JPH10170096A - Initial warming controller for engine driven heat pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate rising lag on the initial stage of starting the warming operation. SOLUTION: When a start detecting means 120 detects starting of warming operation of an engine driven heat pump, an initial setting means 130 sets a higher degree of overheat as compared with the case of normal control and an initial control means 160 controls operation of cooling cycle according to the degree of overheat. When a temperature decision means 140 decides that the difference between a room temperature detected by a room temperature detection means 100 and a target room temperature set by a temperature setting means 110 comes within a predetermined range, and a duration decision means 150 decides than the decision results of the temperature decision means 140 continued for a predetermined time, a normal control transition means 170 performs control for returning the degree of overheat back to a normal level. Consequently, temperature of refrigerant to be delivered from a compressor can be raised and the heat discharge quantity of the first heat-exchanger can be ensured.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heating control device for an engine-driven heat pump device which drives a compressor by an engine and switches the direction of a refrigerant flow in a cooling cycle during cooling and heating.

[0002]

2. Description of the Related Art A refrigeration cycle control apparatus disclosed in Japanese Patent Application Laid-Open No. Hei 5-223358 is one having a refrigeration cycle using an electronic expansion valve. This device is
A compressor, a condenser, an electronic expansion valve, and a refrigeration cycle configured by sequentially connecting evaporators by piping, near the outlet of the evaporator, detects the pressure and temperature of the gas refrigerant ejected from the expansion valve. A pressure sensor and a temperature sensor for detecting the degree of superheat are disposed, and further, a flow rate sensor 12 for detecting a cooling load is disposed near the inlet of the expansion valve.
When the refrigerant load is large, the amount of refrigerant in the evaporator is reduced, and the amount of refrigerant in the condenser is increased to increase the degree of supercooling.When the refrigerant load is small, the degree of subcooling is reduced. Is to do so. That is, while the superheat degree is maintained in the evaporator by the control means, the superheat degree is adjusted, and the flow rate of the refrigerant circulating in the refrigeration cycle is adjusted. Therefore, the degree of supercooling in the condenser is adjusted by the change in the flow rate of the refrigerant, and the degree of supercooling increases as the cooling load increases.

However, this reference is intended only for cooling operation, and operates so as to obtain the degree of superheating and the degree of supercooling according to the detected cooling load.
Specifically, at high load, the amount of refrigerant is reduced by reducing the expansion valve opening to increase the degree of superheat, and at low load, the amount of refrigerant is increased by increasing the degree of opening of the expansion valve to reduce the degree of superheat. That is more. This control is intended to detect the degree of superheat and maintain the degree of superheat, but does not change the degree of superheat in order to eliminate the problem at the time of startup.

Further, as a device having a heater for heating the refrigeration cycle, there is a refrigeration cycle device disclosed in Japanese Patent Application Laid-Open No. 5-113252. This device sequentially connects a compressor, a condenser, a thermal expansion valve, and an evaporator, and a refrigerant suction line from the evaporator to the compressor is branched into a main line and a bypass line. Is provided with a refrigerant overheating heater and a temperature sensing cylinder for a temperature-type expansion valve, and is capable of lowering the discharge temperature even when the condenser load becomes excessive. In other words, when the discharge temperature of the compressor rises above a certain level under conditions where the condensation temperature becomes high, such as when the load on the condenser becomes excessive, the bypass line is heated by the heater. Accordingly, the temperature-sensitive expansion valve for a thermal expansion valve provided in the bypass line determines that the superheat is large.Therefore, the thermal expansion valve operates in a direction in which the superheat decreases, and reduces the discharge temperature of the compressor. It can be reduced.

However, the heater of this reference is not for heating the refrigerant itself but for changing the detection condition of the temperature-sensitive expansion tube for a temperature type expansion valve in order to secure the heat radiation of the condenser in the cooling cycle. It is considered to be mounted on the bypass passage so as to reduce the influence on the refrigeration cycle as much as possible.

Further, an air conditioner disclosed in Japanese Patent Application Laid-Open No. 7-198220 is provided with a refrigerant compressor, a condenser, a first pressure reducing means, a heat exchanger, and a space between the refrigerant compressor and the condenser. A first control valve, a first bypass flow path bypassing the condenser and the first pressure reducing means and connecting an inlet side of the first control valve and an outlet side of the first pressure reducing means; First
A second pressure reducing means disposed on a bypass flow path of
A second control valve for opening and closing the bypass flow path, a second bypass flow path connecting the inlet side of the first control valve and the inlet side of the first pressure reducing means, and provided on the second bypass flow path Refrigerant state detecting means, a third bypass flow path connecting an outlet side of the refrigerant state detecting means and an outlet side of the heat exchanger, and a third control valve for opening and closing the third bypass flow path. It is.

