-off valve 38t - out dilute solution 13b same sound flow #! l
The liquid flows through the solution heat exchanger 11d and the ninth control valve 28t, and then returns to the generator 1 through the flow path. As a result, when the system is stopped, the room temperature solution remaining in the second solution heat exchanger 11c, first solution heat exchanger 11d, concentrated solution tubes 9m, 9b, etc. is replaced with the heated solution. 7th opening/closing box 35 after being replaced
The ninth on-off valve 3γ is opened, the eighth on-off valve 36 and the tenth on-off valve 38t are closed, and each control valve is returned to its normal control state to perform steady operation.

Next, other embodiments of this invention will be explained using Figure t-884 and No. This example will be described later.
In addition, it can also be applied to two-stage absorption heat pumps with FIGS. 2 and 3 cores. In addition, in FIG. 4 and the fifth factor, the same reference numerals as in FIG. 4 indicate the same parts. Furthermore, the refrigerant system including the condenser 2 and evaporator 3 shown in FIG. In the example shown in Fig. 1, the first opening/closing valve 29 and the second opening/closing valve 30t were used to switch the solution flow path during steady operation and startup. The first 30,000 valves were used, 39 tons.
These connection ports are connected to the absorber 4 side of the dilute solution pipe 13 and the solution heat exchanger 11 side, as well as to the piping branched from the concentrated solution 9 between the heat exchanger 11 and the first control valve 12. Then, during steady operation, the generator 1 is connected to the absorber 4 via the concentrated solution pipe 9t, f#, the liquid heat exchanger 11 and the first control valve 12, and then the dilute solution pipe 13t, to the absorber 4, and then the dilute solution pipe 13t, and then #!13. The million valve 39, the solution heat exchanger 11, and the second control valve 14 form a flow path that returns to the generator 1, and at startup, from the generator 1 through the concentrated solution pipe 9, the solution heat exchanger 11 and the m1 million valve 39t - By switching the flow path from the dilute solution pipe 13 to the flow path returning to the generator 1 via the solution heat exchanger 11 and the second control valve 14, the same control and effect as in FIG. 1 can be obtained. 'Similarly, the three-way valve t
-#! The second reason is the third on-off valve 31 and the fourth on-off valve 32.
Or, in place of the force of the fifth on-off valve 33 and the sixth on-off valve 34,
Furthermore, in the 3rd -, the seventh on-off valve 35 and the eighth on-off valve 3
A similar effect can be obtained by providing a three-way valve p instead of the sixth or ninth opening/closing valve 3T and the tenth opening/closing valve 5f3B.

FIG. 5 also shows another embodiment according to the present invention, in which a first on-off valve 29 provided in the dilute solution pipe 13 between the solution heat exchanger 11 and the generator 1 is provided in place of the first on-off valve 29 shown in FIG. 2 control valve 14 is provided between the absorber 4 and the solution heat exchanger 11,
A second control valve 14t is provided at this position, wJ2 control valve 1
4 also has the function of the first on-off valve 29 in FIG. 1, and by switching between steady operation and startup operation, it operates in the same way as the device shown in FIG.
It has the effect of removing This can also be applied to the embodiments of the invention shown in FIGS. 2 and 3, where the fifth on-off valve 3 is shown in FIG.
3t- is removed and the fifth control valve 23t is provided at the position of the fifth on-off valve 33, and the seventh on-off valve 35 and the ninth on-off valve 3Tt are removed for the third cause.

