JPH10238891A - Engine driven type heat pump apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a higher starting performance by securing the temperature of a cooling water at a high waste heat recovery efficiency even in the course of a heater with a simple structure of a path. SOLUTION: A cooling water jacket 28b of an engine 5, an exhaust heat exchanger 23b and a heat exchanger 8 for radiating heat to a refrigerant-three heat exchangers are interlinked sequentially to form a closed circuit S. A bypass path 29g detouring the cooling water jacket 28b is linked to a circulation path S and a circulation pump 28c is arranged in either a heat radiation side circulation half path S2 where the heat exchanger 8 for radiating heat and the exhaust heat exchanger 23b are arranged with borders at linking points P1 and P2 of the bypass path 29g or an engine side circulation half path S1 on the side where the cooling water jacket 28b is arranged with borders at the points P1 and P2. A switching valve K for changing the proportion of the division or the confluence of cooling water is arranged at one or both of the linking points P1 and P2 so as to change the amount of the cooling water flowing through the bypass path based on the temperature of the cooling water in the half path S1 or the engine depending on the case where the pump is arranged in the S2 and in the S1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine driven heat pump apparatus using an engine as a drive source of a heat pump.

[0002]

2. Description of the Related Art As an engine-driven heat pump apparatus using an engine as a drive source of a heat pump, for example, as disclosed in Japanese Patent Application Laid-Open No. Hei 8-212241, cooling water heated by exchanging heat with an engine is turned into a refrigerant. Heat exchange with the refrigerant of the system in the heat exchanger for heat radiation, that is, the exhaust heat recovery device,
Alternatively, there is a type in which a heat exchanger for heat radiation to the outside converts heat with the outside air. This is a cooling water jacket of the engine that forms an engine-side circulation halfway through which cooling water circulates, and an exhaust heat exchanger, a waste heat recovery unit, and a heat-radiation side circulation halfway through which cooling water circulates through a cooling water path that connects them. The engine-side circulation half-way and the heat-radiation-side circulation half-way are connected via a plurality of connecting paths and an on-off valve, the engine-side circulation half-way is provided with a cooling water pump, and the heat-radiation-side circulation half-way is also provided with a cooling water pump. When the temperature of the cooling water jacket is low, the heat radiation side circulation halfway and the engine side circulation halfway are separated and circulated independently of each other, so that even when the engine is warming up, the exhaust heat exchanger is used. The exhaust gas can be cooled, and the waste heat can be transmitted to the refrigerant.

[0003]

In this apparatus, two cooling water pumps for the engine side circulation halfway and two cooling water pumps for the heat dissipation side circulation halfway are used. Even if it is recovered and the cooling water temperature is lowered to increase the exhaust heat recovery efficiency, the engine water temperature can be secured and the engine can be started, but the passage configuration for connecting the engine side circulation halfway and the heat radiation side circulation halfway is complicated. In addition, a plurality of cooling water pumps are required, which increases the cost.

[0004] The present invention has been made in view of the above points, and has a simple passage configuration and can reduce the number of parts.
It is an object of the present invention to provide an engine-driven heat pump device which is low-cost, can increase the exhaust heat recovery efficiency even during warm-up, can secure the engine water temperature, and improves the startability.

[0005]

In order to solve the above-mentioned problems and to achieve the object, an engine-driven heat pump apparatus according to the first aspect of the present invention comprises an engine cooling water jacket, an exhaust heat exchanger, and a refrigerant. Forming a closed circulation path by sequentially connecting the three heat exchange sections of the heat exchanger for heat radiation to the heat exchanger, and connecting a bypass path bypassing the cooling water jacket in the heat exchange section to the circulation path; The cooling water is circulated from the cooling water jacket to return to the cooling water jacket through the exhaust heat exchanger, and then to the cooling water jacket, or from the cooling water jacket to the heat releasing heat exchanger, and then to the cooling water jacket. A cooling water pump that circulates cooling water through the exhaust heat exchanger and returns to the cooling water jacket is connected to the heat exchanger for heat radiation at two connection points at both ends of the bypass path in the circulation path. The heat-radiation-side circulation half-way on the side where the heat exchanger and the exhaust heat exchanger are arranged, or the engine-side circulation half-way on the side on which the cooling water jacket is arranged with the two connection points as a boundary, of the circulation path In the case where the cooling water pump is disposed in the radiating side circulation halfway, based on the cooling water temperature or the engine temperature in the engine side circulation halfway, at least one of the two temperatures is arranged. When the temperature is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the engine-side circulation halfway, and when at least one of the temperatures is high, the flow rate of the cooling water flowing through the bypass path is When the cooling water flow rate is smaller than the flow rate of the cooling water flowing through the engine-side circulation halfway, and the cooling water pump is disposed in the engine-side circulation halfway, at least one of the two temperatures has When, the flow rate of the cooling water flowing through the bypass path is larger than the flow rate of the cooling water flowing through the radiating side circulation half path, and when at least one of the temperatures is large, the flow rate of the cooling water flowing through the bypass path is changed to the radiating side circulation half path. A switching valve for changing the ratio of the branching or merging of the cooling water is arranged at one or both of the connection points so as to reduce the flow rate of the cooling water flowing through the cooling water. When a single cooling water pump is used and the temperature of the engine is low or the temperature of the cooling water jacket of the engine is low due to the switching of the flow path, the cooling water passes through the heat radiation heat exchanger and enters the engine side circulation halfway. Since the amount of cooling water is reduced, the temperature of the cooling water jacket of the engine can be quickly increased, so that the warm-up of the engine can be hastened and the corrosion of the cylinder can be prevented as described later. Cooling water is reliably circulated to the heat exchanger for exhaust heat, or to the heat exchanger for heat radiation via the exhaust heat exchanger and the engine side circulation halfway, so that waste heat can be recovered to the refrigerant even during warm-up operation of the engine. It becomes possible.

According to a second aspect of the present invention, in the engine-driven heat pump device, when the cooling water pump is disposed in the heat radiating side circulation halfway, at least one of the cooling water temperature and the engine temperature is predetermined. When the temperature is equal to or less than the value, the flow rate from the cooling water pump is caused to flow to the bypass path in an entire amount or almost entirely, and the flow rate of the cooling water flowing in the engine-side circulation half path is set to zero or extremely small. When the flow rate is larger than a predetermined value, the whole or almost all of the flow rate from the cooling water pump is caused to flow to the engine-side circulation halfway, and the flow rate of the cooling water flowing through the bypass path is set to zero or extremely small. I have. As a result, the engine can be warmed up more quickly, and all or most of the cooling water circulating from the exhaust heat exchanger to the radiator exchanger flows. Waste heat can be recovered in the refrigerant.

According to a third aspect of the present invention, in the engine driven heat pump apparatus, three heat exchange sections of a cooling water jacket of the engine, an exhaust heat exchanger, and a heat exchanger for radiating heat to the refrigerant are sequentially connected and closed. A circulation path is formed, a bypass path bypassing the cooling water jacket in the heat exchange section is connected to the circulation path, and the cooling water jacket passes through the heat radiation heat exchanger, and then passes through the exhaust heat exchanger. A cooling water pump that circulates cooling water to return to the cooling water jacket,
Of the circulation path, a heat-radiation-side circulation half-way on the side where the heat-radiation heat exchanger and the exhaust heat exchanger are arranged at two connection points that are both ends of the bypass path, The engine is disposed on one of the engine-side circulation halfways on the side where the cooling water jacket is disposed, with the two connection points as a boundary, and the exhaust heat exchanger downstream of the heat-radiation-side circulation halfway. When the cooling water pump is arranged in the heat radiating side circulation halfway based on the cooling water temperature, when the temperature is low, the cooling water flow rate flowing through the bypass path is larger than the cooling water flow rate flowing through the engine side circulation halfway path. When the temperature is high, the flow rate of the cooling water flowing through the bypass passage is made smaller than the flow rate of the cooling water flowing through the engine-side circulation halfway, and when the cooling water pump is arranged in the engine-side circulation halfway, When the temperature is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the radiation side circulation halfway, and when the temperature is high, the flow rate of the cooling water flowing through the bypass path is made smaller than the flow rate. A switching valve for changing a ratio of a branch or a junction of the cooling water is disposed at one or both of the connection points.
When the engine load is small and the engine output is small,
The amount of waste heat to exhaust gas and the amount of waste heat to the engine cooling water jacket are small. For this reason, even when the engine warm-up is completed, the engine temperature tends to decrease. In this case, the odor component containing sulfur mixed in the fuel gas to evoke a gas leak burns, and gaseous sulfur dioxide condenses in the cylinder and causes corrosion of the cylinder. But,
According to this configuration, the temperature of the cooling water jacket of the engine can be increased, and corrosion can be suppressed. Also, engine waste heat can be used.