In this configuration, during heating, the control means closes the first control valve and sets the second control valve at the time of heating.
Is opened to configure a heating cycle including the compressor, the second pressure reducing means, and the heat exchanger. At the time of this heating, if the pressure in the heating cycle becomes higher than a predetermined pressure when the refrigerant is excessive, the pressure state detecting means provided in the second bypass flow path is opened, and the refrigerant in the heating cycle is discharged. The refrigerant is caused to flow into the flow path between the first control valve and the first pressure reducing means, thereby reducing the amount of refrigerant. When the amount of charged refrigerant is insufficient, the first control valve is closed, the second control valve and the third control valve are opened, and the refrigerant stored in the condenser is supplied to the hot gas refrigerant circuit. As a result, the amount of refrigerant in the hot gas refrigerant circuit can be maintained at an appropriate amount. At this time, it is disclosed in the embodiment that the excess or deficiency of the refrigerant amount is detected based on the magnitude of the superheat.

[0008]

In contrast to the above cited references, an engine-driven heat pump apparatus according to the present invention comprises an engine, a compressor connected to the engine via a clutch, and a first engine disposed indoors. A heat exchanger, a second heat exchanger disposed outdoors, an expansion valve disposed between the first heat exchanger and the second heat exchanger, and the second heat exchanger. A cooling cycle comprising a double-pipe heat exchanger for exchanging heat with the cooling water of the engine, and a four-way valve for switching the direction of refrigerant flow in the cooling cycle. The refrigerant flow is changed by switching the four-way valve, and the first heat exchanger is used as an evaporator during the cooling operation, and the first heat exchanger is used as a condenser during the heating operation to cool or heat the room. Is shall. In particular, in the case of the heating operation, the refrigerant is heated by using the engine cooling water as a heat source in the double-pipe heat exchanger, the superheat (degree of superheat) on the compressor suction side is increased, and the heat release amount by the first heat exchanger is reduced. It is intended to be improved.

Normally, the above device adjusts the opening degree of the expansion valve so that the degree of superheat on the compressor discharge side becomes appropriate during normal operation. Since the heating capacity of the heat exchanger is low, the heating start-up property is slow, and the liquid is in a liquid-back state, which adversely affects the durability of the compressor.

[0010] Therefore, an object of the present invention is to provide a heating start control device for an engine-driven heat pump device, which eliminates the delay of the heating start-up property in the initial stage of the heating operation.

[0011]

SUMMARY OF THE INVENTION Accordingly, the present invention provides a compressor connected to an engine via connection means,
A first heat exchanger disposed indoors and a second heat exchanger disposed outdoor
A heat exchanger, an expansion valve arranged between the first heat exchanger and the second heat exchanger, and an engine arranged between the second heat exchanger and the compressor. A cooling cycle comprising a third heat exchanger that exchanges heat with the cooling water, and a switching means for switching the direction of the refrigerant flow of the cooling cycle. The superheat degree of the cooling cycle is set to a predetermined value higher than that during the normal control (claim 1).

Therefore, according to the present invention, at the beginning of heating, the degree of heating in the cooling cycle can be made higher by a predetermined value than during normal control, so that the temperature of the refrigerant discharged from the compressor can be increased. Since the amount of heat dissipated in the first heat exchanger can be secured, the above object can be achieved.

Also, as shown in FIG. 1, the present invention provides a compressor connected to an engine via connecting means,
A first heat exchanger disposed indoors and a second heat exchanger disposed outdoor
A heat exchanger, an expansion valve arranged between the first heat exchanger and the second heat exchanger, and an engine arranged between the second heat exchanger and the compressor. Detecting a room temperature in an engine-driven heat pump apparatus including a cooling cycle including a third heat exchanger that exchanges heat with the cooling water of the first embodiment and switching means for switching a direction of a refrigerant flow in the cooling cycle. Room temperature detecting means 100 to be
Temperature setting means 110 for setting the target indoor temperature, start detection means 120 for detecting the start of the heating operation, and when the start of the heating operation is detected by the start detection means 120, the degree of superheating of the cooling cycle is usually determined. Initial setting means 130 for increasing the control temperature by a predetermined value, and temperature determining means 14 for comparing the room temperature with the target temperature to determine
0 and a duration determining means 150 for determining whether or not the determination result by the temperature determining means 140 has continued for a predetermined time.
And an initial control means 160 for controlling based on the degree of superheat set by the initial setting means 130, and a temperature difference between the room temperature and the target temperature determined by the temperature determination means 140 to be within a predetermined range; and When the continuation time determination means 150 determines that the determination result has passed a predetermined time, there is provided a normal control transition means 170 for returning the degree of superheat to the value at the time of the normal control (claim 3).