7 control valve 26 to the position of the 7th on-off valve 35, and the 9th control valve 28t? A similar effect can be obtained by installing the 9th open/close *37 position. In the 1st case, the refrigerant system runs from the condenser 2 through the refrigerant liquid pipe 1Tt to the refrigerant pump 18t to the evaporator 3. Regarding the second cause, the refrigerant liquid pipe 17 from the condenser 2. Refrigerant pump 1B
The system from the second evaporator 3m to the first evaporator 3b via the flow rate control 24t has been explained, but these are not particularly limited to those shown in Figure 3 Kanakura. For example, in Fig. 2, instead of the flow path running from the condenser 2 to the second evaporator 3ax and the first evaporator 3b in series, there is a refrigerant pump 18t to a refrigerant liquid pipe 17t after exiting.
- The inner part is connected to the second evaporator 3a and the other to the first evaporator 3b, and each evaporator has a flow control valve 24 at its inlet.
A refrigerant system with parallel flow paths may also be used.

Furthermore, the types of valve on-off valves from the WL1 on-off valve 29 to the 10th on-off valve 38 shown in Figs. Any valve that has a function may be used.

(Effects of the Invention) In the absorption heat pump according to the present invention, the bypass heat pump returns the solution discharged from the generator by the solution pump to the generator via only the solution heat exchanger without passing through the absorption tube. Since a pipe was added to the piping system, the room-temperature solution remaining in the solution heat exchanger, concentrated solution tube, etc. at the time of shutdown bypasses the absorber and is replaced with mg whose temperature has increased. Therefore, from startup to steady operation; b
It has two excellent effects: it can shorten the start-up time, and it can shift to steady operation in a stable operating state.

[Brief explanation of the drawing]

Figure 1 is a diagram showing the configuration of an embodiment of a single-stage absorption heat pump according to the present invention BA-1 Figure 2 is a diagram showing the configuration of an embodiment of a two-stage absorption heat pump according to the present invention, wl
Figure a shows the solution system configuration of another embodiment of the two-stage absorption heat pump according to the present invention. The sixth factor is an explanatory diagram showing the configuration of a conventional single-stage absorption heat pump, and the seventh factor is the operating state of the conventional absorption heat pump shown in the sixth factor. Figure 8 is an explanatory diagram showing the conventional two-stage absorption heat pump at 5 ft. Figure 9 is a temperature-pressure-concentration diagram showing the operating state of the conventional absorption heat pump shown in Figure 8. Figure 10 is an explanatory diagram showing the configuration of a solution system in another conventional two-stage absorption heat pump. 1 is a generator 1, 2 is a l11m device, 3 is an evaporator, 4 is an absorber, 9 is a concentrated solution tube, 10 is a solution pump, 11 is a solution heat exchanger, 12 is a first control valve, 13 is a dilute solution 11 is a refrigerant liquid pipe, 18 is a refrigerant pump, 29 is a first on-off valve, 3G is a second on-off valve, and 39 is a first 30,000 valve. Note that the same reference numerals in the figures indicate the same or corresponding parts.

Claims (5)

[Claims] (1) a generator, a condenser for liquefying refrigerant vapor therefrom, at least one evaporator for evaporating refrigerant liquid supplied from the condenser by a refrigerant pump; at least one absorber adapted to be supplied and connected to the generator via a concentrated solution pipe and a dilute solution pipe via separate flow control valves; In an absorption heat pump having a solution pump that supplies a concentrated solution of a container to the absorber, and at least one solution heat exchanger provided in the concentrated solution tube and the dilute solution tube, An absorption heat pump characterized in that a bypass piping system is provided for returning the discharged solution to the generator via only the at least one solution heat exchanger without passing the solution through the absorber. (2) The bypass piping system consists of a first on-off valve that opens and closes the dilute solution pipe passage on the absorber side, and a second on-off valve that short-circuits and shuts off between the concentrated solution pipe and the dilute solution pipe. An absorption heat pump according to claim 1, characterized in that: (3) The absorption heat pump according to claim 2, wherein the first on-off valve is also used as a flow rate control valve provided in the dilute solution pipe. (4) The absorption heat pump according to claim 1, wherein the bypass piping system is constituted by a three-way valve. (5) The absorption heat pump according to claim 2 or 4, wherein the first and second on-off valves or three-way valves are composed of electromagnetic valves.