JPH0968363A - Engine type heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an engine type heat pump device, capable of eliminating the deterioration of a heating capacity due to the lowering of an outside temperature in a cold district. SOLUTION: A heat source machine 10 supplies thermal operating fluid for heating to an indoor machine 80. An engine 1 drives the compressing unit 2 of a heat pump functioning part of the heat source machine 10. An outdoor heat exchanger 5 provides the thermal operating fluid for heating with an outside temperature to heat it. The calorific value of exhaust gas of the engine 1 and a waste heat 1A due to cooling calorific value are given to a heat exchanger 5 through a heat exchanger 5A. When the outside temperature is reduced to a value lower than a predetermined temperature, a mixing ratio regulating unit 1B increases the air excessive rate of the mixed gas of fuel and air, supplied to the engine 1, or an ignition timing regulating unit 1C delays the ignition period of the engine 1. The increase of the air excessive rate and the delay of ignition timing increase the calorific value of waste heat 1A of the engine 1 respectively to supplement the deterioration of heating in the heat exchanger 5 whereby the deterioration of heating capacity due to the reduction of the outside temperature. Exhaust gas can be given directly to the heat exchanger 5 through a heat discharging pipeline 141.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine, that is, a heat pump device powered by an internal combustion engine (in this invention, referred to as an engine heat pump device), for example, an absorption heat pump device for air conditioning such as cooling and heating. The invention relates to a device for driving an engine.

[0002]

2. Description of the Related Art Such an engine heat pump device 1
00, for example, as shown in FIG. 11, using the engine 1 as a power source, a heat source for cooling, for example, a heat source for cooling, or a heat source for heating, for example, a heat source for heating is obtained. A configuration of a heat pump type air conditioner (hereinafter, referred to as a first conventional technique) connected to give a heat source from the heat source device 10 to an indoor unit 80 for air conditioning arranged in a room to perform a cooling operation or a heating operation is well known. is there.

However, the engine type heat pump device according to the present invention also includes an absorption type heat pump device adapted to perform only the above heating operation.

In FIG. 11, the circuit portion indicated by the bold line is
A heat-operated fluid for obtaining a heat source, for example, a conduit of a refrigerant, a circuit portion indicated by a thin line is an electric path for an electrical detection signal / control signal, and the heat source device 10 is generally
Since it is placed outdoors, it is also called an outdoor unit, but it may be placed indoors. Also, in general, one heat source unit 10
Is configured to supply a heat source to a plurality of indoor units.

Then, the engine 1 drives a compressor of the compression section 2, for example, a rotary type compressor, to pressurize a heat-operated fluid for obtaining a heat source, for example, a refrigerant such as Freon R22 or Freon R137 to compress the compressor. It is supplied to the heat operation part 3 through an oil separator (not shown) for separating the oil mixed and operated with the heat operation fluid therein.

The heat operating section 3 performs a required heat operation necessary for a cooling operation or a heating operation by the heat operating fluid, and the heat operating fluid whose pressure is reduced after the heat operation is passed through an accumulator (not shown). It is given to the compression unit 2 again.

The heat manipulating section 3 sends the pressurized heat manipulating fluid to a heat radiating heat exchanger X (condenser) (not shown) to radiate heat and condense it, and then heat the heat manipulating fluid to absorb heat. It is a part for circulating the heat-operated fluid so that the heat-operated fluid is sent to a vessel Y (evaporator) (not shown) to absorb the heat to be vaporized and then recovered.

The conduit switching unit 4 causes the indoor unit 80 to perform a cooling operation,
That is, when cooling is performed, the heat exchanger 81 on the indoor unit 80 side is connected to operate as the heat absorbing heat exchanger Y, and the heat exchanger 5 on the heat source device 10 side is radiated as described above. When each pipe is connected so as to operate as the heat exchanger X for heating, and when the indoor unit 80 is heated, that is, heated, the heat exchanger 5 on the side of the heat source device 10 absorbs heat. This is a part that is connected so as to operate as the exchanger Y, and also connects each heat pipe 81 so that the heat exchanger 81 on the indoor unit 80 side operates as the heat dissipation heat exchanger X. For example, switching of a four-way valve or the like. It is a pipeline switching mechanism that electrically operates the valve.

The heat exchanger 5 is a meandering pipe through which a heat-operated fluid is provided with a large number of fins and is provided with a blower 5B for blowing the outside air to radiate or absorb the outside air. Since it exchanges heat with the outdoor air, it is generally called an outdoor heat exchanger.