According to a fourth aspect of the present invention, in the engine-driven heat pump device, when the cooling water pump is disposed in the heat radiation side circulation half path, the cooling water pump is disposed downstream of the exhaust heat exchanger in the heat radiation side circulation half path. When the cooling water temperature is equal to or less than a predetermined value, the whole or almost all of the flow rate from the cooling water pump is caused to flow to the bypass path, and the flow rate of the cooling water flowing through the engine side circulation half path is set to zero or extremely small, When at least one of the temperatures is larger than a predetermined value, the flow rate from the cooling water pump is caused to flow to the engine-side circulation halfway in all or almost all of the way, and the flow rate of the cooling water flowing in the bypass path is set to zero or extremely small. It is characterized by doing. As a result, more engine waste heat can be used, the temperature of the engine cooling water shacket can be more reliably increased, and corrosion can be less likely to occur.

According to a fifth aspect of the present invention, in the engine driven heat pump device, the switching valve is a thermostat,
It is characterized in that the temperature sensing part is exposed in the engine-side circulation halfway. By using a thermostat as the switching valve, the switching valve operates automatically based on the temperature of the cooling water, so that the circuit configuration is simple and the number of parts can be reduced.

According to a sixth aspect of the present invention, in the engine-driven heat pump device, the switching valve is an electromagnetic valve, and one or both of a water temperature detection sensor and an engine temperature detection sensor for detecting a cooling water temperature of the engine-side circulation halfway. And the electromagnetic valve is controlled by a signal of at least one of the detection sensors. By using a solenoid valve as the switching valve, the solenoid valve can be reliably controlled based on the detected coolant temperature at low cost.

According to a seventh aspect of the present invention, in the engine driven heat pump device, the cooling water pump is an electric pump, a water temperature detection sensor for detecting the cooling water temperature, and the electric pump based on the detected cooling water temperature. And control means for controlling the flow rate of the cooling water. By using an electric pump as the cooling water pump, the cooling water temperature can be ensured even at a low load change by controlling the flow rate of the water pump.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an engine driven air conditioner to which the engine driven heat pump device of the present invention is applied will be described below with reference to the drawings.

FIG. 1 is a diagram showing the overall configuration of an engine-driven air conditioner. Engine driven air conditioner 1
Is an outdoor air conditioning unit (hereinafter, also referred to as an outdoor unit) 2,
And an indoor air conditioning unit 3. The indoor air conditioning unit 3 includes a refrigerant indoor heat exchanger 4, a decompression expansion valve 18.
And a fan for indoor heat exchange (not shown). The outdoor air conditioning unit 2 includes an engine 5, compressors 6, 6
An engine room 7 in which the components are disposed, a main accumulator (hereinafter also referred to as a heat-dissipating heat exchanger, that is, an exhaust heat recovery device) 8,
A piping chamber 10 in which a sub-accumulator 9, an electrical box 50, and a pipeline connecting each device are arranged, a refrigerant outdoor upper heat exchanger 11, a refrigerant outdoor lower heat exchanger 12, and heat for engine cooling water. An outdoor heat exchanger room 14 in which a radiator 13 and the like as an exchanger (hot water heat exchanger) are provided.

A water-cooled gas fuel engine is used as the engine 5, and an intake port of the engine 5 has an intake pipe 21a.
A gas mixer 21b and an air cleaner 21c are connected through the air passage, and the intake pipe 21a penetrates through the top wall of the engine room 7 and the top wall of the outdoor heat exchanger room 14 and opens to the outside. The gas mixer 21b is connected to a gas fuel source by a fuel line 22, and the fuel line 22 is provided with a flow control valve 22a integrated with the gas mixer 21b, a zero governor (not shown), and two solenoid valves (not shown). , To a fuel gas cylinder. The exhaust port of the engine 5 has an exhaust pipe 23a.
Through the exhaust heat exchanger 23b, the exhaust silencer 23c,
The mist separator 23d is connected to the exhaust pipe 23.
a is connected to an exhaust outlet 23e above the outdoor heat exchanger chamber 14. Further, the engine 5 is provided with a lubricating oil tank 24a, and when the amount of lubricating oil decreases, the solenoid valve 24b opens,
Lubricating oil is supplied by gravity.

The output shaft of the engine 5 has a clutch 6a,
The compressors 6, 6 are connected via 6a. Compressor 6
Are connected to a refrigerant outdoor upper heat exchanger 11 and a refrigerant outdoor lower heat exchanger 12 via a refrigerant pipe 16a, a four-way valve 15 switched to a cooling operation position, and a refrigerant pipe 16b. The heat exchangers 11 and 12 are connected to a refrigerant line 16 c, a heat exchange portion 16 e in the main accumulator 8, and a refrigerant line 17.
a and the expansion valve 18 are connected to the refrigerant indoor heat exchanger 4.
b, a four-way valve 15, a refrigerant line 16d, a main accumulator 8, and a sub-accumulator 9, which are connected to the suction ports of the compressors 6, 6. In addition, 102 is a dryer,
103 is a filter for bypassing the liquid.

Reference numerals 900 and 901 denote capillaries;
Reference numerals 10 and 910 each indicate a combination of a temperature detector and a capillary tube, and are for detecting the level of the liquid-phase refrigerant in the main accumulator 8 by detecting the refrigerant temperature. Reference numeral 911 denotes an on-off valve, and 912 denotes an oil discharge passage. When the amount of oil stored in the lower portion of the accumulator increases, the on-off valve 911 is opened manually or automatically so that oil flows from the main accumulator 8 to the sub-accumulator 9. .

An oil separator 19a for separating the lubricating oil in the refrigerant is provided in the middle of the refrigerant pipe 16a. When the amount of the lubricating oil separated by the oil separator 19a exceeds a predetermined value, the oil strainer 19b Is returned to the main accumulator 8 via a solenoid valve 19c that opens when the value exceeds a predetermined value. The lubricating oil is further returned to the compressor 6 via the sub-accumulator 9. The refrigerant line 16a is connected to the main accumulator 8 via an oil strainer 20a and a solenoid valve 20b which opens when the pressure in the line is equal to or higher than a predetermined pressure, thereby avoiding an abnormal increase in refrigerant line pressure.

Reference numeral 90 denotes a solenoid valve, and reference numeral 91 denotes an oil strainer. When cooling, when the load on the refrigerant indoor heat exchanger 4 becomes particularly small, the solenoid valve 90 opens, and the refrigerant bypasses the refrigerant indoor heat exchanger 4. Then, it is made to flow to the main accumulator 8 so as to balance with the load.

The top plate 37e is formed with a discharge opening 37f for discharging the introduced outside air upward. The outside opening 37f allows the outside air to enter the outdoor heat exchanger room 14 through the wire mesh 3.
An outdoor heat exchange blower fan 44 for sucking air from the portions 8a and 38b and discharging the air upward is provided. Further, the central partition plate 40 is formed with two vent air outlets 40 b so as to open into the outdoor heat exchanger chamber 14. The outlet 40b is surrounded by a silence box 40c.

The space between the bottom plate 45 and the floor plate is a box-shaped ventilation passage 46, and the bottom plate 45 has an engine room 7
A large number of ejection ports 45a for blowing out ventilation air are arranged substantially uniformly over the entire surface. In addition, ventilation passage 4
6, two engine room air inlets 46a opening into the piping chamber 10 are formed on the right middle plate 44b side, and a ventilation fan 47 is arranged in each air inlet 46a.