Therefore, in the present invention, when the start detecting means 120 detects the start of the heating operation of the engine-driven heat pump apparatus, the initial setting means 1
30 sets a degree of superheat greater than that during normal control, and the initial control means 160 controls the operation of the cooling cycle according to this degree of heating. During this control, the temperature determining means 140 determines that the temperature difference between the indoor temperature from the indoor temperature detecting means 100 and the target indoor temperature by the temperature setting means 110 is within a predetermined range, and the temperature determining means 150 determines this temperature difference. The above object can be achieved by performing control to return the degree of superheat to a normal value by the normal control shifting means 170 when it is determined that the determination result by the means 140 has continued for a predetermined time.

In the present invention, the degree of superheat is preferably the degree of superheat on the discharge side of the compressor.

[0016]

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

An engine-driven heat pump device 1 shown in FIG. 2 is an engine 8 driven by gasoline or the like as fuel.
And a compressor 2 connected to the engine 1 via an electromagnetic clutch 12, a four-way valve 7 connected to a discharge side and a suction side pipe of the compressor 2, and a pipe extending to one of the four-way valves 7. The first connected and arranged in the room 13
A heat exchanger 3 and a second heat exchanger 5 disposed outdoors;
An electronic expansion valve 4 arranged on a pipe connecting the first heat exchanger 3 and the second heat exchanger 5, and an electronic expansion valve 4 arranged between the second heat exchanger 5 and the four-way valve 7. And a double tube heat exchanger 6 to which the cooling water of the engine 8 is supplied. In addition, 11 is a blower for indoor units, and 12 is a blower for outdoor units.

Further, in order to control the engine-driven heat pump apparatus 1, the following sensors are provided as detecting means. Detecting the temperature T ₁ and pressure P _H of the refrigerant temperature detecting sensor 20 and the high-pressure sensor 19 is disposed on the discharge side pipe of the compressor 2 is discharged, provided on the suction side pipe of the compressor 2 temperature The detection sensor 27 and the low pressure sensor 18 detect the temperature T of the drawn refrigerant.
₂ and pressure P _L are detected. Further, a temperature sensor 21 disposed on the first heat exchanger 3 detects a temperature T ₂ of the refrigerant passing through the first heat exchanger 3, and the temperature sensors 22 and 23
Detects the refrigerant temperatures T ₃ and T ₄ before and after the electronic expansion valve 4. Further, the temperature sensor 24 detects the temperature T ₅ of the refrigerant passing through the second heat exchanger 5, and the temperature sensor 25 flows between the double-tube heat exchanger 6 and the second heat exchanger 5. The temperature T ₆ of the refrigerant is detected. The temperature sensor 28 disposed in chamber 13 detects the room temperature T _R, the rotational speed sensor 2
9 detects an engine speed R, and further detects a temperature sensor 26.
Detects the engine cooling water temperature T _W.

Each signal detected by the detection means is supplied to a multiplexer (MPX) 14 and an A / D converter 1
5, the control unit 17 receives a set temperature T _S set by the operation panel 16 and other set signals. After being processed according to a predetermined program, the control signal C is input to the control unit 17. ₁ -C speed control system for the control devices (engine 8 as _6, the four-way valve 7, the indoor blower 11, the electronic expansion valve 4, the outdoor blower 10, the engine cooling water solenoid valve 9,
And the electromagnetic clutch 12). The control unit 17 includes a central processing unit (C) (not shown).
PU), a read-only memory (ROM), a random access memory (RAM), an input / output port (I / O), an output circuit, and the like.

In the engine-driven heat pump apparatus 1 having the above configuration, when the heating operation is set, the four-way valve 7
Are switched to connect the discharge side of the compressor 2 to the first heat exchanger 3 side and the suction side of the compressor 2 to the second heat exchanger 5 side. As a result, the refrigerant flows in the direction indicated by the solid arrow in FIG. The state of the refrigerant in this heating cycle is shown, for example, by a Mollier diagram shown in FIG.

[0021] First, the low pressure low temperature (temperature T _7, the pressure P _H) sucked by the compressor 2 becomes refrigerant is compressed high-temperature high-pressure (temperature t _1, the pressure P _H). When the refrigerant passes through the first heat exchanger 3, it radiates heat to the indoor air to heat the indoor. At this time, the refrigerant condenses and its enthalpy decreases, and the temperature of the refrigerant decreases from t ₁ to t ₃ . Then, adiabatic expansion as it passes through the electronic expansion valve 4, the pressure of the refrigerant in the P _L from P _H, the temperature is lowered from t ₃ to t _4. Second
When passing through the heat exchanger 5, the refrigerant absorbs the heat of the passing air and evaporates, and its enthalpy rises. The temperature of the coolant rises from the time t ₄ to t _5. The refrigerant is further heated further in the double-pipe heat exchanger 6, the temperature of the refrigerant regressing up from t ₅ to t ₆ to the compressor 2. The broken line in FIG.
_{1 to} t ₆ are shown, and the relationship between the temperatures is expressed as t ₁ > t
_{2> t 3> t 6>} t 5> t is _4.

In this heating cycle, the degree of superheat SH on the discharge side of the compressor is determined from the detected value T ₁ (t ₁ ) of the temperature sensor 20 and the detected value T ₂ (t ₂ ) of the temperature sensor 21. (SH = T
₁ -T _2). Supercooling SC (Super Cool)
Is represented by t ₂ -t ₃ .

When the cooling operation is set, the four-way valve 7 is switched so that the discharge side of the compressor 2 goes to the second heat exchanger 5 and the suction side of the compressor 2 goes to the first heat exchanger 3. Connected. As a result, the refrigerant is
Flows in the direction indicated by the dashed arrow. The state of the refrigerant in this cooling cycle is shown, for example, by a Mollier diagram shown in FIG.

First, the low-pressure low-temperature (temperature T ₁₁ , pressure P _H ) refrigerant sucked by the compressor 2 is compressed to a high-temperature high pressure (temperature t _7, pressure P _H ). This refrigerant passes through the double-tube heat exchanger 6 with the solenoid valve 9 closed, reaches the second heat exchanger 5, and radiates heat and condenses when passing through the second heat exchanger 5. At this time, the lower the enthalpy of the refrigerant, the temperature of the refrigerant falls to t _9. Then, adiabatic expansion as it passes through the electronic expansion valve 4, the pressure of the refrigerant in the P _L from P _H, the temperature is lowered from t ₉ to t _10. When passing through the first heat exchanger 3, the refrigerant absorbs the heat of the air in the room 13 and evaporates, increasing its enthalpy. Temperature of the refrigerant rises from the time t ₁₀ to t _11, to return to the compressor 2. Incidentally, those shown by the broken line in FIG. 4, t ₇ ~
indicates an isothermal line of t _11, the relationship of each temperature, t _7> t _8>
t ₉ > t ₁₁ > t ₁₀ .

As described above, in the engine-driven heat pump device 1, the shortage of heat during heating in the normal heat pump system can be supplemented with the engine cooling water during normal heating in addition to normal cooling operation. The heating operation can be performed efficiently. In the embodiment shown in FIG. 2, one compressor 2 is driven by the engine 8 for convenience of description, but it is desirable that one engine 8 drives a plurality of compressors.

As an example of the control of the engine-driven heat pump apparatus 1 having the above-described configuration, flowcharts are shown in FIGS. 5 to 7. The control of the engine-driven heat pump apparatus 1 will be described with reference to the following flowcharts. The heating start control according to the invention will be described.

In FIG. 5, control of the engine-driven heat pump apparatus 1 is started from step 200 by turning on an air-conditioning on / off switch from the operation panel 16, and in step 210, the engine is driven by a setting switch on the operation panel 16. It is determined whether the air conditioning setting of the heat pump apparatus 1 is a cooling operation. In this determination, if the air conditioning setting is the cooling operation, the process proceeds to step 220, where the cooling setting is performed.
Specifically, the four-way valve 7 is switched so that the refrigerant flows in the direction of the dashed line B in FIG. When it is determined in step 210 that the operation is not the cooling operation (in the case of the heating operation), the process proceeds to step 230 to perform the heating setting. Specifically, the four-way valve 7
Is switched so that the refrigerant flows in the direction of the solid line A in FIG.

Then, the routine proceeds to step 240, where the minimum rotational speed R _min is set as the set rotational speed R _S of the engine 8. Then, the engine 8 is started the routine proceeds to step 250, wherein said detected by the rotation number detection sensor and the actual engine speed R _a set rotation speed to the R _S are equal, control of step 250 by the determination step 260 if but held increases the value of the engine rotational speed Ra, and the actual engine speed R _a and the setting rotational speed R _S is equal, the process proceeds to step 270, clutch 12 is turned on, the compressor 2 is Starts operation. In this embodiment, the minimum rotational speed R
_min is 1100 rpm.

Then, in the determination at step 280,
If it is determined that the heating operation has been set, the process proceeds to step 300, where the following start control is executed. If it is determined that the cooling operation has been set, the process proceeds to step 290, where the compressor 2 on the discharge side superheat respective initial value alpha ₁ to the lower limit value alpha and the upper limit value beta of SH, beta ₁ is set, the timer T _d, an initial value 0 is set to T _e, is normally controlled to below the step 500 Be executed. In this embodiment, the initial value α ₁ is 20 ° C., and the initial value β ₁ is 25 ° C.

The start control starting from step 300 is executed at the beginning of the heating operation. In this embodiment, it is set to always start when the heating control is turned on, but the engine cooling water temperature Tw is set.
May be started only when is less than or equal to a predetermined value.

As shown in FIG. 6, the starting control includes:
First, at step 310, to set the heating time of the initial lower limit value alpha ₂ to the lower limit value alpha superheat SH, the upper limit of the degree of superheating SH beta
Is set to the initial heating upper limit β ₂ , and the timers T _a , T _b ,
Set an initial value 0 to _Tc . In this embodiment, the initial heating lower limit α ₂ is set to 20 ° C., and the initial heating upper limit β ₂ is set to 30 ° C. This value is set to be higher than the normal set value during heating. In this embodiment, the value during normal control is such that the initial heating lower limit α ₂ is set in the same manner as 20 ° C., but the initial heating upper limit β ₂ is 25 ° C. Is also set low.

In step 320, the engine 8 sets the set engine speed R _S and the detected actual engine speed R _S
The rotational speed is controlled so that the deviation from a becomes zero, and the opening of the electronic expansion valve 4 is adjusted so that the superheat degree SH on the compressor discharge side is within a range larger than α and smaller than β. Specifically, when the degree of superheat SH is smaller than the above range, the amount of refrigerant flowing through the electronic expansion valve 4 is reduced to increase the degree of superheat SH. Is larger, the electronic expansion valve 4 is opened to increase the amount of refrigerant, thereby lowering the degree of superheat SH.

Then, in step 330, a temperature deviation ΔT between the room temperature T _R and the set temperature T _S which changes under the control of step 320 is calculated.

[0034]

## EQU1 ## ΔT = T _R −T _S

This temperature deviation ΔT is calculated in steps 340 and 3
At 50, it is determined whether the value is equal to or less than a predetermined value, is equal to or more than a predetermined value, and is within a predetermined range. Specifically, in step 340, it is determined whether or not the temperature deviation ΔT is larger than a predetermined value (+ γ1). If so, step 35
Go to 0. In this step 350, it is determined whether or not the temperature deviation ΔT is smaller than a predetermined value (−γ2). If there is, the process proceeds to the normal control transition control in step 460 and subsequent steps.
In this embodiment, γ1 and γ2 are set to 1 ° C.

[0036] In the temperature lowering control, firstly, the first timer T _a is counted in step 360, the second and third timer T _b, T _C is reset. Then, in step 370, it is determined whether or not the first timer Ta has elapsed _a predetermined time θ1, and if the predetermined time θ1 has elapsed, the process proceeds to step 380, and the value of the set rotation speed R _S is reduced by a predetermined value R _r. Similarly the superheat lower limit alpha and superheat upper limit beta likewise predetermined value alpha _S, lowering beta _S, lowering the heating capability of the air conditioner, thereby controlling the direction of lowering the room temperature T _R. When the first timer T _a is not the predetermined time θ1 elapsed in step 370, and return to step 320, in which the current control is continued. In this embodiment, θ1 is 3 minutes, the predetermined value R _r is 200 rpm, α _S and β _S are 5 ° C.

Then, in step 390, it is determined whether or not the set rotational speed R _S is equal to or less than the minimum rotational speed R _min . If it is determined in this determination that the set rotation speed R _S is not less than or equal to the minimum rotation speed R _min , the process returns to step 320 and control is performed in accordance with the set value in step 380, and the set rotation speed R _S is determined. If it is determined that the rotation speed is equal to or lower than the minimum rotation speed R _min , the process proceeds to step 40.
At 0, the set rotational speed R _S and the lower limit values α and β of the superheat degree SH are set to the minimum set values R _min , α _min and β _min , and the routine returns to step 320. In this embodiment, R _min is 1100 rpm, α _min is 20 ° C., β
_min is 30 ° C.

In the temperature rise control, first, at step 410, the second timer _Tb is counted.
The first and third timers T _a and T _C are reset. Then, in step 420, the second timer T _b is performed is determined whether a predetermined time θ2 elapsed, the routine proceeds to step 430 when the predetermined time θ2 elapsed, the set rotational speed value predetermined value structured R _S raised R _r, likewise the superheat lower limit alpha and superheat upper limit beta likewise predetermined value alpha _S, increased beta _S, increasing the heating capacity of the air conditioner, thereby controlling the direction to raise the room temperature T _R is there. Further, in the case where the second timer T _b is not the predetermined time θ2 lapse step 420, and return to step 320, in which the current control is continued. In this embodiment, θ2 is 3 minutes, the predetermined value R _r is 200 rpm, α _S and β _S are 5 ° C.
And

Then, in step 440, it is determined whether or not the set rotational speed R _S is equal to or more than the maximum rotational speed R _max . If it is determined in this determination that the set rotation speed R _S is not equal to or greater than the maximum rotation speed R _max , the process returns to step 320 and control is performed according to the set value in step 430, and the set rotation speed R _S is If it is determined that the rotation speed is equal to or more than the maximum rotation speed _Rmax , the process proceeds to step 45.
At 0, the set rotational speed R _S and the lower limit values α and β of the superheat degree SH are set to the minimum set values R _max , α _max and β _max , and the _routine returns to step 320. In this embodiment, R _max is 1900 rpm, α _min is 40 ° C., β
_min is 50 ° C.

In the normal control transition control, first, in step 460, the third timer _Tc is counted, and the first and second timers _Ta and _Tb are reset. Then, in step 470, the third timer T
_It is determined whether or not _c has elapsed a predetermined time θ3. If the predetermined time θ3 has elapsed, the routine proceeds to step 480, where the superheat degree lower limit α and the superheat degree upper limit β are set to predetermined values α in order to perform normal control values. _S0 , β _{SO are} lowered, and the routine shifts to normal control from step 500. Step 470
If the third timer _Tc has not passed the predetermined time θ3 in step, the routine returns to step 320 and the current control is continued. In this embodiment,
The predetermined value θ3 is 6 minutes, the predetermined value α _s0 is set to 0 so as not to change, and the predetermined value β _S0 is 5 ° C. Accordingly, the superheat degree SH is set to a value of a so-called normal control in which only the upper limit value of the superheat degree SH is reduced, and the process shifts to the normal control starting from step 500.

Thus, in this start control,
If the temperature difference ΔT has passed a predetermined time or less than a predetermined value, but to increase the predetermined value the value of the set rotational speed R _S and the degree of superheat SH, 1 ° C. also specifically set temperature T _S is than the room temperature T _R
If the following condition continues for 3 minutes, the set rotation speed R _S is increased by 200 rpm and the value of the superheat degree SH is increased by 5 ° C. Also, if the temperature deviation ΔT has passed a predetermined time or greater than a predetermined value, but the value of the set rotational speed R _S and the degree of superheat SH Ru predetermined Drops, also specifically set temperature T _S is than the room temperature T _R 1 When the temperature of not less than 0 ° C. continues for 3 minutes, the set rotational speed R _S is decreased by 200 rpm and the value of the superheat degree SH is decreased by 5 ° C.

As a result of the above control, if the temperature deviation ΔT enters a stable control in which the temperature deviation ΔT stays within a predetermined range for a predetermined time, the control exits the starting control and shifts to a normal control. It returns to the normal value. Specifically, when the temperature deviation ΔT is continuously stopped within the range of -1 ° C to + 1 ° C for 6 minutes, the upper limit of the superheat degree SH is reduced by 5 ° C and the control is shifted to the normal control.

The normal control starting from step 500 is similar to step 320 in step 510.
Setting the rotational speed R _S and the actual engine speed R _a is the engine 8 so as to match a controlled, also within the superheat degree SH is given (α <SH <β) and electronic solenoid valve 4 is controlled so that Is done. Further, the temperature deviation ΔT is calculated in the same manner as in step 330.

In step 530, the temperature deviation ΔT is determined to be larger or smaller than a predetermined value (+ γ3). If the temperature deviation ΔT is larger, the process proceeds to the temperature lowering control in step 550 and below. This step 540
Then, the magnitude of the temperature deviation ΔT and the predetermined value (−γ4) is determined. If the temperature deviation ΔT is small, the process proceeds to the temperature increase control in step 600 and below. If the temperature deviation is large (the temperature deviation ΔT is within the predetermined range). Returns to step 510.

In the temperature lowering control starting from step 550, first, at step 550, the fourth timer _Td is counted, and the fifth timer _Te is reset. Then, in step 560, it is determined whether or not the fourth timer _Td has passed a predetermined time θ4 (3 minutes). If not, the flow returns to step 510 to maintain the current control, If the time has elapsed, the process proceeds to step 570. Then, in step 570, the set rotation speed R
_S is lowered by a predetermined value Rr (200 rpm), and the superheat SH
The lower limit value α and the upper limit value β are set to predetermined values α _S (5 ° C.), β
_S (5 ° C) lower. Then, proceed to step 580,
The calculated set rotation speed R _S is compared with the minimum rotation speed R _min . If the set rotation speed R _S is equal to or less than the minimum rotation speed R _min , the process proceeds to step 590 to set the set rotation speed R _S and the degree of superheat. The lower limit α and the upper limit β of SH are set to the minimum value [R _min (11
00 rpm), α _min (20 ° C), β _min (25 ° C)]
And the process returns to step 510. If the set rotation speed R _S is not equal to or less than the minimum rotation speed R _min , the process proceeds to step 510 with the numerical value set in step 570.
Is to return to.

[0046] In this way, the room temperature T _R and the set temperature T
_When the temperature deviation ΔT of _S is larger than a predetermined value (+ γ3: + 1 ° C.), the set rotation speed R _S is lowered, the superheat degree SH is lowered, the air conditioning capacity is lowered, and the indoor temperature is lowered. is there.

In the temperature rise control starting from step 600, first, at step 600, the fifth timer T _e
Is counted, and the fourth timer _Td is reset.
Then, in step 610, the fifth timer T
_It is determined whether _e has passed a predetermined time θ5 (3 minutes),
If not, the process returns to step 510 to maintain the current control.
Go to 0. Then, in step 620, the set rotational speed R _S is increased by a predetermined value Rr (200 rpm), and the lower limit α and the upper limit β of the superheat degree SH are set to predetermined values α _S (5 ° C.), β
Raise _S (5 ° C).

Then, in step 630, it is determined whether or not the cooling operation is being performed. If it is determined that the cooling operation is being performed, the process proceeds to step 640 where the calculated set rotation speed R _S and the cooling maximum rotation speed are calculated. R _mc is compared, and if the set rotation speed R _S is equal to or greater than the cooling maximum rotation speed R _mc , the process proceeds to step 650 to set the set rotation speed R _S , the lower limit α and the upper limit β of the superheat degree SH to the cooling condition. Time maximum value [R _mc (1700 rp
m), α _mc (35 ° C.), β _mc (40 ° C.)], and return to step 510. If the set rotation speed R _S is not equal to or greater than the cooling maximum rotation speed R _mc , the process returns to step 510 with the value set in step 620.

If it is determined in step 630 that the heating operation is being performed, the process proceeds to step 660, where the calculated set rotation speed R _S and the heating maximum rotation speed R R are calculated.
_max is compared, and the set rotation speed R _S becomes the maximum rotation speed R during heating.
If it is not less than _max , the routine proceeds to step 670, where the set rotation speed R _S and the lower limit value α and the upper limit value β of the superheat degree SH are set to the heating maximum value [R _max (1900 rpm), α _max (40
° C), β _max (45 ° C)], and returns to step 510. In addition, the set rotation speed R _S is the maximum rotation speed R _mc during cooling.
If not, the process returns to step 510 with the value set in step 620.

[0050] In this way, the room temperature T _R and the set temperature T
_If the temperature deviation ΔT of _S is smaller than a predetermined value (+ γ4: −1 ° C.), the set rotation speed R _S is increased by one step, and the superheat degree SH is increased by one step to increase the air conditioning capacity, and It raises the temperature.

The numerical values such as the above-mentioned predetermined values are values set optimally by experiments. Further, during the cooling operation, when the discharge temperature of the compressor exceeds 70 ° C,
The control may be shifted from the SH control to the discharge temperature control of the compressor. However, in the present invention, the manner of the cooling control is not particularly limited. Further, in this embodiment, the range of the superheat degree during the normal control may be set to be different between the heating operation and the cooling operation, and may be different from the superheat degree during the start control. Alternatively, the range of the degree of superheat during normal operation may be set to a range that does not overlap. Specifically, in this embodiment, the range of the superheat degree corresponding to the minimum set number of revolutions at the time of the start control is 20 ° C. to 30 ° C., and 20 ° C. to 25 ° C. at the time of the normal control. The temperature may be 25 ° C. to 30 ° C. during control, and 20 ° C. to 25 ° C. during normal control.

[0052]

As described above, according to the present invention, the set engine speed and the superheat degree SH on the discharge side of the compressor are both changed by the temperature deviation between the room temperature and the set temperature. By doing so, the air conditioning capacity of the engine-driven heat pump device can be improved, and the room temperature can quickly reach the set temperature. Furthermore, if the temperature of the engine cooling water is not sufficiently increased at the beginning of heating, the refrigerant in the double-pipe heat exchanger cannot be sufficiently overheated. Since the heat radiation amount of the heat exchanger can be secured, the air-conditioning capacity at the time of starting heating can be improved.

[Brief description of the drawings]

FIG. 1 is a functional block diagram showing a configuration of a heating start control device of an engine-driven heat pump device according to the present invention.

FIG. 2 is an explanatory diagram showing a configuration of an engine-driven heat pump device according to the embodiment of the present invention.

FIG. 3 is a Mollier diagram during a heating operation.

FIG. 4 is a Mollier diagram during a cooling operation.

FIG. 5 is a flowchart of the air conditioning control according to the embodiment of the present invention.

FIG. 6 is a flowchart of a start control according to the embodiment of the present invention.

FIG. 7 is a flowchart of normal control according to the embodiment of the present invention.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 engine driven heat pump device 2 compressor 3 first heat exchanger 4 electronic expansion valve 5 second heat exchanger 6 double tube heat exchanger 7 four way valve 8 engine 12 electromagnetic clutch

Claims (3)

[Claims] A first heat exchanger disposed indoors, a second heat exchanger disposed outdoors, and the first heat exchange. An expansion valve disposed between the heat exchanger and the second heat exchanger;
A cooling cycle including a third heat exchanger disposed between the heat exchanger and the compressor and exchanging heat with the cooling water of the engine; and a switch for switching a direction of a refrigerant flow in the cooling cycle. A heating initial control device for an engine-driven heat pump device, wherein the degree of superheat of the cooling cycle is set to a predetermined value higher than that during normal control at the beginning of heating. 2. A compressor connected to the engine via a connecting means, a first heat exchanger disposed indoors, a second heat exchanger disposed outdoor, and the first heat exchange. An expansion valve disposed between the heat exchanger and the second heat exchanger;
A cooling cycle including a third heat exchanger disposed between the heat exchanger and the compressor and exchanging heat with the cooling water of the engine; and a switch for switching a direction of a refrigerant flow in the cooling cycle. An engine-driven heat pump device comprising: means for detecting an indoor temperature; a temperature setting means for setting a target indoor temperature; a start detecting means for detecting a start of a heating operation; and the start detecting means. Initialization means for increasing the degree of superheat of the cooling cycle by a predetermined value larger than the value at the time of normal control when the start of the heating operation is detected by the: a temperature determined by comparing the room temperature with the target temperature Determining means; duration determining means for determining whether or not the determination result by the temperature determining means has continued for a predetermined time; and, based on the degree of superheat set by the initial setting means. The temperature difference between the room temperature and the target temperature is determined to be within a predetermined range, and the duration determination means determines that the predetermined time has elapsed. A normal control transition unit for returning the degree of superheat to a value at the time of the normal control in a case where the heating is started. 3. The heating initial operation control device for an engine-driven heat pump device according to claim 1, wherein the superheat degree is a superheat degree on a discharge side of a compressor.