The heat exchanger 81 has a structure similar to that of the heat exchanger 5, and provides a recirculation of room air by a blower mechanism to absorb heat from the room air during a cooling operation, that is, during cooling, to heat the room air. It is a heat exchanger that radiates heat to indoor air during operation, and because it exchanges heat with indoor air, it is generally
It is called an indoor heat exchanger.

On the side of the heat source device 10, the detected values of the temperature and pressure of each part of the heat-operated fluid on the side of the heat source device 10 and the set values set by the setting operation part 6 are given to the control part 7, The temperature of the object on the machine 80 side, for example, the temperature of the room air, and the set value of the set temperature that is the control target of the cooling operation or the heating operation set in the control section 82 from the setting operation section 83 are sent to the control section 7. The control processing function of the control unit 7 uses these respective values to give a control signal for operating the compression unit 2 from the control unit 7 to the engine 1 for operation control.

Further, a setting signal for applying a specific condition to this control is given from the setting operation section 6 to the control section 7 to perform a required limited operation. Further, on the side of the outdoor unit 80, the control unit 82 controls the operation of a blower (not shown) that recirculates the indoor air, or the room based on the set temperature that is the target of the cooling operation or the heating operation from the operation unit. A flow control valve (not shown) of the heat-operated fluid passing through the heat exchanger 81 is controlled.

In the engine type heat pump device 100 as described above, as shown in FIG. 12, the heat exchanger 5A is provided between the outdoor heat exchanger 5 and the blower 5B, and this heat exchanger is provided only during the heating operation. 5A, cooling part 1D of engine 1
By circulating the cooling water that has been cooled and heated, a part of the heat generated by the engine 1 itself is given to the heat-operated fluid that passes through the heat exchanger 5, and the coefficient of performance of the entire device during the heating operation is observed. Temperature detector D1 for detecting the temperature of the outside air, a pressure detector D2 for detecting the pressure of the discharge port of the compression section 2, and a temperature detector for detecting the temperature of the heat-operated fluid passing through the outdoor heat exchanger 5. By controlling the rotation speed of the blower 5B based on each detected value obtained from D3 and the like,
The structure (hereinafter, referred to as the second conventional technology) configured to appropriately control the heating operation of the outdoor heat exchanger 5 is specially developed.
-327767.

[0014]

In the second prior art described above, a part of the heat generated by the engine itself can be used as a heat source for heating, so that it is particularly effective in cold regions. However, in such a cold region, the outside air temperature is often 0 ° C. or less even during the day, so that the heating of the outdoor heat exchanger due to the outside air temperature cannot be used, and the heating capacity is deteriorated. .

In order to compensate for such a decrease in heating capacity and obtain a sufficient heating capacity, it is necessary to increase the shaft output of the engine, that is, the engine output in order to increase the compression output of the compression section 2. Therefore, the engine becomes large, and the device cannot be provided in a compact size.

[0016] Therefore, there is a problem that it is desired to provide a small-sized engine type heat pump device which is suitable for cold districts and which solves such inconvenience.

[0017]

SUMMARY OF THE INVENTION The present invention relates to an engine type heat pump device which obtains a heat source for heating with a required heat-operated fluid using the engine as a drive source as described above,

Exhaust heat exchanging means for exchanging exhaust heat of the engine with the heat-operated fluid,

A first structure is provided, which comprises exhaust heat increasing means for increasing the amount of exhaust heat by controlling the excess air ratio of the fuel-air mixture gas supplied to the engine to be higher than the steady air excess ratio. ,

In place of the exhaust heat increasing means in the above-mentioned first structure, an exhaust heat increasing means for increasing the heat quantity of the exhaust heat by controlling the ignition timing of the engine to be delayed from the steady ignition timing is provided. A second configuration,

Instead of the exhaust heat increasing means in the above-mentioned first structure, control for increasing the excess air ratio of the fuel-air mixture supplied to the engine above the steady excess air ratio, and ignition of the engine. By providing the engine heat pump device according to the third configuration, which is provided with the exhaust heat increasing means for increasing the heat quantity of the exhaust heat by the control combined with the control for delaying the timing from the steady ignition timing. It is designed to solve the problem.

The "exhaust heat" in the present invention means, as will be described later with reference to FIG. 5, heat generated by heating engine cooling water and heat contained in engine exhaust. It is a general term for heat including.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION As an embodiment of the present invention, an embodiment in which the present invention is applied to the engine type heat pump device 100 shown in FIG. 10 will be described.