The terminal room 699 is a communication passage connecting the piping room 10 and the indoor air-conditioning unit 3.
Each of the joints 800a, 801a of 801 and the solenoid valve 22c of the fuel line 22 are located in the terminal chamber 699,
99 is connected to an external pipe introduced from below.

A circulation path S of a cooling water circulation system for an outdoor unit as the outdoor air conditioning unit 2 is provided. A circulation path S of the cooling water circulation system includes a cooling water jacket 28 b of the engine 5, a switching valve K, and a circulation path 2 that connects these.
An engine-side circulation half-way S1 comprising 9a1 and 29a2;
Exhaust heat exchanger 23b, linear three-way valve 28d, one is radiator 13, the other is heat exchange part 29g in main accumulator 8, cooling water pump 28e, and circulation passages 29e1, 29e2, 29b, 29c, 29d, 2 communicating these.
9f1,29f2,29p
have. The engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2 form a circulation path when the engine is warmed up when the cooling water temperature exceeds a predetermined value. The communication passage 29q forms a bypass that bypasses the engine-side circulation half-way S1.

The radiator 13 is connected to a cooling water reservoir tank 30a through a water pipe 30c and an inlet 30b. One port of the switching valve K is also connected to the inlet 30b. The port of the switching valve K is always in communication with the cooling water jacket 28b through a throttle, and air can be released from the circulation passages 29a1, 29a2 and the communication passage 29q when the engine is cold. The cooling water reservoir tank 30
A communication passage 30e between the water inlet 30d and the atmosphere is also provided in the upper part of a. The engine cooling water is supplied by a linear three-way valve 2
When 8d is switched, it is supplied to the heat exchanging section 29g in the main accumulator 8 by the water pipe 29h, thereby giving heat to the refrigerant.

The downstream connection point P of the cooling water jacket 28b
1 and the upstream connection point P2, the circulation path S can be divided into an engine-side circulation half-way S1 and a radiation-side circulation half-way S2. In this embodiment, a communication passage 29q connecting both connection points P1 and P2 is provided, and a switching valve K is provided at the downstream connection point P1. This switching valve K shuts off the communication passage 29q when the engine 5 is in a warm-up state, circulates cooling water through the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2, and when the engine 5 is in a cold state. Communication passage 29q
To communicate the cooling water with the radiating side circulation half-way S2 and the communication path 29q.
Switch to cycle.

A bypass passage D is connected to the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2, bypassing the switching valve K, and a throttle d1 is formed in the bypass passage D. The communication passage 29 when the engine 5 is in a cold state
q and the cooling water to the radiating side circulation half-way S2 and the communication path 29.
When circulating through q, a small amount of cooling water can flow by connecting the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2 via the bypass passage D.

If the cooling water does not flow through the cooling water jacket 28b during the operation of raising the temperature of the engine 5, if the cooling water jacket 28b has a hot spot with a large amount of heat generated from a combustion chamber (not shown) of the engine 5 in the cooling water jacket 28b. Boiling may occur, causing thermal corrosion of the engine component walls (particularly in the case of aluminum alloy cylinders and cylinder heads) in that part, but even a small amount of cooling water prevents partial boiling. Thus, thermal corrosion can be prevented.

The cooling water pump 28e is an electric pump, and a water temperature detection sensor T1 for detecting the temperature of the cooling water is provided in the engine side circulation half-way S1, and the cooling water pump 28e is controlled based on the detected cooling water temperature to control the cooling water. By controlling the flow rate of the cooling water and controlling the flow rate of the water pump, the circulation flow rate of the cooling water can be reduced even at the time of a low load change, and the cooling water temperature can be secured. Although the cooling water pump 28e is disposed in the heat-radiation-side circulation half-way S2, it may be disposed in the engine-side circulation half-way S1, and the water temperature detection sensor T1 is disposed in the engine-side circulation half-way S1. The heat radiation side circulation half-way S2 may be arranged.

FIG. 2 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine driven air conditioner. In this embodiment, the members having the same reference numerals as those in the embodiment of FIG. In this embodiment, a switching valve K is disposed at the upstream connection point P2. This switching valve K shuts off the communication passage 29q when the engine 5 is in a warm-up state, and allows the cooling water to communicate with the engine-side circulation half-way S1. In addition to circulating the heat radiation side circulation halfway S2, when the engine 5 is in a cold state, the cooling water is circulated through the communication path 29q to circulate the cooling water to the heat radiation side circulation halfway S2 and the communication path 29q. The bypass passage D bypasses the switching valve K.
Are connected to the engine-side circulation half-way S1 and the radiation-side circulation half-way S2.

As described above, in the embodiment shown in FIGS. 1 and 2, the three heat exchangers of the cooling water jacket 28b, the exhaust heat exchanger 23b, and the heat exchanger 8 for radiating the refrigerant to the refrigerant are sequentially arranged. A closed circulation path S is formed by being connected. A bypass, which is a communication passage 29q that bypasses the inner cooling water jacket 28b of the heat exchange section, is connected to the circulation path S, and the cooling water is cooled from the cooling water jacket 28b through the exhaust heat exchanger 23b and subsequently through the heat radiation heat exchanger 8. The cooling water is circulated to return to the water jacket 28b, or the cooling water is circulated to return to the cooling water jacket 28b from the cooling water jacket 28b, through the heat dissipation heat exchanger 8, and then through the exhaust heat exchanger 23b. The pump 28e is connected to the heat-radiating heat exchanger 8 and the exhaust heat exchanger 23b on the side of the two connecting points P1 and P2, which are both ends of the bypass path, of the circulation path S. S2 or two connecting points P in the circulation path S
The cooling water jacket 28b is disposed on one side of the engine-side circulation half-way S1 on the side where the cooling water jacket 28b is disposed on the boundary between P1 and P2. Based on the temperature of the cooling water in the engine-side circulation halfway S1 or the temperature of the engine, the cooling water pump 28e
Is disposed in the heat radiating side circulation halfway S2, when at least one of the two temperatures is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the engine side circulation halfway S1. When the temperature of the engine becomes high, the flow rate of the cooling water flowing through the bypass
When the cooling water pump is disposed in the engine-side circulation half-way S1 and the temperature of at least one of the two temperatures is low, the cooling water flow through the bypass is reduced to the radiation-side circulation half-way. One of the connection points P1 and P2 is set so that the flow rate of the cooling water flowing through the bypass path is made smaller than the flow rate of the cooling water flowing through the bypass path when the temperature of at least one of the cooling water flows through the bypass path is increased. Alternatively, a switching valve K for changing the ratio of the branching or merging of the cooling water is disposed on both sides.

As described above, when the engine temperature is low or the temperature of the cooling water jacket 28b of the engine 5 is low by using the single cooling water pump 28e and switching the flow path by the switching valve K, the heat radiation The amount of cooling water passing through the heat exchanger 8 and entering the engine-side circulation half-way S1 is reduced,
Since the temperature of the cooling water jacket 28b of the engine 5 can be quickly increased, the warm-up of the engine 5 can be accelerated, and the corrosion of the cylinder of the engine 5 can be prevented as described later, and the heat is radiated from the exhaust heat exchanger 23b. The cooling water surely circulates to the heat exchanger 8 or to the heat-radiating heat exchanger 8 via the exhaust heat exchanger 23b and the engine-side circulation half-way S1, so that even during the warm-up operation of the engine 5, waste heat is generated. Recovery to the refrigerant becomes possible.

In the case where the cooling water pump 28e is disposed in the radiating half-way S2, when at least one of the cooling water temperature and the engine temperature becomes lower than a predetermined value, the flow rate from the cooling water pump 28e is reduced Alternatively, the flow rate of the cooling water flowing through the cooling water pump 28e is reduced to zero or extremely small when the flow rate of the cooling water flowing through the engine-side circulation half-way S1 is reduced to zero or extremely small. Alternatively, almost all of the cooling water flows into the engine-side circulation half-way S1, and the flow rate of the cooling water flowing through the bypass is set to zero or extremely small. As a result, the warm-up of the engine 5 can be further accelerated, and all or almost all of the cooling water circulating from the exhaust heat exchanger 23b to the heat exchanger 8 flows, and during the warm-up operation of the engine 5, Also, more waste heat can be recovered to the refrigerant.

The cooling water jacket 28 of the engine 5
b, the exhaust heat exchanger 23b, and the three heat exchange portions of the heat exchanger 8 for radiating heat to the refrigerant are connected in order to form a closed circulation path S, and the cooling water jacket of the heat exchange section is formed in the circulation path S. 28
cooling water that circulates the cooling water so as to return to the cooling water jacket 28b from the cooling water jacket 28b, and then to the cooling water jacket 28b via the exhaust heat exchanger 23b. The pump 28e is connected to two connection points P1, which are both ends of the bypass path, of the circulation path S.
Radiation heat exchanger 8 and exhaust heat exchanger 23 starting from P2
In the heat-radiation-side circulation half-way S2 on the side where b is disposed, or in the engine-side circulation half-way S1 on the side where the cooling water jacket 28b is disposed on the boundary between the two connection points P1 and P2 in the circulation path S. Arranged on either side, the heat radiation side circulation half path S2
When the cooling water pump 28e is disposed in the heat radiating side circulation halfway S1 based on the cooling water temperature in the downstream portion of the inner exhaust heat exchanger, when the temperature becomes low, the flow rate of the cooling water flowing through the bypass passage is reduced to the engine side circulation halfway. When the flow rate is larger than the flow rate of the cooling water flowing through S1, and when the temperature is high, the flow rate of the cooling water flowing through the bypass is made smaller than the flow rate of the cooling water flowing through the engine-side circulation half-way S1, and the cooling water pump 28e is arranged in the engine-side circulation half-way S1. In this case, when the temperature is low, the flow rate of the cooling water flowing through the bypass path is set to be larger than the flow rate of the cooling water flowing through the heat radiation side circulation halfway S2, and when the temperature is high, the flow rate of the cooling water is set lower than the flow rate of the cooling water flowing through the bypass path. In addition, a switching valve K for changing the ratio of the branching or merging of the cooling water is arranged at one or both of the connection points P1 and P2. Thus, when the engine load is small and the output of the engine 5 is small, the amount of waste heat to the exhaust gas and the amount of waste heat to the cooling water jacket 28b of the engine 5 are small. For this reason, even if engine warm-up has ended,
The engine temperature tends to drop. In this case, the odor component containing sulfur mixed in the fuel gas to induce gas leakage burns, and gaseous sulfur dioxide condenses in the cylinder of the engine 5 and causes corrosion of the cylinder.
However, according to this configuration, the temperature of the cooling water jacket 28b of the engine 5 can be increased, and corrosion can be less likely to occur. Also, engine waste heat can be used.

In the case where the cooling water pump 28e is disposed in the radiating circulation halfway S2, when the cooling water temperature downstream of the exhaust heat exchanger in the radiating circulation halfway S2 becomes lower than a predetermined value,
All or almost all of the flow rate from the cooling water pump 28e is caused to flow to the bypass of the communication path 29q so that the flow rate of the cooling water flowing through the engine-side circulation half-way S1 is set to zero or extremely small, and at least one of the temperatures becomes lower than a predetermined value. When it becomes large, the flow rate from the cooling water pump 28e is caused to flow to the engine-side circulation half-way S1 in its entirety or almost entirely, so that the flow rate of the cooling water flowing through the bypass path is made zero or extremely small. As a result, more engine waste heat can be used, and the temperature of the coolant shacket 28b of the engine 5 can be more reliably increased, so that corrosion is less likely to occur.

That is, in FIGS. 1 and 2, the cooling water pump 28e is disposed on the circulation passages 29p and 29e1,
Although the heat load on the cooling water pump 28e is reduced, the heat exchange in the main accumulator 8 on the circulation passage 29e2 on the downstream side of the exhaust heat exchanger 23b and on the upstream side of the connection point P2 or as a heat release part to the refrigerant is performed. It may be arranged on the circulation passage 29b on the upstream side of the portion 29g for the sake of space or the like. 1 and 2, the exhaust heat exchanger 23
b is arranged upstream of the connection point P2 and downstream of the cooling water pump 28e, and high-temperature cooling water flows into the switching valve K regardless of the switching state. When K is arranged, it becomes possible to use a thermostat. That is, the amount of heat absorbed by the exhaust heat exchanger 23b can be detected whether the temperature sensing unit detects the temperature of the cooling water on the circulation passage 29e2 or the temperature of the cooling water on the circulation passage 29a1. Note that the exhaust heat exchanger 23b may be arranged downstream of the connection point P1. In this case, the connection point P1
A thermostatic switching valve K can be arranged at
It is preferable that the temperature sensing part detects the temperature of the cooling water on the side of the circulation passage 29a2. Thereby, the temperature rising state of the engine 5 can be easily detected. Further, in all of the above, the temperature sensor is separately provided from the cooling water jacket 28 in addition to the switching valve K.
(b) The temperature of the downstream side or the temperature of the cylinder of the engine 5 may be detected, and the switching valve K may be operated based on this temperature.

FIG. 3 is a diagram showing the overall configuration of another embodiment of the engine-driven air conditioner. Engine 201
Is a water-cooled spark ignition type gas engine, which drives a refrigerant compressor 208 via a transmission 202. The transmission 20 provided between the engine 201 and the compressor 208
2 are pulleys 204, 2 fixed to the output shaft 203 of the engine 201 and the input shaft 206 of the compressor 208, respectively.
07, the belt 205 is stretched. A refrigerant circuit 210 for circulating refrigerant by a compressor 208 to the engine 201;
01 and a cooling water circuit 250 for recovering waste heat
The cooling water circuit 250 includes an engine 2
A cooling water jacket 263 and an exhaust heat exchanger 262 provided in an exhaust pipe are incorporated as a waste heat supply unit for cooling water.

The refrigerant circuit 210 is a circuit for circulating refrigerant such as Freon by the compressor 208.
The oil separator 230 is connected to the oil separator 230 by a pipe 211, and the oil separator 230 and the four-way valve 232 are connected to the pipe 21.
2, a four-way valve 232 and a double-pipe heat exchanger 233, which is a heat exchanger for radiating heat to the refrigerant, are connected by a pipe 213, and the double-pipe heat exchanger 233 and a plurality of outdoor heat exchangers 234 are connected. Are connected by a branch pipe 214, and the outdoor heat exchanger 234 and the distributor 236 are connected to a plurality of pipes 215.
And the distributor 236 is connected to the pipeline 21
6 and a plurality of indoor heat exchangers 240 connected by a pipe 217 via electronic expansion valves 238 respectively arranged in the branch portions 217a.
0 and the four-way valve 232 are collectively connected by a pipe 218, and the four-way valve 232 and the compressor 208 are connected by a pipe 219 via an accumulator 245.

In the pipe 219 between the accumulator 245 of the refrigerant circuit 210 and the compressor 208, oil separated from the refrigerant in the oil separator 230 is supplied to the compressor 20.
In order to return to 8, the oil return passage 231 extending from the oil separator 230 is connected via a capillary 270 in the middle. The outdoor heat exchanger 234 disposed between the pipe 214 and the pipe 215 is provided with a fan 325 for blowing air to the outdoor heat exchanger 234, and the pipe 217 and the pipe 218 are provided. The dryer 241 and the strainers 242 and 244 are provided for the plurality of electronic expansion valves 238 and the indoor heat exchanger 240 that are arranged in parallel.
Are deployed respectively.