[0024]

EXAMPLES Examples will be described below with reference to FIGS. 1 to 10, the parts indicated by the same reference numerals as those in FIGS. 11 and 12 have the same functions as the parts indicated by the same reference numerals in FIGS. 11 and 12. 1 to 10 are designated by the same reference numerals.
This is a part having the same function as the part having the same reference numeral explained in any of 0.

[Outline of "Exhaust Heat" Utilization] In the configuration of the engine-type heat pump device 100 as shown in FIG. 1, when the energy amount of the fuel given to the engine 1 is 100%, the distribution of the energy amount to each part is For example, in FIG.
As described above, the shaft output of the engine 1, that is, the amount of energy mainly given to the compression unit 2 is about 30%, and the amount of energy that is naturally radiated to the outside from the periphery of the engine 1 or is lost as exhaust loss is about 10%. %, The “exhaust heat” in which the remaining about 60% is recovered, that is, the amount of energy given to the cooling water for cooling the engine 1 with respect to the amount of heat and the amount of heat obtained by some heat exchange with the exhaust gas from the engine 1. The total amount is 60%.

In the present invention, 60% of the energy amount of the "exhaust heat" is recovered and the heat amount of the "exhaust heat" itself is increased to increase the heating capacity when the outside air temperature is lowered. It was done like this.

In addition to the above, if the heat pump functional portion 100A has an energy amount α%, for example, 20%, for obtaining the heat amount of the outside air from the outdoor heat exchanger 5, the heat pump functional portion 100A has a heating capacity. ,
30% of shaft output and α% of outside air heat gain, that is, 2
The sum of 0% and 60% of the "waste heat" recovered, for example,
That's 110%.

However, when the outside air temperature becomes, for example, 0 ° C. or lower, α% of the outside air heat gain is 0%.
Since the value becomes% or a negative value, the heating capacity decreases, and it is necessary to compensate for this decrease or more.

Then, as a result of trying various experiments in the same engine, as a method of increasing "exhaust heat",
A method of increasing the excess air ratio of a mixed gas of fuel and air (hereinafter referred to as a mixed gas) supplied to the engine as shown in FIG. 6 and a method of delaying the ignition timing of the engine as shown in FIG. 7 are effective. The experimental result was obtained.

6 and 7 are, for example, a 4-cycle F2 type (4 cylinder type) 22 in which the fuel is LP gas.
The engine of 00 cc was obtained in an operating state in which the engine was operated at a rotational speed of 1600 rpm and a shaft output of 14.4 PS (French horsepower). FIG. 6 shows changes in the amount of recovered heat when the excess air ratio λ was changed, Further, FIG. 7 shows changes in the amount of recovered heat when the ignition timing is changed.

Therefore, under the above operating conditions,
The amount of heat recovered in FIGS. 6 and 7 is obtained as “exhaust heat” per four cycles of the engine 1. The amount of heat recovered is the sum of the amount of heat measured by collecting the exhaust gas from the engine and the amount of heat measured by collecting the engine cooling water, and averaged by the amount of rotation with four cycles of the engine during that period. Was sought by
It does not include the efficiency of the heat exchanger to recover the "waste heat".

Here, in the case of a 4-cycle gasoline engine, the excess air ratio λ is obtained by calculating a mixing ratio M = Ga / Gf from the fuel weight per time Gf and the air weight Ga.
It is well known that when the theoretical mixing ratio Mth is set to Mth = 14.8 to 15, λ = M / Mth.

As shown in FIG. 6, the steady-state excess air ratio λ is set to about 1.3, and the lean maximum output air-fuel mixture, that is, the maximum excess air ratio λ is set to about 1.6. , The amount of recovered heat increases as the excess air ratio λ increases. Therefore, it can be considered that the heat quantity of “exhaust heat” is also increasing.

Further, the ignition timing is the time when the piston is most inserted into the cylinder, that is, when the crank interlocking with the piston reaches the so-called upper dead center TDC, the rotation angle of the crankshaft is 0 °. , BTDC (Before TD)
C) 20 ° ", that is, the steady ignition timing is reached at a position of -20 °. From this steady ignition timing, the crankshaft rotation angle of 0 ° is exceeded, and 5 is more than that.
“ATDC (After TDC) 5 °” after “°”, that is, when the time until the ignition timing is changed to the position of + 5 ° is changed, the recovered heat amount is sequentially increased as the ignition timing is delayed. Therefore, it can be considered that the heat quantity of the “exhaust heat” is likewise sequentially increasing.