A flexible tube 300 is disposed in the middle of the pipe 211, and a high-pressure side temperature sensor 303 for detecting the temperature of the refrigerant passing through the pipe 211, and a high-pressure side sensor between the compressor 208 and the electronic expansion valve 238. A high pressure side pressure sensor 301 for detecting the refrigerant pressure of the refrigerant circuit is provided. The high pressure side refrigerant circuit is
During cooling, the pipe 211, the oil separator 230, the pipe 212, the four-way valve 232, the pipe 213, the double pipe heat exchanger 2
33, a pipeline 214, an outdoor heat exchanger 234, a pipeline 215, and a pipeline 216. During heating, the pipeline includes a pipeline 211, an oil separator 230, a pipeline 212, a four-way valve 232, and a pipeline 218. A compressor temperature sensor 306 is provided in the compressor 208, and the flexible pipe 3 is provided in the middle of the pipe 219.
00 are respectively arranged. Further, a low-pressure side pressure sensor 302 that detects the refrigerant pressure of the low-pressure side refrigerant circuit between the electronic expansion valve 238 and the compressor 208 is disposed in the pipe 219. The low-pressure side refrigerant circuit includes a pipe 218 for cooling, a four-way valve 232, and a pipe 219 in which an accumulator 245 is disposed in the middle, and a liquid-gas heat exchanger 2 for heating.
33, pipe 216, pipe 215, outdoor heat exchanger 234,
It comprises a pipe 214, a double pipe heat exchanger 233, a pipe 213, a four-way valve 232 and a pipe 219.

The refrigerant circuit 210 includes an oil separator 2
30 and the middle of the pipeline 212 connecting the four-way valve 232;
A refrigerant bypass path 220 is provided between the four-way valve 232 and a portion of the pipe 219 connecting the compressor 208 before the accumulator 245.
An opening / closing control valve 221 serving as a flow control valve and an opening / closing valve for adjusting the flow rate of the bypassed refrigerant is installed in the middle of the step.

On the other hand, in the cooling water circuit 250, an exhaust heat exchanger 262 is connected to a cooling water pump 261 by a pipe 251, and an exhaust heat exchanger 262 provided in an exhaust pipe of the engine 201 and a cooling water jacket 263 are connected to a pipe. The cooling water jacket 263 and the switching valve 264 are connected by a pipe 253, the switching valve 264 and the outdoor radiator 265 are connected by a pipe 254, and the outdoor radiator 2
65 and the water tank 267 are connected by a pipe 255, the middle of the pipe 255 and the cooling water pump 261 are connected by a pipe 257, and the pipe 257 and the switching valve 264 are connected via a double pipe heat exchanger 233. The pipe 256 is connected, the exhaust heat exchanger 262 and the pipe 254 are connected by the pipe 258, and the pipe 258 and the water tank 267 are connected by the pipe 259. A throttle valve 268 is provided in the pipe 258, and the pipes 258 and 259 are used as passages for venting air. The pipe 255 is used as a passage for replenishing cooling water, and is connected to the outdoor radiator 265. Used as a passage for circulating cooling water toward the water pump.
The outdoor radiator 265 includes the outdoor radiator 265.
Is provided with a fan 266 for blowing air to.

The double tube heat exchanger 233 provided between the refrigerant circuit 210 and the cooling water circuit 250 exchanges heat between the refrigerant flowing through both circuits and the cooling water. An intake pipe 317 is connected to the engine 201, and an air cleaner 318 is disposed upstream of the intake pipe 317.
A mixer 319 for mixing gaseous fuel and a throttle valve 320 downstream of the mixer 319 are arranged at the downstream side of. The opening and closing of the throttle valve 320 is controlled by a throttle valve opening control actuator 311 composed of a step motor. A gas discharge port is provided in the venturi section of the mixer 319, and the fuel gas flow control valve 31
2. A gas supply line 316 having a pressure reducing valve 313 and two on-off valves 314 and connected to a fuel gas supply source 315 is connected. Further, the engine 201 has an exhaust pipe 3
23 is connected, and the exhaust heat exchanger 2
Exhaust gas can be discharged to the atmosphere via 62. The engine 201 is provided with an engine speed sensor 310 for detecting the engine speed.

In this embodiment, the circulation path S of the cooling water circulation system is connected to the cooling water jacket 26 of the engine 201.
3. Switching valve K, circulation passages 252a, 252 for communicating these
52b, an exhaust heat exchanger 262, a switching valve 264, one of which is an outdoor radiator 26.
5, the other is a double tube heat exchanger 233, a cooling water pump 26
1. Pipelines 252, 253, 254, 2 connecting these
It has a heat-radiation-side circulation half-way S2 composed of 55, 256, and 257. Engine-side circulation half-way S1 and heat radiation-side circulation half-way S
2, a circulation path for warming up the engine when the coolant temperature exceeds a predetermined value is formed. The communication path 270 forms a bypass path.

The downstream connection point P of the cooling water jacket 270
1 and the upstream connection point P2, the circulation path S can be divided into an engine-side circulation half-way S1 and a heat-radiation-side circulation half-way S2, and in this embodiment, a link connecting both connection points P1 and P2 is considered. A passage 270 is arranged, and the switching valve K is connected to the downstream connection point P1.
Is arranged. The switching valve K shuts off the communication passage 270 when the engine 201 is in a warm-up state, circulates the cooling water through the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2, and when the engine 201 is in a cold state. The communication is switched so that the cooling water is circulated through the communication passage 270 and circulates through the heat radiating half-way S2 and the communication passage 270.

A bypass passage D is connected to the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2, bypassing the switching valve K, and a throttle d1 is formed in the bypass passage D. When the cooling water is circulated through the communication passage 270 and the cooling water is circulated through the communication halfway S2 and the communication passage 270 when the engine 201 is in a cold state, the engine side circulation halfway S1 and the heat dissipation side circulation halfway S2 are connected through the bypass passage D. Then a small amount of cooling water can flow.

Further, the cooling water pump 261 is an electric pump, and a water temperature detecting sensor T1 for detecting the cooling water temperature is provided in the engine side circulation halfway S1, and the cooling water pump 28e is controlled based on the detected cooling water temperature to control the cooling water. By controlling the flow rate of the cooling water and controlling the flow rate of the water pump, the circulation flow rate of the cooling water can be reduced even at the time of a low load change, and the cooling water temperature can be secured. Although this cooling water pump 261 is arranged in the heat-radiation-side circulation half-way S2, it may be arranged in the engine-side circulation half-way S1, and the water temperature detection sensor T1 is arranged in the engine-side circulation half-way S1. The heat radiation side circulation half-way S2 may be arranged.

FIG. 4 is a diagram showing the configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. In this embodiment, the members having the same reference numerals as those in the embodiment of FIG. In this embodiment, a switching valve K is disposed at the upstream connection point P2. The switching valve K shuts off the communication passage 270 when the engine 201 is in a warm-up state, and allows the cooling water to communicate with the engine-side circulation half-way S1. When the engine 201 is in a cold state, the communication path 2
70 and communicates the cooling water with the heat radiation side circulation half-way S2 and the communication path 2
Circulate to 70. Bypassing the switching valve K, a bypass passage D is connected to the engine-side circulation half-way S1 and the heat radiation-side circulation half-way S2.

As described above, in the embodiment shown in FIGS. 3 and 4, the double-tube heat exchanger 233 which is a heat exchanger for radiating heat to the cooling water jacket 263, the exhaust heat exchanger 262, and the refrigerant of the engine 201 is provided. Are sequentially connected to form a closed circulation path S. A bypass, which is a communication path 270 that bypasses the inner cooling water jacket 263 of the heat exchange section, is connected to the circulation path S, and the cooling water jacket 263 passes through the exhaust heat exchanger 262, and then passes through the double pipe heat exchanger 233. The cooling water is circulated so as to return to the cooling water jacket 263, or the cooling water jacket
3. A cooling water pump 2 for circulating the cooling water to return to the cooling water jacket 263 via the exhaust heat exchanger 262.
Reference numeral 61 denotes a heat-radiation-side circulation half-way on the side where the double-pipe heat exchanger 233 and the exhaust heat exchanger 23b are arranged with the two connection points P1 and P2 at both ends of the bypass in the circulation path S as boundaries. The cooling water jacket 263 is disposed at one of S2 and the engine-side circulation half-way S1 on the side where the cooling water jacket 263 is disposed, with the two connection points P1 and P2 as boundaries. In the case where the cooling water pump 261 is disposed in the heat radiation side circulation halfway S2 based on the temperature of the cooling water in the engine side circulation halfway S1 or the engine temperature, when at least one of the two temperatures becomes small, the coolant flows through the bypass path. The cooling water flow rate is made larger than the cooling water flow rate flowing through the engine-side circulation half-way S1, and when at least one of the temperatures increases, the cooling water flow rate flowing through the bypass path is made smaller than the cooling water flow rate flowing through the engine-side circulation half-way S1. When the cooling water pump is disposed in the engine-side circulation half-way S1, when at least one of the two temperatures is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the heat-radiation side circulation half-way S2. When at least one of the temperatures is large, the flow rate of the cooling water flowing through the bypass path is set to be smaller than the flow rate of the cooling water flowing through the heat radiating half-way S1. P1, one or both of the P2 placing shunt or switching valve K to vary the percentage of confluence of the cooling water.

Also in the case of this embodiment, by using a single cooling water pump 261 and switching the flow path by the switching valve K,
If the engine temperature is low or the temperature of the cooling water jacket 263 of the engine 201 is low, the double-tube heat exchanger 233
, The amount of cooling water entering the engine-side circulation half-way S1 decreases, and the temperature of the cooling water jacket 263 of the engine 201 can be quickly increased.
In addition to preventing corrosion of the first cylinder, the cooling water is discharged from the exhaust heat exchanger 262 to the double pipe heat exchanger 233 or to the double pipe heat exchanger 233 via the exhaust heat exchanger 262 and the engine-side circulation half-way S1. Since the circulation is ensured, the waste heat can be recovered to the refrigerant even during the warm-up operation of the engine 201.

In the case where the cooling water pump 261 is disposed in the radiating half-way S2, when at least one of the cooling water temperature and the engine temperature becomes equal to or lower than a predetermined value, the flow rate from the cooling water pump 261 is completely reduced. Alternatively, the flow rate of the cooling water flowing through the cooling water pump 261 is almost completely reduced to zero or a very small amount by flowing the cooling water to the bypass passage, and the flow rate of the cooling water from the cooling water pump 261 is completely reduced when at least one of the temperatures is higher than a predetermined value. Alternatively, almost all of the cooling water flows into the engine-side circulation half-way S1, and the flow rate of the cooling water flowing through the bypass is set to zero or extremely small. As a result, the warming-up of the engine 201 can be accelerated, and all or most of the cooling water circulating from the exhaust heat exchanger 262 to the double-pipe heat exchanger 233 flows. Inside
More waste heat can be recovered to the refrigerant.

Further, the cooling water jacket 263 of the engine 201, the exhaust heat exchanger 262, and the three heat exchanging portions of the double tube heat exchanger 233 for the refrigerant are connected in order to form a closed circuit S
The circulation path S is connected to a bypass of a communication path 270 that bypasses the inner cooling water jacket 263 of the heat exchange section.
3. A cooling water pump 2 for circulating the cooling water to return to the cooling water jacket 263 via the exhaust heat exchanger 262.
61 is a heat radiation side circulation half-way on the side where the double pipe heat exchanger 233 and the exhaust heat exchanger 262 are arranged with the two connection points P1 and P2 serving as both ends of the bypass path in the circulation path S as boundaries. S2 or one of the engine-side circulation half-ways S1 on the side where the cooling water jacket 263 is arranged, with the two connection points P1 and P2 as boundaries.
Based on the temperature of the cooling water downstream of the exhaust gas heat exchanger in the heat radiating half circuit S2, the cooling water pump 261 is switched to the heat radiating half circuit S1.
When the temperature is low, the flow rate of the cooling water flowing through the bypass passage is made larger than the flow rate of the cooling water flowing through the engine-side circulation half-way S1 when the temperature is low. When the cooling water pump 261 is arranged in the engine-side circulation half-way S1 when the flow rate of the cooling water flowing through the side-circulation half-way S1 is smaller than that in the engine-side circulation half-way S1, the flow rate of the cooling water flowing through the bypass path is reduced by the radiation-side circulation half-way S2 when the temperature is low. The flow rate of the cooling water flowing is set to be larger than the flow rate of the cooling water.
A switching valve K for changing the ratio of the branching or merging of the cooling water is arranged in one or both of P1 and P2. Thus, when the engine load is small and the output of the engine 201 is small, the amount of waste heat to the exhaust gas and the amount of waste heat to the cooling water jacket 263 of the engine 201 are small. For this reason, even when the engine warm-up is completed, the engine temperature tends to decrease. In this case, an odor component containing sulfur mixed in the fuel gas to evoke gas leakage burns, and gaseous sulfur dioxide is condensed in the cylinder of the engine 201 and causes corrosion of the cylinder. The temperature of the cooling water jacket 263 of the engine 201 can be increased, corrosion can be less likely to occur, and engine waste heat can be used.

In the case where the cooling water pump 261 is disposed in the radiating side circulation half-way S2, when the cooling water temperature in the downstream portion of the exhaust heat exchanger of the radiating side circulation half-way S2 becomes lower than a predetermined value,
All or almost all of the flow rate from the cooling water pump 261 is caused to flow to the bypass of the communication path 270 so that the flow rate of the cooling water flowing through the engine-side circulation half-way S1 is made zero or extremely small, and at least one of the temperatures becomes lower than a predetermined value. When it becomes large, the entire or almost all of the flow rate from the cooling water pump 261 flows to the engine-side circulation half-way S1, so that the flow rate of the cooling water flowing through the bypass path is set to zero or extremely small. As a result, more waste heat of the engine can be used, and the temperature of the cooling water shaket 263 of the engine 201 can be more reliably increased, so that corrosion can be made more unlikely.

FIG. 5 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. In this embodiment, the members having the same reference numerals as those in the embodiment of FIG. In this embodiment, an indoor heat exchanger 240 is arranged in parallel between a branch pipe 216a connected to the pipe 216 and a branch pipe 218a of the pipe 218, and the electronic expansion valve 238 is connected to the branch pipe 216a. , Strainers 291 are arranged. A dryer 241 and a valve 290 are arranged in the pipeline 216, and a valve 292 and a strainer 293 are arranged in the pipeline 218. Further, a pipeline 294 is connected to the pipeline 216, and a plurality of indoor heat exchangers are connected to the pipeline 294 and the pipeline 218 via the branch pipelines as described above.

A control valve 280 is disposed in the line 253 instead of the switching valve 264 in FIG.
Switching between 56 and the conduit 254 is performed, and the flow rate of the cooling water is controlled. A switching valve K is disposed at the downstream connection point P1, and a water tank 267 is connected to the switching valve K by a pipe 259. The conduit 259 is used as a passage for venting air.

FIG. 6 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. In this embodiment, the switching valve K is connected to the upstream connection point P2.
Are arranged, and the members denoted by the same reference numerals as those in the embodiment of FIGS. 4 and 5 have the same configuration and operation, and therefore the description thereof will be omitted.

FIG. 7 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. In this embodiment, the switching valve K is connected to the downstream connection point P1.
Are arranged, and the members having the same reference numerals as those in the embodiment of FIG. 3 have the same configuration and operation, and therefore description thereof will be omitted. In this embodiment, the distributor 236 and the liquid receiver 610 are connected via a line 216, and the line 216
Is provided with a strainer 281 and an expansion valve 282, and the expansion valve 282 has a check valve 283.
4 are connected. The liquid / gas heat exchanger 237 connected to the pipe 218 is connected to the liquid receiver 610 via a pipe 285, and a dryer 286 is disposed in the pipe 285. A plurality of indoor heat exchangers 240 are connected to the liquid-gas heat exchanger 237 via an electronic expansion valve 238 and a strainer 239 respectively arranged in a branch part 217a.
Connected by The pipe 212 and the distributor 236 are connected via a pipe 287, and the pipe 287
, An on-off valve 288 and a check valve 289 are arranged.

A water tank 267 is connected to an exhaust heat exchanger 262 provided in an exhaust pipe of the engine 201 via a pipe 400 and a pipe 401. A pipeline 402 is connected to the pipeline 253 and the pipeline 400, and the pipeline 402 is connected to an exhaust heat exchanger 262 via a pipe 403. A pair of check valves 404 and 405 are connected to the pipe 402, and a pipe 259 and a pipe 258 are connected between the check valves 404 and 405.