[First Embodiment] First, a first embodiment will be described with reference to FIGS. 1 to 3 and 8. In the first embodiment, as the "exhaust heat" 1A of the engine 1, heat obtained by the cooling water a for cooling the engine 1 itself and heat obtained by the exhaust from the engine 1 can be recovered, for example, , A configuration in which cooling water a for cooling the cylinder of the engine 1 and cooling water b flowing through a heat exchanger (not shown) provided in the exhaust passage of the engine 1 are circulated to the heat exchanger 5A, and supplied to the engine 1. The amount of heat of the above "exhaust heat" is variably adjusted by controlling the mixing ratio adjusting unit 1B for adjusting the mixing ratio M of the mixed gas by the control unit 7 to change the excess air ratio λ. It is an embodiment configured as described above.

The mixing ratio adjusting section 1B is adapted to adjust, for example, a cam position adjusting mechanism for changing the reciprocating distance of the fuel pump or a lever adjusting mechanism for changing the choke angle of the air supply passage. .

The control unit 7 is a control unit for performing control processing by a microcomputer, and is constituted by using a commercially available CPU board (CPU / B) 70 as shown in FIG. 2, for example. Each detection signal obtained by detecting the state and each operation signal input by operating the setting operation unit 6 are fetched as input data from the input / output port 71 and stored in the working memory 73, and the input data The control memory 72 is configured to output from the input / output port 71 each control signal for controlling each unit obtained by performing the required control processing based on the program of the processing flow stored in the processing memory 72 and the control data. When necessary, the clock circuit 74 measures the time required for control processing, and the operating state, control state, and setting state of each unit are displayed on the display unit 75. Are those that you have configured so that.

Then, in the processing memory 72, the "first processing flow" program as shown in FIG. 3 and the outside air temperature data on the horizontal axis in FIG. 8 for controlling with the control characteristic as shown in FIG. The amount of heat of "exhaust heat" based on the detection signal of the outside air temperature detected by the temperature detector D1 by the "first control data" stored as a table in which the data of the excess air ratio λ on the vertical axis are associated with each other. Is variably adjusted.

In FIG. 8, the stationary excess air ratio is 1.3,
It shows the control data to increase the "exhaust heat" by increasing the excess air ratio as the outside air temperature decreases to 0 ° or less, and normally, the decrease of the outside air temperature is about -20 ° C. Since it can be considered up to the outside temperature
The control characteristic is set so that the maximum excess air ratio λ = 1.6 at 20 ° C., and the value of the excess air ratio λ for each predetermined temperature change, for example, every 1 ° C. change, The “first control data” tabulated corresponding to the value of the outside air temperature is stored in the processing memory 72.

When used in an area where the outside air temperature drops even lower, the control characteristics are set as shown by the chain double-dashed line in FIG.
"Control data of" may be stored in the processing memory 72.

[Description of Processing Flow] The processing flow of FIG. 3 will be described below.

This processing flow is configured as a subroutine attached to the main processing flow for controlling the entire operation of the heat source device 10, and shifts to this processing flow at predetermined time intervals, for example, every 5 seconds. It was designed to do.

In step SP1, the outside air temperature data, that is, the current temperature data detected by the temperature detector D1 and the previous temperature data are fetched, and the next step S1.
Move to P2.

In step SP2, it is determined whether or not the current temperature data and the previous temperature data have changed by a predetermined "temperature change value", for example, 1 ° C or more. If it has changed to the predetermined "temperature change value" or more, the process proceeds to the next step SP3, and if not, the process returns to the main processing flow.

In step SP3, the current temperature data is below a predetermined "temperature value" required to change the excess air ratio λ to a value different from the steady excess air ratio, that is, in the case of FIG. Determines whether the temperature is “0 ° C.” or lower. When the temperature is "0 ° C" or less, the process proceeds to the next step SP4, and when not, step S
Move to P6.

In step SP4, the value of the excess air ratio λ corresponding to the current temperature data, for example, from the table of the "first control data" stored in the processing memory 72,
If the temperature data this time is “-10 ° C.” data, the value of 1.45 of the excess air ratio λ is set as “corresponding data”.
Read out as s and stored in the working memory, the process proceeds to the next step SP5.

◆ In step SP5, "corresponding data",
That is, the control signal for controlling the mixing ratio adjusting unit 1B is output so as to correspond to the excess air ratio λ = 1.45, and after the mixing ratio is adjusted to the corresponding state, the process returns to the main processing routine.

In step SP6, the data of the steady excess air ratio λ from the table of the "first control data" stored in the processing memory 72, that is, the excess air ratio λ = 1.
After reading the value of 3 and storing it in the working memory, the process proceeds to the next step SP7.

In step SP7, the steady excess air ratio, that is, the excess air ratio λ = 1.
After the control signal for controlling the mixture ratio adjusting unit 1B is output and the mixture ratio is adjusted to the corresponding state, the process returns to the main processing routine.

[Summary of Configuration of First Embodiment] To summarize the configuration of the above-described first embodiment, in the engine heat pump apparatus 100 that uses the engine 1 as a drive source to obtain a heat source for heating by a required heat-operated fluid. ,

The "exhaust heat" of the engine 1 is
Exhaust heat exchange means for giving heat to the heat exchanger 5A and exchanging heat with the above-mentioned heat-operated fluid,

By controlling the excess air ratio λ of the fuel-air mixed gas supplied to the engine 1, that is, the mixed gas, for example, by controlling the mixing ratio adjusting unit 1B by the control unit 7, a steady excess air ratio, for example, , Excess air ratio λ = 1.3
The first configuration is provided with the exhaust heat increasing means for increasing the heat amount of the above “exhaust heat” by increasing the heat amount.

[Second Embodiment] Next, a second embodiment will be described with reference to FIGS. 1 to 3 and 9. In the second embodiment, the control unit 7 controls the ignition timing adjustment unit 1C of the engine 1 instead of the configuration of increasing the "exhaust heat" of the engine 1 by controlling the mixing ratio adjustment unit 1B in the first embodiment. In this embodiment, the amount of "exhaust heat" is increased by providing a configuration for delaying the ignition timing.

The ignition timing adjusting section 1C is, for example, a position 30 ° before the upper dead center TDC, that is, "BTDC3.
The first pulse generator that obtains the "reference pulse" at the position of "0 °" and one "advancing pulse" for every 1 ° of the rotation angle of the crankshaft (not shown) of the engine 1 are obtained. A second pulse generator and a pulse counter that generates an ignition pulse at the time when the "advance pulse" is counted by a "predetermined number" from the "reference pulse" are provided, and the pulse counter counts " By varying the "predetermined number", the time point of the ignition pulse given to the spark plug is changed to adjust the ignition timing of the engine 1.

The processing flow stored in the processing memory 72 of the control unit 7 is for controlling the steps SP3 to SP7 in the "first processing flow" of FIG. 3 with the control characteristics as shown in FIG. Further, the "second control data" stored in a table in which the data of the outside air temperature on the horizontal axis of FIG. 9 and the data of the ignition timing on the vertical axis are stored in the table to detect the outside air temperature detected by the temperature detector D1. The ignition timing is adjusted based on the signal, and the amount of "exhaust heat" is variably adjusted.

FIG. 9 shows the steady ignition timing at the upper dead center TDC.
It shows the control data for increasing the "exhaust heat" by delaying the ignition timing as the outside air temperature decreases to 0 ° or lower, that is, at -10 °, that is, "BTDC 10 °". Normally, it can be considered that the decrease of the outside air temperature is up to about −20 ° C. Therefore, when the outside air temperature is −20 ° C., the maximum ignition timing delay is + 5 °, that is, “ATDC 5 °”. The "second control data", which is set in the characteristic and tabulated in correspondence with the value of the outside air temperature, for each predetermined temperature change, for example, for each 1 ° C change, is stored in the processing memory 72 as a table. I remember.

When used in an area where the outside air temperature drops further, the control characteristic is set as shown by the chain double-dashed line in FIG.
"Control data of" may be stored in the processing memory 72.

Therefore, the steps SP3 to SP7 in the process flow of FIG. 3 operate as follows.

In step SP3, the temperature data this time is below a predetermined "temperature value" required to change the ignition timing to a value different from the steady ignition timing, that is, in FIG.
In the case of, it is determined whether or not the temperature is “0 ° C.” or less. When the temperature is equal to or lower than "0 ° C", the process proceeds to the next step SP4, and otherwise, the process proceeds to step SP6.

At step SP4, the value of the ignition timing corresponding to the temperature data of this time, for example, the temperature data of this time is "-10 °" from the table of the "second control data" stored in the processing memory 72. If the data is “C”, the value of the ignition timing of −2.5 ° is read as “corresponding data” and stored in the working memory, and then the next step S
Move to P5.

◆ In step SP5, "corresponding data",
That is, the control signal for controlling the ignition timing adjusting unit 1C is output so that the ignition timing corresponds to -2.5 °, and after the ignition timing is adjusted to the corresponding state, the process returns to the main processing routine.

In step SP6, the data of the steady ignition timing, that is, the value of the ignition timing of -10 ° is read out from the table of the "second control data" stored in the processing memory 72 and stored in the working memory. After that, the process proceeds to the next step SP7.

◆ In step SP7, the steady ignition timing,
That is, the control signal for controlling the ignition timing adjusting unit 1C is output so that the ignition timing corresponds to −10 °, and after adjusting the ignition timing to the corresponding state, the process returns to the main processing routine.

[Summary of Configuration of Second Embodiment] To summarize the configuration of the second embodiment, instead of the exhaust heat increasing means in the first configuration,

The ignition timing of the engine 1 is set to, for example,
By controlling the ignition timing adjusting unit 1C by the control unit 7, the exhaust heat increasing means for increasing the heat quantity of the exhaust heat by delaying the steady ignition timing, for example, a value of −10 ° is provided. This is what constitutes the configuration of.

In this second structure, since the ignition timing is changed, the energy amount 30% of the shaft output in FIG. 5 is slightly changed. Although the amount of output energy 30% is slightly reduced and the amount of energy given to the heat pump functional part is reduced, the amount of "exhaust heat" increased by changing the ignition timing is as shown in FIG. Since it becomes extremely large, the substantial heating capacity can be sufficiently increased.

[Third Embodiment] Next, referring to FIGS.
A third embodiment will be described with reference to FIG. In this third embodiment,
Control for increasing the "exhaust heat" of the engine 1 by controlling the mixture ratio adjusting unit 1B in the first embodiment and "exhaust heat" for the engine 1 by controlling the ignition timing adjusting unit 1C in the second embodiment.
This is an embodiment in which a combined control is provided so that the control for increasing the amount of heat is performed in parallel.

That is, the processing memory 72 stores the above-mentioned "first control data" and "second control data", and at the same time, steps SP3 to SP7 in the "first processing flow" of FIG. 8 is configured so that the control with the control characteristic shown in FIG. 8 and the control with the control characteristic shown in FIG. 9 are performed in parallel.

Therefore, in the case where the control characteristic of FIG. 8 and the control characteristic of FIG. 9 are performed in parallel as they are, the engine 1 is not as compared with the first embodiment or the second embodiment.
The amount of “exhaust heat” can be further increased, and when the control characteristics of FIG. 8 and the control characteristics of FIG. Even if the control of the portion 1B and the control of the ignition timing adjusting portion 1C are controlled in small amounts, the same "exhaust heat" of the engine 1 as in the first or second embodiment is obtained. Can be configured into.

[Fourth Embodiment] Next, referring to FIG. 1, FIG. 2, FIG.
A fourth embodiment will be described with reference to FIGS. The fourth embodiment controls the mixture ratio adjusting unit 1B in the first embodiment to increase "exhaust heat" of the engine 1 and the ignition timing adjusting unit 1C in the second embodiment to control the engine 1 This is an embodiment in which the control unit 7 performs the control processing as shown in FIG. 10 in which the control for increasing the heat amount of “exhaust heat” is selected and performed according to the degree of decrease in the outside air temperature.

That is, the processing memory 72 stores the "third control data" for performing the control shown in FIG. 10 and the "first processing flow" shown in FIG. 4, and the temperature detector D1. On the basis of the temperature data of the temperature detection signal detected in step 1, the engine is operated by increasing the excess air ratio λ in the "first low temperature range" where the outside air temperature is relatively low, for example, in the range of 0 ° C to -20 ° C. The “exhaust heat” of the engine 1 is increased by increasing the amount of “exhaust heat” of No. 1 and delaying the ignition timing in the “second low temperature range” where the outside air temperature is extremely low, for example, a low range exceeding −20 ° C. It is configured to perform control to increase the amount of heat.

In FIG. 10, the thick solid line indicates the excess air ratio λ.
And the thick dotted line shows the control characteristic of the ignition timing. The steady excess air ratio λ is 1.3, and the outside air temperature is in the “first low temperature range”, that is, 0 ° C to −. 20 ° C
In the range, the control is performed so as to increase the “exhaust heat” of the engine 1 by increasing the excess air ratio λ, the steady ignition timing is set to −10 °, and the outside air temperature is the “second low temperature range”. That is, in a low range over −20 ° C., control is performed so as to increase “exhaust heat” of the engine 1 by changing the ignition timing, and a predetermined temperature change of the outside air temperature, for example, The value of the excess air ratio λ and the value of the ignition timing for each 1 ° C change are stored in the processing memory 72 as “third control data” tabulated in association with the value of the outside air temperature.

[Description of Processing Flow] The processing flow of FIG. 4 will be described below.

Similar to the processing flow of FIG. 3, this processing flow is configured as a subroutine attached to the main processing flow for controlling the overall operation of the heat source device 10, and is set at a predetermined time interval, for example, 5 It is designed to shift to this processing flow every second.

In steps SP1 and SP2,
Step SP1 to step S in the processing flow of FIG.
Since the same processing as P2 is performed, the description thereof is omitted here.

In step SP3, the temperature data of this time becomes a value within the "first low temperature range", that is, a value within the range of "0 ° C to -20 ° C" in the case of FIG. Is determined. If the value is in the "first low temperature range", the process proceeds to the next step SP4, and if not, the process proceeds to step SP6.

In step SP4, from the table of the "third control data" stored in the processing memory 72, the value of the excess air ratio λ and the value of the ignition timing corresponding to the temperature data of this time, for example, this time. When the temperature data is “−10 ° C.” data, the value of the excess air ratio λ of 1.45 and the value of the ignition timing of −10 ° are “first correspondence data”.
Read out as s and stored in the working memory, the process proceeds to the next step SP5.

In step SP5, "first corresponding data", that is, excess air ratio λ = 1.45 and ignition timing =
After the control signal for controlling the mixture ratio adjusting unit 1B and the ignition timing adjusting unit 1C is output so as to correspond to −10 ° and the mixture ratio and the ignition timing are adjusted to the corresponding states, the main processing is performed. Return to routine.

In step SP6, the temperature data this time becomes a value within the "second low temperature range", that is, a value within the "low range exceeding -20 ° C" in the case of FIG. Is determined. If the value is in the "second low temperature range", the process proceeds to the next step SP7, and if not, the process proceeds to step SP9.

In step SP7, from the table of the "third control data" stored in the processing memory 72, the value of the excess air ratio λ and the value of the ignition timing corresponding to the temperature data of this time, for example, this time. When the temperature data is “−30 ° C.”, the excess air ratio λ is 1.6, and
After reading the value of -2.5 ° of the ignition timing as "second corresponding data" and storing it in the working memory, the process proceeds to the next step SP8.

In step SP8, "second corresponding data", that is, excess air ratio λ = 1.6 and ignition timing =-
A control signal for controlling the mixture ratio adjusting unit 1B and the ignition timing adjusting unit 1C is output so as to correspond to 2, 5 °, and after the mixture ratio and the ignition timing have been adjusted to correspond to each other, the main Return to the processing routine.

In step SP9, the data of the steady excess air ratio λ, that is, the excess air ratio λ = 1.
3 and steady ignition timing, that is, ignition timing = −10
After reading the value of 0 ° and storing it in the working memory, the process proceeds to the next step SP10.

In step SP10, the mixing ratio adjusting unit 1B and the ignition timing adjustment are performed so as to correspond to the steady excess air ratio, that is, the excess air ratio λ = 1.3 and the steady ignition timing = −10 °. After outputting a control signal for controlling the section 1C and adjusting the mixture ratio and the ignition timing to correspond to each other,
Return to the main processing routine.

[Summary of Configurations of Third and Fourth Embodiments]
To summarize the configurations of the third and fourth embodiments described above,
Instead of the exhaust heat increasing means in the above-mentioned first configuration,

The excess air ratio of the fuel-air mixed gas supplied to the engine 1 is controlled by, for example, controlling the mixing ratio adjusting unit 1B by the control unit 7 to obtain a steady air excess ratio,
For example, a control for increasing the excess air ratio λ = 1.3 and an ignition timing of the engine 1 described above, for example, by controlling the ignition timing adjusting unit 1C by the control unit 7, can provide a steady ignition timing, for example, A third configuration is provided in which exhaust heat increasing means for increasing the amount of exhaust heat is provided by control combined with control for delaying ignition timing = −10 ° or more.

[Modified Implementation] The present invention includes the following modified implementations.

(1) As shown in [Modified Configuration] of FIG. 1, the engine 1 itself is cooled to add the "exhaust heat" of the engine 1 to the heat-operated fluid passing through the heat exchanger 5. The first exhaust heat recovery component that transfers the heated cooling water to the heat exchanger 5A by giving it to the heat exchanger 5A via the cooling exhaust heat conduit 1A2, and the exhaust gas of the engine 1 itself exhaust gas exhaust heat conduit 1A1
Second through which exhaust heat is transferred to the heat-operated fluid passing through the heat exchanger 5 by being discharged so as to be sprayed to the heat exchanger 5 through
And the exhaust heat recovery component.

(2) The first exhaust heat recovery portion in the above configuration (1) is removed, and the exhaust heat recovery is performed only by the second exhaust heat recovery portion.

[0089]

According to the present invention, even when the temperature of the outside air drops and the heat source for heating cannot be recovered from the outdoor heat exchanger, "exhaust heat" of the engine is given to the outdoor heat exchanger. The exhaust heat of the engine is controlled by increasing the excess air ratio of the mixed gas supplied to the engine and by delaying the ignition timing of the engine. Therefore, it is possible to obtain a sufficient heating capacity regardless of the decrease in the outside air temperature, and it is possible to provide an engine type heat pump device for cold regions with an improved coefficient of performance as a whole.

[Brief description of the drawings]

In the drawings, FIGS. 1 to 10 show an embodiment of the present invention, and FIGS. 11 and 12 show a prior art. The contents of each drawing are as follows.

FIG. 1 is an overall block configuration diagram.

FIG. 2 is a block diagram of a main part

[Fig. 3] Flow chart of main part control processing

FIG. 4 is a flow chart of a main part control process.

[Figure 5] Overall energy distribution map

FIG. 6 is a characteristic diagram of a main part operation experiment.

[Fig. 7] Main part operation test characteristic diagram

FIG. 8 is a control characteristic diagram of main parts.

FIG. 9 is a control characteristic diagram of main parts.

FIG. 10 is a control characteristic diagram of main parts.

FIG. 11 is an overall block configuration diagram.

FIG. 12 is an overall block configuration diagram.

[Explanation of symbols]

 1 Engine 1A Exhaust Heat 1A1 Exhaust Exhaust Heat Pipeline 1A2 Cooling Exhaust Heat Pipeline 1B Mixing Ratio Adjusting Section 1C Ignition Timing Adjusting Section 1D Cooling Section 2 Compressing Section 3 Heat Operating Section 4 Pipeline Switching Section 5 Heat Exchanger 5A Heat Exchanger 5B Blower 6 Setting Operation Section 7 Control Section 10 Heat Source Machine 70 CPU / B 71 Input / Output Port 72 Processing Memory 73 Working Memory 74 Clock Circuit 75 Display Section 80 Indoor Unit 81 Heat Exchanger 82 Control Section 83 Setting Operation Section 100 Engine Heat Pump Device 100A Heat pump function part D1 temperature detector D2 pressure detector D3 temperature detector

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Hiroki Hamada 2-5-5 Keihan Hondori, Moriguchi City, Osaka Prefecture Sanyo Electric Co., Ltd. (72) Inventor Yoshio Masuda 2-5 Keihan Hondori, Moriguchi City, Osaka No. 5 Sanyo Electric Co., Ltd. (72) Inventor Yoshikazu Yoshida 2-5-5 Keihan Hondori, Moriguchi City, Osaka Prefecture Sanyo Electric Co., Ltd. (72) Inventor Koji Fujitani 2 Keihan Hondori, Moriguchi City, Osaka Prefecture 5-5, Sanyo Electric Co., Ltd.

Claims (3)

[Claims] 1. An engine-type heat pump device for obtaining a heat source for heating by a required heat-operated fluid using an engine as a drive source, wherein exhaust heat of the engine is exchanged with the heat-operated fluid. And an exhaust heat increasing means for increasing the heat quantity of the exhaust heat by controlling to increase the excess air ratio of the fuel-air mixture gas supplied to the engine above the steady excess air ratio. Heat pump device. 2. An engine heat pump device for obtaining a heat source for heating by a required heat operation fluid using an engine as a drive source, wherein exhaust heat exchange means for exchanging exhaust heat of the engine with the heat operation fluid. And an exhaust heat increasing means for increasing the heat quantity of the exhaust heat by controlling the ignition timing of the engine to lag behind the steady ignition timing. 3. An engine heat pump device for obtaining a heat source for heating with a required heat operation fluid by using an engine as a drive source, and exhaust heat exchange means for exchanging exhaust heat of the engine with the heat operation fluid. And a control in which the control for increasing the excess air ratio of the fuel-air mixture gas supplied to the engine above the steady excess air ratio and the control for delaying the ignition timing of the engine behind the steady ignition timing are combined. An engine heat pump device, comprising: an exhaust heat increasing means for increasing the amount of exhaust heat.