FIG. 8 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. In this embodiment, the switching valve K is connected to the upstream connection point P2.
Are arranged, and the members having the same reference numerals as those in the embodiment of FIGS. 4 and 7 have the same configuration and operation, and therefore the description thereof will be omitted.

FIG. 9 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner. 9 (a) and 9 (b) are configured similarly to the embodiment of FIG. 3, but in the embodiment of FIG. 9 (a), the cooling water pump 261 is used to cool the engine-side circulation half-way S1. It is arranged on the upstream side of the water jacket 263, and in the embodiment of FIG. 9B, it is arranged on the downstream side of the cooling water jacket 263.

In this embodiment, when at least one of the cooling water temperature and the engine temperature is low, the flow rate of the cooling water flowing through the bypass of the communication passage 270 is larger than the flow rate of the cooling water flowing through the radiating half-way S2. Then, when at least one of the temperatures is high, cooling is performed to one or both of the connection points P1 and P2 so that the flow rate of the cooling water flowing through the bypass path of the communication path 270 is made smaller than the flow rate of the cooling water flowing through the radiating half-way S2. A switching valve K for changing the ratio of water divergence or merging is provided. This embodiment also uses a single cooling water pump 261 and has a similar operation and effect by switching the flow path.

When the temperature is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the heat radiating half-way S2, and when the temperature is high, the flow rate of the cooling water is made lower than the flow rate of the cooling water flowing through the bypass path. As described above, the switching valve K that changes the ratio of the branch or the merge of the cooling water is disposed at one or both of the connection points P1 and P2. As a result, when the engine load is small and the output of the engine 201 is small, the amount of waste heat to the exhaust gas and the amount of waste heat to the cooling water jacket 263 of the engine 201 are small, so even if the engine warm-up is finished, the engine temperature tends to decrease. For example, it has the same operation and effect as the embodiment of FIG.

Further, in this embodiment, the cooling water pump 261 is an electric pump, and the control means F controls the electric pump to control the flow rate of the cooling water based on the cooling water temperature detected by the water temperature detection sensor T1. ing. Cooling water pump 26
When 1 is an electric pump, the temperature of the cooling water can be ensured by the water pump flow control even when the load is low.

FIG. 10 is a diagram showing the configuration of another embodiment of the switching valve. In this embodiment, the switching valve K is a thermostat, and FIG. 10A shows the arrangement position of the thermostat K10, and is applied to the switching valve K arranged at the downstream connection point P1. As shown in FIGS. 10B and 10C, the thermostat K10 has a valve element 500 and a temperature sensing portion 501 exposed in the engine circulation path, and a bypass passage 500a is formed in the valve element 500. ing. The temperature sensing part 501 changes according to the temperature of the cooling water, and the port k1 is closed.
2 and k3, the cooling water can be circulated through the radiation side circulation half-way S2, the port k2 is closed, and the port k is closed.
When 1 and k3 are communicated, cooling water can be circulated through the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2. This thermostat K10 is applied to the switching valve K arranged at the downstream connection point P1 in the embodiment shown in FIGS. 1, 3, 5, 7, and 9, and in this case, the thermostat K10 has a bypass passage 500a. The bypass passage D that bypasses the switching valve K from the valve is unnecessary. Note that a mechanical centrifugal pump driven by a belt by a pulley provided on a crankshaft (not shown) may be used instead of the electric pump. Thus, the cooling water can be constantly circulated during the operation of the engine.

FIG. 11 is a diagram showing the configuration of another embodiment of the switching valve. In this embodiment, the switching valve K is a thermostat K10, and FIG.
And is applied to the switching valve K arranged at the upstream connection point P2. The thermostat K10 is shown in FIG.
As shown in (b), the valve body 510, 511 has a temperature sensing portion 512, and the valve body 510, 511 has a bypass passage 5.
10a and 511a are formed. The temperature sensing portion 512 changes according to the temperature of the cooling water, and the port k5 is closed.
4 and k6, the cooling water can be circulated through the radiation side circulation half-way S2, the port k6 is closed, and the port k is closed.
When 4 and k5 are communicated, cooling water can be circulated through the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2. This thermostat K10 is shown in FIGS. 2, 4, 6, and 8.
In this case, the thermostat K10 has the bypass passages 510a and 511a, so that the bypass passage D for bypassing the switch valve K is unnecessary. As described above, by setting the switching valve K to the thermostat K10, the switching valve K automatically operates based on the temperature of the cooling water, so that the circuit configuration is simple and the number of parts can be reduced.

FIG. 12 is a diagram showing the configuration of another embodiment of the switching valve. In this embodiment, the switching valve K is replaced by a solenoid valve K
20 and FIG. 12 (a) and FIG.
Reference numeral 20 denotes a three-way valve. FIG. 12A is disposed at an upstream connection point P2, and FIG. 12B is disposed at a downstream connection point P1.

Water temperature detection sensor T1 for detecting the temperature of cooling water
12A, the solenoid valve K20 is controlled based on the detected coolant temperature. In FIG.
4 and k6, the cooling water can be circulated through the radiation side circulation half-way S2, the port k6 is closed, and the port k is closed.
When 4 and k5 are communicated, cooling water can be circulated through the engine-side circulation half-way S1 and the heat-radiation-side circulation half-way S2. In FIG. 12B, when the port k1 is closed and the ports k2 and k3 are connected to each other, the cooling water can be circulated to the heat radiation side circulation halfway S2. When the port k2 is closed and the ports k1 and k3 are connected, the engine side circulation is performed. Half path S1 and radiation side circulation half path S
2 can circulate cooling water.

FIG. 12C and FIG. 12D show that the solenoid valve K30 is an open / close valve. FIG. 12C shows one solenoid valve K30a arranged downstream of the upstream connection point P2, and another solenoid valve K30b arranged between the upstream connection point P2 and the downstream connection point P1. ing. A water temperature detection sensor T1 for detecting the temperature of the cooling water, and the solenoid valves K30a and K30b are controlled based on the detected cooling water temperature.
In (c), by closing the solenoid valve K30a and opening the solenoid valve K30b, it is possible to circulate the cooling water in the radiating half-way S2. By closing the solenoid valve K30b and opening the solenoid valve K30a, the engine-side circulation is performed. Half path S1 and radiation side circulation half path S
Cooling water can be circulated in two paths.

FIG. 12D shows that one solenoid valve K30c is arranged downstream of the downstream connection point P1, and the other solenoid valve K30c
30d is arranged between the downstream connection point P1 and the upstream connection point P2. Water temperature sensor T for detecting cooling water temperature
1 and the solenoid valve K30 based on the detected coolant temperature.
c, by controlling the solenoid valve K30d, and in FIG. 12 (d), by closing the solenoid valve K30c and opening the solenoid valve K30d, it is possible to circulate the cooling water through the radiation side circulation half-way S2, and close the solenoid valve K30d. By opening the solenoid valve K30c, the cooling water can be circulated through the engine-side circulation half-way S1 and the radiation-side circulation half-way S2. Also, the engine temperature detection sensor T
12 is arranged, and the solenoid valve K20 of FIGS. 12 (a) and 12 (b) or FIG.
(C) and (d) solenoid valves K30a, K30b, K30
c, K30d may be controlled. As described above, by using the switching valve as the solenoid valve, the solenoid valve can be reliably controlled based on the detected coolant temperature at low cost.

[0068]

As described above, according to the first aspect of the present invention, a single cooling water pump is used and the flow path is switched.
If the temperature of the engine is low or the temperature of the cooling water jacket of the engine is low, the amount of cooling water passing through the heat radiation heat exchanger and entering the half circulation path on the engine side will decrease, and the temperature of the cooling water jacket of the engine will decrease. Since the engine can be quickly raised, the engine warm-up can be accelerated and the cylinder can be prevented from being corroded, as will be described later. In addition, the exhaust heat exchanger can be radiated to the heat exchanger, or the exhaust heat exchanger and the engine can be circulated. Since the cooling water reliably circulates through the half-way to the heat-radiating heat exchanger, it is possible to recover the waste heat into the refrigerant even during the warm-up operation of the engine.

According to the second aspect of the present invention, the warm-up of the engine can be accelerated, and all or most of the cooling water circulating from the exhaust heat exchanger to the heat radiating exchanger flows. Even during the warm-up operation, more waste heat can be recovered to the refrigerant.

According to the third aspect of the present invention, when the engine load is small and the engine output is small, the amount of waste heat to the exhaust gas and the amount of waste heat to the cooling water jacket of the engine are small. For this reason, even when the engine warm-up is completed, the engine temperature tends to decrease. In this case, the odor component containing sulfur mixed in the fuel gas to evoke a gas leak burns, and gaseous sulfur dioxide condenses in the cylinder and causes corrosion of the cylinder. However, according to this configuration, the temperature of the cooling water jacket of the engine can be increased, corrosion can be less likely to occur, and engine waste heat can be used.

According to the fourth aspect of the present invention, it is possible to use the engine waste heat more, to increase the temperature of the engine cooling water shacket more reliably, and to make the corrosion less likely to occur. it can.

According to the fifth aspect of the present invention, since the switching valve is a thermostat, it automatically operates based on the temperature of the cooling water, so that the circuit configuration is simple and the number of parts can be reduced.

According to the sixth aspect of the present invention, since the switching valve is an electromagnetic valve, the electromagnetic valve can be reliably controlled based on the detected cooling water temperature at low cost.

According to the seventh aspect of the present invention, by using an electric pump as the cooling water pump, the water pump flow rate can be controlled.
Cooling water temperature can be ensured even at low load fluctuations.

[Brief description of the drawings]

FIG. 1 is a diagram showing an overall configuration of an engine-driven air conditioner.

FIG. 2 is a diagram illustrating a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 3 is a diagram showing an overall configuration of another embodiment of an engine-driven air conditioner.

FIG. 4 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 5 is a diagram illustrating a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 6 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 7 is a diagram showing a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 8 is a diagram illustrating a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 9 is a diagram illustrating a configuration of a cooling water circulation system according to another embodiment of the engine-driven air conditioner.

FIG. 10 is a diagram showing a configuration of another embodiment of the switching valve.

FIG. 11 is a diagram showing a configuration of another embodiment of a switching valve.

FIG. 12 is a diagram showing a configuration of another embodiment of the switching valve.

[Explanation of symbols]

 5 Engine 28b Cooling water jacket 28e Cooling water pump 29q Communication path S1 Engine-side circulation half-way S2 Radiation-side circulation half-way S Cooling water circulation system P1 Downstream connection point P2 Upstream connection point K Switching valve

Claims (7)

[Claims] 1. A closed circulation path is formed by sequentially connecting three heat exchange portions of a cooling water jacket of an engine, an exhaust heat exchanger, and a heat exchanger for radiating heat to a refrigerant, and forms a closed circulation path. A bypass passage bypassing the cooling water jacket is connected to the cooling water jacket, and cooling water is circulated from the cooling water jacket to the exhaust heat exchanger, and then to the cooling water jacket via the heat radiation heat exchanger. Alternatively, a cooling water pump that circulates cooling water from the cooling water jacket to the heat radiation heat exchanger, and subsequently to the cooling water jacket through the exhaust heat exchanger, may include: Or a heat radiation side circulation half-way on the side where the heat radiation heat exchanger and the exhaust heat exchanger are disposed, or a boundary between the two connection points in the circulation path. As the cooling water The cooling water pump is arranged in one of the engine-side circulation half-circuits on the side where the bracket is arranged, and the cooling-water pump is arranged in the heat-radiation-side circulation half-circuit based on the cooling water temperature or the engine temperature in the engine-side circulation half-way. When at least one of the two temperatures is low, the flow rate of the cooling water flowing through the bypass passage is made larger than the flow rate of the cooling water flowing through the engine-side circulation half-way, and the temperature of at least one of the two temperatures increases. When the flow rate of the cooling water flowing through the bypass passage is smaller than the flow rate of the cooling water flowing through the engine-side circulation half-way, and when the cooling-water pump is disposed in the engine-side circulation half-way, at least one of the two temperatures is used. When the temperature of the cooling water decreases, the flow rate of the cooling water flowing through the bypass passage is made larger than the flow rate of the cooling water flowing through the radiating half circulation path, and the temperature of the at least one of A switching valve for changing a ratio of a branch or a junction of the cooling water to one or both of the connection points so that a cooling water flow rate flowing through the bypass path is smaller than a cooling water flow rate flowing through the radiating circulation halfway when the flow rate is large. An engine-driven heat pump device comprising: 2. When the cooling water pump is disposed in the heat radiating side circulation halfway, when at least one of the cooling water temperature and the engine temperature becomes equal to or lower than a predetermined value, the flow rate from the cooling water pump is reduced. All or almost all of the cooling water flows into the bypass path, and the flow rate of the cooling water flowing through the engine-side circulation half path is set to zero or extremely small,
When the at least one temperature is higher than a predetermined value, the flow rate from the cooling water pump is caused to flow to the engine-side circulating halfway path in the entire amount or almost all of the way, and the flow rate of the cooling water flowing through the bypass path is set to zero or negligible. The engine-driven heat pump device according to claim 1, wherein 3. A closed circuit is formed by sequentially connecting three heat exchangers of a cooling water jacket of an engine, an exhaust heat exchanger, and a heat exchanger for radiating heat to a refrigerant, and forms a closed circuit. Connecting a bypass which bypasses the cooling water jacket in the portion, from the cooling water jacket to the heat radiating heat exchanger,
Subsequently, a cooling water pump that circulates cooling water through the exhaust heat exchanger and returns to the cooling water jacket is connected to two connection points at both ends of the bypass path in the circulation path. The heat-radiation-side circulation half-way on the side where the heat exchanger and the exhaust heat exchanger are disposed, or the engine side on the side where the cooling water jacket is disposed with the two connection points as a boundary, in the circulation path In the case where the cooling water pump is disposed in the heat radiation side circulation half path, based on the cooling water temperature of the exhaust heat exchanger downstream of the heat radiation side circulation half path, When the temperature is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the engine-side circulation halfway. When the temperature is high, the flow rate of the cooling water flowing through the bypass path is changed to the engine-side circulation halfway. Less than the flow rate of cooling water flowing,
When the cooling water pump is arranged in the engine-side circulation halfway, when the temperature is low, the flow rate of the cooling water flowing through the bypass path is made larger than the flow rate of the cooling water flowing through the heat-radiation side circulation halfway, and the temperature is reduced. An engine-driven type, wherein a switching valve for changing a ratio of a branch or a junction of the cooling water is disposed at one or both of the connection points so as to be smaller than a flow rate of the cooling water flowing through the bypass passage when the flow becomes large. Heat pump device. 4. When the cooling water pump is disposed in the radiating half-circle, when the temperature of the cooling water downstream of the exhaust heat exchanger in the radiating half-circle becomes lower than a predetermined value, the cooling water is reduced. All or almost all of the flow from the pump is allowed to flow to the bypass path, and the flow rate of the cooling water flowing through the engine-side circulation half-way is set to zero or extremely small, and when the temperature of at least one of them is greater than a predetermined value, 4. The engine according to claim 3, wherein all or almost all of the flow rate from the cooling water pump flows to the engine-side circulation half-way, and the flow rate of the cooling water flowing through the bypass path is reduced to zero or extremely small. Uproar heat pump device. 5. The engine-driven heat pump according to claim 1, wherein the switching valve is a thermostat, and the temperature sensing part is exposed in the engine-side circulation halfway. apparatus. 6. The switching valve is an electromagnetic valve, and one or both of a water temperature detection sensor and an engine temperature detection sensor for detecting a cooling water temperature of the engine-side circulation halfway is disposed, and the signal of at least one of the detection sensors is provided. 5. The electromagnetic valve according to claim 1, wherein the solenoid valve is controlled.
The engine-driven heat pump device according to any one of the above. 7. A cooling water pump comprising an electric pump, a water temperature detecting sensor for detecting the cooling water temperature, and control means for controlling the electric pump based on the detected cooling water temperature to control the flow rate of the cooling water. The engine-driven heat pump device according to any one of claims 1 to 6, further comprising: