DE102006022557A1 - Ejektorpumpenkreisvorrichtung - Google Patents

Abstract

In an ejector cycle device having an ejector (17), an evaporator (18) is disposed in a refrigerant branch passage connected to a refrigerant suction port (17b) of the ejector, an opening / closing member (16, 17e) for opening and closing a refrigerant passage is arranged to flow of the refrigerant in the evaporator, and a control unit (25) controls an operation of the compressor intermittently. In the ejector cycle device, the control unit brings the opening / closing element into a closed state in a period for which the operation of the compressor is stopped. Accordingly, it can limit collection of the liquid refrigerant in the evaporator while the compressor is turned off.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The The present invention relates to an ejector cycle device with an ejector, which has a function of reducing pressure a refrigerant and has a function of circulating a refrigerant.

2. Description of others designs

These Type of ejector cycle device is, for example, the JP-B1-3322263 known. JP-B1-3322263 discloses an ejector cycle device, a first evaporator and a second evaporator having. The second evaporator is refrigerant downstream from an ejector with functions for reducing a pressure of a refrigerant and for circulating a refrigerant arranged, a vapor / liquid separator is refrigerant downstream arranged this second evaporator, and the first evaporator is between a liquid refrigerant outlet the vapor / liquid separator and a refrigerant suction port of Ejector pump set.

According to this The ejector cycle device becomes that of the first evaporator spent vapor phase refrigerant sucked by a pressure drop, by a high-speed stream of the refrigerant is caused when the refrigerant is extended, and the speed of the refrigerant when the refrigerant is expanded through a diffuser section (pressure increasing section) converted into pressure energy to the pressure of the refrigerant (suction pressure) too increase. Therefore, it is possible to reduce the driving force of a compressor and thus the Efficiency of a cooling circuit to improve.

Besides that is it is possible a heat absorption (Cool-) Process in separate rooms both the first and the second evaporator or in the to perform the same room by means of the two evaporators. In an ejector cycle device having an evaporator (above first evaporation apparatus), which only at the refrigerant suction of the Ejector is arranged, is a mechanical or electrical control valve upstream of the ejector or upstream of the evaporator.

Opening the The control valve arranged upstream of the ejector is thus regulated. that the degree of superheating at the outlet of the evaporator or the high pressure of the refrigerant in the cooling circuit is controlled. The opening the control valve arranged upstream of the evaporator is regulated, thereby the degree of superheating of the refrigerant to control at the outlet of the evaporator.

The The control valve described in JP-B1-3322263 controls the degree of superheat at the outlet of the evaporator or the high pressure of the refrigerant at the time of ejector cycle operation, but opens and includes not a refrigerant channel in operative connection with the intermittent operation of the compressor. For this reason, even if the compressor is switched off, held the control valve in a state of a specific opening. Accordingly developed itself, when the compressor is turned off, a phenomenon that the high pressure and the low pressure of the circuit brought into a uniform state are, i. a pressure balance. In the process of developing this pressure balance causes that through the nozzle section the ejector pump flowing refrigerant Flow noise. If the compressor is off, the compressor does not cause any Operating noise to to create a peaceful environment, and therefore, those created by the nozzle section caused flow noise to the ear relevant.

In addition, if the compressor is switched off and then restarted, liquid refrigerant returned to the compressor and compressed by the compressor. In this case, the life becomes of the compressor deteriorates.

If for example, an internal temperature of a room to be cooled to an extreme low temperature, for example, near -20 ° C like on a vehicle mounted refrigerator, is reduced, the low pressure of the cooling circuit to a low Reduced pressure according to this extremely low temperature near -20 ° C become. Therefore, the pressure difference between the high pressure and the Low pressure of the cooling circuit when the compressor is switched off, very big.

Therefore, in the process of developing a pressure balance when the compressor is turned off, a large amount of the liquid refrigerant flows from the high pressure side through the nozzle portion of the ejector to the low pressure side. Here, the inside temperature is already lowered to the extremely low temperature, and the heat load of the evaporator becomes small, and the refrigerant is not sucked to the suction side of the compressor. Therefore, the refrigerant flowing to the low pressure side collects as liquid phases refrigerant in the vapor / liquid separator and the evaporator downstream of the ejector. As a result, when the compressor is next started, the liquid refrigerant may leak from the vapor-liquid separator and may flow back to the compressor.

Further beats JP-A-2005-308380 (corresponding to US 2005/0178150 A1 and the US 2005/0268644 A1) an ejector cycle device before, with a branch passage from a branch point of a refrigerant passage branches off upstream of an ejector and with the refrigerant suction of the Ejector pump is connected; a throttle mechanism and a first Evaporator, which are arranged in the branch channel; and one second evaporator, the refrigerant downstream the ejector is arranged. According to this ejector cycle device the first evaporator is connected in parallel to the ejector pump, and the branch channel has the throttle mechanism exclusively for the first one Evaporator. In this case, the refrigerant quantities of the first and the second evaporator are easily controlled. In which Process of developing the pressure balance when the compressor is turned off, but caused by the nozzle section the ejector and the throttle mechanism of the branch channel flowing refrigerant Flow noise.

Further when an internal temperature of a room to be cooled to an extreme low temperature close to -20 ° C, for example, like one on a vehicle mounted refrigerator decreases, the heat load of the evaporator small when the compressor is turned off. Therefore, the process of developing a pressure balance develops a phenomenon that the refrigerant into the first and the second evaporator flows and there collects. In this case, the refrigerant flow causes flow noise when the refrigerant further into that in the first and second evaporators liquid Refrigerant flows. Further becomes the liquid Refrigerant that collects in the first and second evaporators, while the compressor is switched off, sucked in by the compressor, and the liquid refrigerant is returned to the compressor when the compressor the next Time is started.

In addition, As shown in JP-A-5-312421, an ejector cycle device known from a refrigerant channel for connecting a compressor, a radiator, an ejector and a first evaporator and a branch duct, of the Refrigerant passage branches off and a throttle device and a second evaporator contains built up.

In the ejector cycle apparatus described in JP-A-5-312421 However, frost is liable to adhere to three portions of the second evaporator, which is of a comparatively low evaporation temperature, an upstream section of the first evaporator, which is on the air upstream side is arranged, because the first evaporator of a comparatively high Evaporation temperature, and a storage (vapor / liquid separator), the refrigerant flow down of the first evaporator is arranged on. When the frost is reflected in the three sections, the cooling capacity of the ejector cycle significantly deteriorated.

SUMMARY OF THE INVENTION

In In view of the above problems, it is an object of the present invention The invention is to provide an ejector cycle device that prevents refrigerant flow noise can when a compressor is turned off.

It Another object of the present invention is an ejector cycle device to provide for the introduction of liquid refrigerant in an evaporator stands while a compressor is switched off at the next operating time of the compressor in the compressor can prevent.

It It is still another object of the present invention to provide an ejector cycle device effectively provide frost on a low pressure side component, For example, on evaporators and a memory, remove can.

According to one aspect of the present invention, an ejector cycle device includes a compressor that draws and compresses a refrigerant, a radiator that radiates heat of a high-pressure refrigerant discharged from the compressor; an ejector pump disposed downstream of the radiator to decompress and expand the refrigerant from the radiator; an evaporator disposed in a refrigerant branch passage connected to a refrigerant suction port of the ejector; an opening / closing member that opens and closes a refrigerant flow and can prevent a flow of refrigerant into the evaporator; and a control unit that brings the opening / closing member into a closed state in a period in which the operation of the compressor is stopped. Accordingly, while the operation of the compressor is stopped, the opening / closing member prevents refrigerant flow into the evaporator. That's why it can be a liquid collection Prevent refrigerant in the evaporator while the compressor is turned off, and prevent return of liquid refrigerant from the evaporator to the compressor when the compressor is started next time. As a result, when the operation of the compressor is stopped, refrigerant flow noise can be restricted.

To the Example is the one connected to the refrigerant suction port Evaporator arranged as a first evaporator, and a second evaporator may be located downstream of the ejector be. In this case, you can the first evaporator and the second evaporator for cooling a to be cooled Room can be arranged, or they can be cooled separately for cooling Rooms arranged be.

In addition, can a temperature detecting element for detecting a temperature in Reference to a temperature of a to be cooled by the evaporator Room can be arranged, and the control unit can operate of the compressor based on the temperature sensing element control detected temperature intermittently. The refrigerant branch channel can branch at a branch point upstream of the ejector and can be connected to the refrigerant suction port be. Further, the opening / closing member may be an opening / closing valve, which is located upstream of the branching point, or on the branch point arranged three-way valve or an upstream of the evaporator in the refrigerant branch channel arranged opening / closing valve or a channel opening / closing mechanism arranged in the ejector pump itself be.

The Control unit can be the opening / closing element in the period in which the compressor is switched off, from closing state to an open state control and then restart the operation of the compressor. Further The control unit may be the opening / closing element before switching off the compressor from an open state to a closed state Control and can the compressor for a certain time, in which the opening / closing element is closed, continuously in an operating condition and then turn off the compressor.

In addition, can the opening / closing element an upstream of the evaporator connected to the refrigerant suction port is, arranged opening / closing valve and a channel opening / closing mechanism disposed in the ejector pump itself contain. In this case, the control unit controls the opening / closing valve in the period, for which the compressor is off, from a closed state to an open state, thereby the pressure in a cooling circuit to bring into balance, and then brings the channel opening / closing mechanism in an open state back and then restart the operation of the compressor.

In The ejector cycle device may have a throttling mechanism upstream of the opening / closing element be arranged to increase the pressure of the refrigerant upstream of the opening / closing element in such a way to reduce the refrigerant in two phases of a vapor and a liquid is brought. Next you can the ejector and the opening / closing valve be combined with each other at least as an integrated unit.

According to one Another aspect of the present invention includes an ejector cycle device a compressor that is a refrigerant sucks and compresses; a cooler, the heat the high-pressure refrigerant discharged from the compressor radiates; a Ejector pump, which has a nozzle section for reducing a pressure of the refrigerant downstream of the radiator to the refrigerant expand, and the refrigerant by a jet stream of the refrigerant from the nozzle section sucks; a first evaporator, which in a refrigerant suction of the Ejector pump to be sucked refrigerant evaporates, so a cooling capacity to have; a second evaporator, that from the ejector flowing refrigerant evaporates, so a cooling capacity to have; a tire removal member comprising the first and the second Evaporator heats to perform a Reifentfernungsbetrieb, at the frost adhering to the first and second evaporators Will get removed; an evaporator temperature detecting element that a temperature of at least one of the first evaporator and the second evaporator detected; and a control unit that the Tear removal element controls to the first and the second evaporator to heat and perform the Reifentfernungsbetrieb when the by the evaporator temperature sensing element detected temperature reaches a predetermined temperature. Accordingly, the Reifentfernungsbetrieb the first and second evaporator carried out in a suitable manner be while a deterioration of the cooling capacity the first and the second evaporator can be prevented.

For example, the evaporator temperature detecting element may be arranged to detect the temperature of the first evaporator. In this case, the control unit controls the Reifentfernungselement to perform the Reifentfernungsbetrieb when the by the evaporator temperature sensing element he reached temperature of the first evaporator reaches a predetermined temperature. Alternatively, the evaporator temperature detecting element may be arranged to detect the temperature of the second evaporator. In this case, the control unit controls the frost removal member to perform the frost removal operation when the temperature of the second evaporator detected by the evaporator temperature detection element reaches a predetermined temperature.

alternative a storage tank can drain the refrigerant of the second evaporator, and a storage temperature detecting element may be disposed be arranged so that it detects a temperature of the memory. Further, the evaporator temperature sensing element with a first evaporator temperature sensor, which detects a temperature of the first evaporator, and a second evaporator temperature sensor, arranged for detecting the temperature of the second evaporator is to be provided. In this case, the control unit controls the Reifentfernungselement to perform the Reifentfernungsbetrieb when a Temperature caused by any component of the storage temperature sensing element and the first and second evaporator temperature sensors is detected, reaches a predetermined temperature or more.

The Control unit can the Reifentfernungsbetrieb of the first and the second evaporator perform in a state when the compressor is turned off is.

The Reifentfernungselement can with a Durchgangsschalteinrichtung, the refrigerant downstream of the cooler is arranged, and a hot gas supply channel, by which the high-temperature refrigerant from the passage switching means a refrigerant upstream side the second evaporator is supplied, be provided. In In this case, the control unit controls the passage switching means, around a refrigerant channel in a state when the compressor is in operation, to the hot gas supply passage to switch, and it leads the frost removal operation of the first and second evaporators by using high temperature refrigerant.

According to one Still another aspect of the present invention includes a Ejektorpumpenkreisvorrichtung a compressor, which is a refrigerant sucks and compresses; a cooler, the heat the high-pressure refrigerant discharged from the compressor radiates; a ejector; the one nozzle section for reducing a pressure of the refrigerant downstream of the radiator to the refrigerant expand, and the refrigerant through a jet stream of the refrigerant from the nozzle section sucks; a first evaporator which discharges into a refrigerant suction port of the ejector to be sucked refrigerant evaporates to a cooling capacity to have; a second evaporator, that from the ejector outflowing refrigerant evaporates to a cooling capacity to have; a reservoir of refrigerant downstream the second evaporator is arranged; a tire removal element, which heats the first and the second evaporator, so one To perform frost removal operation, in the frost adhering to the first and second evaporators Will get removed; a storage temperature sensing element having a Temperature of the memory detected; and a control unit that the Tear removal element controls to the first and the second evaporator to heat and perform the Reifentfernungsbetrieb, if a temperature detected by the storage temperature detection element an outer wall the memory reaches a predetermined temperature. In this case, too may cause frost formation on a component on a low pressure side, such as memory, are effectively restricted.

Also In this case, the frost removal element may be located on an upstream side of the air be arranged first and second evaporator.

According to one Further aspect of the present invention may be arranged a Reifentfernungselement to heat the first and second evaporators to perform such a Reifentfernungsbetrieb, in which at the first and the frost attached to the second evaporator is removed, and a control unit may control the tire removal member to move the tire removal member Reifentfernungsbetrieb the first and second evaporator perform. That's why it's possible to perform the Reifentfernungsbetrieb suitably during the cooling the first and second evaporators is effectively performed.

To the By way of example, the tire removal element can be made up of a plurality of heating element sections for heating the first and second evaporators in the frost removal operation be constructed. Furthermore For example, the frost removal member may be airflowed on both the first and the second Also, the second evaporator may be arranged or arranged so be that it is both the first and the second evaporator contacted, or can for heating both the first and the be arranged second evaporator.

Alternatively, the Reifentfernungselement be provided on one side of the first and second evaporator. In this case, a radiant heat absorbing member may be provided on the other of the first and second evaporators so that radiant heat is transferred from the frost removing member to the radiant heat absorbing member. Alternatively, the frost removal member is provided on one side of the first and second evaporators so that the heat is transferred from the frost removal member to the other of the first and second evaporators by convection.

According to one Still another aspect of the present invention may be used in an ejector cycle device a heat conduction element be arranged to the first and the second evaporator connect so as to heat between the first evaporator and the second evaporator transferred to. In this case, by performing the frost removal operation frost on the first and second evaporators be effectively removed in a short time.

To the Example may be the heat conduction element be arranged so that it contacts the Reifentfernungselement, or may be in the first and the second evaporator arranged heat exchange ribs or a holding member for holding the first and second evaporators or attached to the front ends of the first and second evaporator Be side plates.

BRIEF DESCRIPTION OF THE DRAWINGS

Above and other objects, features and advantages of the present invention will be preferred from the following detailed description Examples under With reference to the accompanying drawings better understandable.

In this demonstrate:

1 a schematic representation of an ejector cycle device for a vehicle according to a first embodiment of the present invention;

2 a schematic partial cross-sectional view of an example of a channel opening / closing mechanism of an ejector according to the first embodiment;

3 a block diagram of an electrical control unit of the first embodiment;

4 a representation of the operation of the first embodiment;

5A and 5B Representations of the operation of an opening and closing control of an opening / closing valve when a compressor is turned off, according to the first embodiment;

6 a representation of the operation of components of an ejector cycle device according to a second embodiment of the present invention;

7 an illustration of a way to determine a pumping out time according to the second embodiment;

8th a schematic representation of an ejector cycle device for a vehicle according to a third embodiment of the present invention;

9 a representation of the operation of components of the ejector cycle device according to the third embodiment;

10A and 10B Representations of an operation of an opening and closing control of an opening / closing valve when a compressor is turned off, according to the third embodiment;

11 a representation of the operation of components of an ejector cycle device according to a fourth embodiment of the present invention;

12 a schematic representation of an ejector cycle device for a vehicle according to a fifth embodiment of the present invention;

13 a representation of the operation of components of an ejector cycle device according to the fifth embodiment;

14 a schematic representation of an ejector cycle device for a vehicle according to a sixth embodiment of the present invention;

15 a schematic representation of an ejector cycle device for a vehicle according to a seventh embodiment of the present invention;

16 a representation of the operation of components of an ejector cycle device according to the seventh embodiment;

17 a schematic representation of an ejector cycle device for a vehicle according to an eighth embodiment of the present invention;

18 a representation of the operation of components of the ejector cycle device according to the eighth embodiment;

19 a schematic representation of an ejector cycle device for a vehicle according to a ninth embodiment of the present invention;

20 a schematic representation of an ejector cycle device for a vehicle according to a tenth embodiment of the present invention;

21 a schematic representation of an ejector cycle device for a vehicle according to an eleventh embodiment of the present invention;

22 a schematic representation of an ejector cycle device for a vehicle according to a twelfth embodiment of the present invention;

23 a schematic representation of an ejector cycle device for a vehicle according to a thirteenth embodiment of the present invention;

24 a schematic representation of an ejector cycle device for a vehicle according to a fourteenth embodiment of the present invention;

25 a schematic representation of an ejector cycle device for a vehicle according to a fifteenth embodiment of the present invention;

26 a schematic representation of an ejector cycle device for a vehicle according to a sixteenth embodiment of the present invention;

27 a schematic representation of an ejector cycle device for a vehicle according to a seventeenth embodiment of the present invention;

28 a schematic representation of an ejector cycle device for a vehicle according to an eighteenth embodiment of the present invention;

29 FIG. 12 is an illustration showing examples of settings of an interval of a frost removal operation (defrosting operation) relative to an outside air temperature; FIG.

30 FIG. 10 is a time chart of a frost removal control (defrosting control) in the ejector cycle device of FIG 28 ;

31 a representation of examples of the settings of a predetermined temperature T relative to an outside air temperature;

32 a schematic representation of an ejector cycle device for a vehicle according to a nineteenth embodiment of the present invention;

33 a schematic representation of an ejector cycle device for a vehicle according to a twentieth embodiment of the present invention;

34 1 is a schematic diagram of an ejector cycle device for a vehicle according to a twenty-first embodiment of the present invention;

35 FIG. 10 is a time chart of a frost removal control in the ejector cycle device of FIG 34 ;

36 a schematic representation of an ejector cycle device for a vehicle according to a twenty-second embodiment of the present invention;

37 FIG. 10 is a time chart of a frost removal control in the ejector cycle device in FIG 36 ;

38 FIG. 12 is a schematic diagram of an ejector cycle device for a vehicle according to a twenty-third embodiment of the present invention; FIG.

39A FIG. 2 is a schematic diagram of an ejector cycle device for a vehicle according to a twenty-fourth embodiment of the present invention; and FIG 39B a representation of a direction shown by an arrow A in FIG 39A ;

40A 12 is a schematic diagram of an ejector cycle device for a vehicle according to a twenty-fifth embodiment of the present invention, and FIG 40B a representation of a direction shown by an arrow B in 40A ;

41A and 41B a schematic A front view and a schematic side view of an arrangement example of evaporators and an electric heating element according to a twenty-sixth embodiment of the present invention;

42A and 42B a schematic front view and a schematic side view of an arrangement example of evaporators and an electric heating element according to a twenty-seventh embodiment of the present invention;

43A and 43B Schematic diagrams of an arrangement example of evaporators and an electric heating element according to a twenty-eighth embodiment of the present invention, wherein 43A shows a state of normal operation and 43B shows a state at the time of a frost removal operation;

44A and 44B a front view and a side view of an arrangement example of evaporators and an electric heating element according to another embodiment of the present invention;

45A and 45B a front view and a side view of an arrangement example of evaporators and an electric heating element according to a still further embodiment of the present invention;

46A and 46B a front view and a side view of an arrangement example of evaporators and an electric heating element according to a still further embodiment of the present invention;

47A a schematic representation of an ejector cycle device according to a twenty-ninth embodiment of the present invention, and 47B a representation of a by an arrow A in 47A represented direction;

48 FIG. 12 is a graph showing a change of a cooling performance and a change of a frost removal performance (defrosting performance) according to a heat transfer amount of integrated fins; FIG.

49A a schematic representation of an ejector cycle device according to a thirtieth embodiment of the present invention, and 49B a representation of a by an arrow B in 49A represented direction;

50A and 50B a schematic front view and a schematic side view of an arrangement example of evaporators and an electric heating element according to a thirty-first embodiment of the present invention; and

51A and 51B 12 is a schematic front view and a schematic side view of an arrangement example of evaporators and an electric heating element according to a thirty-second embodiment of the present invention.

DETAILED DESCRIPTION THE PREFERRED EMBODIMENTS

(First embodiment)

1 and 2 show the first embodiment of the present invention. 1 shows an example in which an ejector cycle device 10 is used according to the first embodiment for a cooling device for a vehicle. Here, the cooling device for a vehicle of this embodiment cools the inside of a room to an extremely low temperature of, for example, about -20 ° C.

In the ejector cycle device 10 This embodiment becomes a compressor 11 for sucking and compressing a refrigerant by a vehicle engine (not shown) via an electromagnetic clutch 12 , a belt and the like turned and driven. This compressor 11 is connected to the vehicle engine and disconnected from it by the electromagnetic clutch 12 intermittently power is sent, whereby it is operated intermittently. That is, the refrigerant discharge capacity of the compressor 11 by changing the intermittent operating rate of the compressor 11 by intermittently actuating the electromagnetic clutch 12 controlled.

A cooler 13 is on the refrigerant discharge side of this compressor 11 arranged. The cooler 13 exchanges heat between that of the compressor 11 discharged high-pressure refrigerant and by a cooling fan sent outside air (air outside the vehicle compartment) to cool the high-pressure refrigerant.

In this embodiment, a conventional chlorofluorocarbon-based refrigerant is used as the refrigerant circulating in a refrigeration cycle. In this case, the ejector cycle device forms 10 a circuit with a subcritical pressure, in which the high pressure does not exceed the critical pressure of the refrigerant. Therefore, the works cooler 13 as a condenser for cooling and condensing the refrigerant.

A liquid receiver 14 is as a vapor / liquid separator for separating the vapor and the liquid of the refrigerant and for storing the liquid refrigerant refrigerant downstream of the radiator 13 arranged, and the liquid refrigerant is from this liquid receiver 14 discharged to the downstream side. A throttling mechanism 15 is with the refrigerant downstream side of the liquid receiver 14 connected.

In particular, this throttle mechanism 14 composed of a fixed throttle such as a capillary tube and an orifice and reduces the high-pressure liquid refrigerant from the liquid receiver 14 to a medium-pressure refrigerant in the state of two phases of vapor and liquid. Then there is an opening / closing valve 16 with the downstream side of this throttle mechanism 15 connected. In particular, this opening / closing valve 16 constructed from an electromagnetic valve and is in operative connection with the intermittent operation of the compressor 11 opened and closed, as described below.

Then there is an ejector pump 17 on the farther downstream side of the opening / closing valve 16 arranged. This ejector pump 17 is used as a pressure reducing means for reducing the pressure of the refrigerant and also as a refrigerant circulation means (pulse transporting pump) for circulating the refrigerant by the suction operation (entrainment action) of the high-velocity discharged refrigerant flow.

The ejector pump 17 is provided with a nozzle section 17a which reduces the passage area through which the passage through the opening / closing valve 16 medium pressure refrigerant passes, and which reduces the pressure of the medium-pressure refrigeration means, thereby expanding the medium-pressure refrigerant in an isentropic manner; and a refrigerant suction port 17b in the same space as the refrigerant discharge port of the nozzle portion 17a is disposed and the vapor-phase refrigerant from a later-described first evaporator 18 sucks.

A mixing section 17c for mixing the high-speed refrigerant from the nozzle section 17a and of the refrigerant suction port 17b sucked refrigerant is downstream of the nozzle portion 17a and the refrigerant suction port 17b arranged. Then, a diffuser portion constituting a pressure increasing part is 17d downstream of the mixing section 17c in the ejector pump 17 arranged.

This diffuser section 17d is formed in a shape in which the passage area for the refrigerant is gradually increased, and performs a process of reducing the speed of the refrigerant flow and increasing the pressure of the refrigerant, that is, a process of converting the speed energy of the refrigerant into its pressure energy.

Next is the ejector 17 with a channel opening / closing mechanism 17e for variably controlling the passage area of the nozzle portion 17a Mistake. 2 shows an example of this channel opening / closing mechanism 17e and a needle 17f located in the channel of the nozzle section 17a is arranged in such a way that it moves in the longitudinal direction of the channel. The tip of this needle 17f is formed in a slender and pointed shape (tapered shape).

The base section of the needle 17f is with a drive section 17g connected, and the needle 17f is determined by the operating force of this drive section 17g in the longitudinal direction of the channel (in the up / down direction in FIG 2 ) emotional.

If the needle 17f from the position in 2 is moved down and the large diameter section of the needle 17f in pressure contact with the inner wall surface of the minimum passage portion of the nozzle portion 17a can be brought, the channel of the nozzle section 17a be completely closed. As drive section 17g For example, a motor actuator such as a stepper motor or an electromagnetic solenoid mechanism may be used. That is, various types of drive devices that are electrically controlled may function as a drive section 17g be used.

A second evaporator 21 is with the downstream side of the diffuser section 17d the ejector pump 17 connected, and the refrigerant downstream side of this second evaporator 21 is with the suction side of the compressor 11 connected.

There is also a refrigerant branch channel 19 from the upstream part of the ejector 17 branched off, and the downstream side of this refrigerant branch channel 19 is with the refrigerant suction section 17b the ejector pump 17 connected. A reference character Z denotes the branch point of the refrigerant branch passage 19 ,

A throttling mechanism 20 is in this refrigerant branch channel 19 arranged, and the first vaporizer 18 is downstream of this throttle mechanism 20 arranged. The throttle mechanism 20 is a pressure reduction unit for controlling the refrigerant flow rate to the first evaporator 18 and therefore may be formed of a fixed throttle, such as a capillary tube and an orifice. In this regard, an electric control valve whose valve opening (opening of the throttle passage) is controlled by an electrically driven actuator as a throttle mechanism 20 be used.

In this embodiment, the first and second evaporators 18 . 21 both combined together to form an integrated construction. For example, the components of the two evaporators 18 . 21 formed of aluminum and connected by soldering in the integrated construction.

To be cooled air is through a common electrically driven blower 22 to the two evaporators 18 . 21 blown as indicated by an arrow A in 1 shown, causing the blown air through the two evaporators 18 . 21 is cooled. The through these two evaporators 18 . 21 Cooled cooling air, for example, becomes a common room to be cooled 23 cleverly. In this way, the common room to be cooled becomes 23 through the two evaporators 18 . 21 cooled.

Here are of these two evaporators 18 . 21 the one with a channel downstream of the ejector 17 connected second evaporator 21 on the upstream side in the air flow direction shown by an arrow A, and that with the refrigerant suction port 17b the ejector pump 17 connected first evaporator 18 is disposed on the downstream side in the air flow direction shown by the arrow A.

In this regard, in this embodiment, the ejector cycle device becomes 10 for the cooling device for a vehicle as described above, and therefore, the common space to be cooled is 23 an interior of a cooling unit for receiving goods to be cooled. In the room to be cooled 23 is a temperature sensor (thermistor) 24 for detecting an internal temperature of the room 23 arranged.

Next, an electric control unit of this embodiment will be based on 3 described. A control unit 25 is composed of a well-known microcomputer including a CPU, a ROM and a RAM and its peripheral circuits. This control unit 25 performs various types of calculations and processing on the basis of control programs stored in the ROM to perform the functions of the above-mentioned various parts 12 . 16 . 17g and 22 to control.

Not just the reading of the above temperature sensor 24 but also measuring signals from a group of sensors 26 and various kinds of operation signals from the operation panel 27 become the control unit 25 entered.

In particular, the group contains sensors 26 an outside air sensor for detecting an outside air temperature (temperature outside the vehicle compartment) and the like. The control panel 27 is equipped with a temperature setting switch for setting the cooling temperature of the room to be cooled 23 Mistake.

Next, the operation of the ejector cycle device will be described 10 of the first embodiment. First, a basic operation in the state of operation of the compressor 11 described. If through the control output of the control unit 25 Electricity through the electromagnetic clutch 12 flows to the electromagnetic clutch 12 put in the connection state, the rotational force of the vehicle engine is on the compressor 11 transferred to the compressor 11 to operate.

In this operating condition of the compressor 11 becomes the opening / closing valve 16 through the control output of the control unit 25 brought into a valve opening state. In the ejector pump 17 becomes the drive section 17g through the control output of the control unit 25 driven to the needle 17f to a certain opening position of the nozzle portion 17a to move.

Therefore, the refrigerant flows in a high temperature / high pressure state passing through the compressor 11 compressed and discharged from it, into the radiator 13 , In the cooler 13 The high-temperature refrigerant is cooled by the outside air and condensed. The refrigerant after flowing through the radiator 13 is through the liquid receiver 14 separated into vapor and liquid, and the high-pressure liquid refrigerant becomes the downstream side of the liquid collecting vessel 14 issued and through the throttle mechanism 15 directed.

The liquid high-pressure refrigerant is in the opening / closing valve 16 decompressed to an intermediate pressure, whereby it enters a two-phase state of a vapor and a liquid phase. This medium-pressure refrigerant is at the branch point Z in a refrigerant flow to the ejector 17 and a refrigerant flow to Refrigerant branch passage 19 branched.

That into the ejector 17 flowing refrigerant is through the nozzle section 17a reduced in pressure and stretched. Therefore, the pressure energy of the refrigerant through the nozzle portion becomes 17a converted into velocity energy, and the refrigerant is at a high speed from the jet port of this nozzle portion 17a pushed out. The refrigerant (vapor-phase refrigerant) after flowing through the first evaporator 18 of the refrigerant branch channel 19 is simultaneously from the refrigerant suction port 17b sucked by a pressure reduction of the refrigerant.

That from the nozzle section 17a discharged refrigerant and into the refrigerant suction port 17b sucked refrigerants are in the mixing section 17c downstream of the nozzle section 17a mixed together and flow into the diffuser section 17d , In this diffuser section 17d the passage area becomes larger to convert the velocity energy (expansion energy) of the refrigerant into pressure energy, thereby increasing the pressure of the refrigerant.

That from the diffuser section 17d the ejector pump 17 flowing refrigerant flows into the second evaporator 21 , In the second evaporator, the low-pressure refrigerant absorbs heat from the air blown in the direction shown by the arrow A and vaporizes. The vapor phase refrigerant after evaporation is added to the compressor 11 sucked and compressed again.

In contrast, this is in the refrigerant branch channel 19 flowing refrigerant is reduced in pressure by the throttle mechanism and becomes a low-pressure refrigerant, and the low-pressure refrigerant flows into the first evaporator 18 , In the first evaporator 18 The refrigerant absorbs heat from the air blown in the direction shown by the arrow A and vaporizes. The vapor-phase refrigerant after the evaporation is passed through the refrigerant suction port 17b into the ejector pump 17 sucked.

As described above, according to this embodiment, the refrigerant on the downstream side of the diffuser portion 17d the ejector pump 17 the second evaporator 21 be supplied, and the refrigerant on the side of the refrigerant branch channel 19 can through the throttle mechanism 20 the first evaporator 18 be supplied. Therefore, the first and second evaporators can 18 . 21 simultaneously perform a cooling process. For this reason, that by both the first and the second evaporator 18 . 21 cooled cooling air in the room to be cooled 23 blown out to the room 23 to cool.

Here, the refrigerant evaporation pressure of the second evaporator becomes 21 to one through the diffuser section 17d increased pressure, while the outlet of the first evaporator 18 with the refrigerant suction port 17b the ejector pump 17 connected is. Accordingly, the lowest pressure immediately after the nozzle portion 17a is generated on the first evaporator 18 be applied.

Thereby, the refrigerant evaporation pressure (the refrigerant evaporation temperature) of the first evaporator 18 lower than the refrigerant evaporation pressure (the refrigerant evaporation temperature) of the second evaporator 21 be. The second evaporator 21 with a higher refrigerant evaporation temperature is disposed on the upstream side in the air flow direction shown by the arrow A, and the first evaporator 18 with a lower refrigerant evaporation temperature is disposed on the downstream side. Therefore, both a temperature difference between the refrigerant evaporation temperature and the air temperature in the second evaporator 21 and a temperature difference between the refrigerant evaporation temperature and the air temperature in the first evaporator 18 be ensured.

For this reason, the first and second evaporators can 18 . 21 to improve their cooling performance effectively. Therefore, the cooling capacity for the common room to be cooled 23 by a combination of the first and second evaporators 18 . 21 be effectively increased. Further, the suction pressure of the compressor 11 through the diffuser section 17d be increased so as to increase the driving force of the compressor 11 to reduce.

In addition, in the ejector-type refrigerant cycle device of this example, that of the branching point Z is upstream of the ejector 17 branched refrigerant branch channel 19 with the refrigerant suction port 17b the ejector pump 17 connected and is with the throttle mechanism 20 and the first evaporator 18 Mistake. Therefore, the low pressure refrigerant with the two phases of vapor and liquid can be the first evaporator 18 through the refrigerant branch channel 19 be fed independently.

For this reason, the flow rate of the first evaporator 18 flowing refrigerant through the throttle mechanism 20 without dependence on the function of the ejector pump 17 be independently controlled.

In addition, under the condition that the heat load of the circuit is small, the difference between the high pressure and the low pressure in the circuit becomes small, and therefore, one into the ejector 17 flowing refrigerant small. In this case, in the conventional refrigerating cycle of JP-B1-3322263, the flow rate of the refrigerant flowing through the evaporator on the ejector suction side (corresponding to the first evaporator) depends 18 in this embodiment) only from the refrigerant suction power of the ejector. Therefore, an amount of refrigerant entering the ejector becomes smaller → the refrigerant suction capacity of the ejector decreases → the flow rate of the refrigerant of the suction side evaporator becomes smaller. This makes it difficult to ensure the cooling performance of the suction-side evaporator.

In contrast, according to this embodiment, the refrigerant flow is upstream of the ejector 17 branches, and this branched refrigerant is through the refrigerant branch channel 19 into the refrigerant suction port 17b sucked. Therefore, the refrigerant branch channel 19 parallel to the ejector pump 17 in the refrigeration cycle device 10 connected.

For this reason, the refrigerant branch channel 19 the refrigerant by utilizing not only the refrigerant suction power of the ejector 17 but also the refrigerant suction / discharge capacity of the compressor 11 be supplied. This allows, even with a phenomenon, that the input power of the ejector pump 17 becomes smaller, a reduction amount of the flow rate of the refrigerant of the first evaporator 18 be made smaller. Therefore, even under the conditions of a low heat load, the cooling performance of the first evaporator 18 easy to be guaranteed.

Next, the intermittent control of the compressor 11 described. Basically, the operation of the compressor 11 on the basis of such an internal temperature Tr of the room to be cooled 23 (hereafter referred to as "inside temperature") detected by the temperature sensor 24 is detected, intermittently controlled.

In particular, the control unit interrupts 25 , as in 4 when the internal temperature Tr decreases to a lower limit set temperature Toff, the current passage through the electromagnetic clutch is shown 12 to the operation of the compressor 11 to stop. When the internal temperature Tr by stopping the operation of the compressor 11 rises to an upper limit setting temperature Ton, the control unit sends 25 Electricity through the electromagnetic clutch 12 to the compressor 11 to start again.

in this connection is For example, the lower limit set temperature Toff is about -20 ° C to -22 ° C, and the upper limit set temperature Ton is a predetermined temperature higher than the lower limit set temperature Toff, for example, about -16 ° C to -18 ° C.

In this way, by intermittently controlling the operation of the compressor 11 in accordance with the level of the inside temperature Tr, the inside temperature Tr is controlled within a predetermined temperature range between the lower limit set temperature Toff and the upper limit set temperature Ton.

The opening / closing valve 16 and the passage opening / closing mechanism 17e the ejector pump 17 be through the control unit 25 in operative connection with the intermittent control of the compressor 11 controlled as follows. That is, when the inside temperature Tr decreases to the lower limit set temperature Toff, both the opening / closing valve become 16 as well as the passage opening / closing mechanism 17e the ejector pump 17 in operative connection with stopping the operation of the compressor 11 brought into a closed state.

The opening / closing valve 16 is for a first specific time t1 in a period of time during which the compressor 11 is shut off, held continuously in a closed state and is then returned first to an open state. When the opening / closing valve 16 is returned to the opening state and then elapses a second predetermined time t2, the passage opening / closing mechanism 17e the ejector pump 17 returned to an opening state.

After the passage opening / closing mechanism 17e returned to the open state, the compressor is 11 started again. Here, the first predetermined time t1 and the second predetermined time t2 are set in such a manner that t1> t2 holds.

In particular, either a first control based on the inside temperature Tr or a second control based on a timer function for opening / closing control of the opening / closing valve 16 and the passage opening / closing mechanism 17e the ejector pump 17 be used.

First, the first control will be described. In the first control, as in 4 1, a first auxiliary setting temperature T1 which is higher than the lower limit setting temperature Toff by a certain value, and a second auxiliary setting temperature T2 slightly higher than that first auxiliary setting temperature T1 and slightly lower than the upper limit setting temperature Ton is set as setting temperatures for the inside temperature Tr.

When the compressor 11 is turned off and then the internal temperature Tr rises to the first auxiliary setting temperature T1, first the opening / closing valve 16 returned to an opening state. When the inside temperature Tr further rises to the second auxiliary setting temperature T2, the through-opening / closing mechanism also becomes 17e the ejector pump 17 returned to an opening state. Then, when the inside temperature Tr rises further to the upper limit setting temperature Ton, the compressor becomes 11 started again. 5A Fig. 15 is a diagram for illustrating in common such opening / closing states of the opening / closing valve 16 , which are determined on the basis of the internal temperature Tr.

In contrast, in the second control, the above first determined time t1 and the above second determined time t2 are determined directly by the timer function of the control unit 25 set. 5B FIG. 12 shows an example of a method of determining the first predetermined time t1, that is, closing the opening / closing valve 16 required time t1, and this example will be described later in detail.

By the opening / closing valve 16 in operative connection with the process of switching off the compressor 11 is brought into a closed state as described above, the channel upstream of the branch point Z is brought into a locked state. It is possible if the compressor 11 is turned off, a flow of the refrigerant upstream of the opening / closing valve 16 into the channel to the ejector pump 17 and in the refrigerant branch channel 19 by preventing the difference between the high pressure and the low pressure in the circuit.

Because of this, it is possible if the compressor 11 is turned off, to prevent the occurrence of flow noise when the refrigerant through the nozzle section 17a the ejector pump 17 and the throttle mechanism 20 of the branch channel 19 arrives.

At the same time, it is possible to collect the liquid refrigerant in the first and second evaporators 18 . 21 to prevent and thus returning and compressing the liquid refrigerant to / through the compressor 11 to prevent when the compressor is started next time.

In addition, it is possible to flow the refrigerant upstream of the opening / closing valve 16 for the first, time t1 determines during which the opening / closing valve 16 is in a closed state, in the first and the second evaporator 18 to prevent. Therefore, the high pressure and the low pressure in the circuit can be prevented from getting into equilibrium.

In particular, as shown by solid lines H and L in the lower part of 4 shown for the first specific time t1, during which the opening / closing valve 16 is kept in a closed state after the compressor 11 shut off, the high pressure is slightly lower than when the compressor 11 is in operation, and the low pressure will be slightly higher than when the compressor 11 is in operation and is kept at a comparatively low value.

This means that the refrigerant temperatures in the first and second evaporator 18 . 21 be kept at comparatively low levels, even after the compressor 11 is switched off.

When the refrigerant from the high pressure side into the first and the second evaporator 18 . 21 flows when the compressor 11 is switched off, the low pressure increases → the refrigerant temperature in the first and in the second evaporator 18 . 21 gets higher, and the internal temperature Tr rises. The increase in the internal temperature Tr results in a problem of shortening the compressor turn-off time → increasing the power required to drive the compressor. According to this embodiment, when the compressor 11 is turned off, the above problem can be avoided by the opening / closing valve 16 is set in a closed state.

When the compressor 11 is turned off, the first and the second evaporator 18 . 21 set to a state where they substantially stop the cooling operation. Therefore, in this embodiment, the electrically driven blower 22 for blowing air to the first and second evaporators 18 . 21 in operative connection with the process of switching off the compressor 11 off. However, if it is necessary, a temperature distribution in the room to be cooled 23 To make even, the electrically driven blower 22 be operated continuously, even if the compressor 11 is switched off.

In addition, when the opening / closing valve 16 in operative connection with the process of switching off the compressor 11 is closed to suddenly interrupt the flow of non-compressible liquid-phase refrigerant Chen, the cold medium pressure upstream of the opening / closing valve 16 abruptly, causing a waterfall phenomenon and producing unusual sounds. In this embodiment, however, the throttle mechanism 15 upstream of the opening / closing valve 16 arranged, and the flow of medium pressure refrigerant, through this throttle mechanism 15 is reduced in pressure and brought into the state of two phases of vapor and liquid is interrupted by the opening / closing valve 16. Therefore, the opening / closing valve interrupts 16 finally, the refrigerant stream containing the compressible vapor phase refrigerant.

As a result, this can prevent the refrigerant pressure upstream of the opening / closing valve 16 suddenly rises when the opening / closing valve 16 is closed. Therefore, it is possible to avoid a water surge phenomenon (liquid splash phenomenon) and prevent the occurrence of unusual noises caused by the phenomenon.

The opening / closing valve 16 is held in a closed state for the first predetermined time t1, and then returned to an open state. Here, the passage opening / closing mechanism 17e the ejector pump 17 still kept in the closed state. Therefore, this passes through the opening / closing valve 16 flowing refrigerant only through the refrigerant branch channel 19 and flows through the first evaporator 18 → the ejector pump 17 → the second evaporator 21 ,

This can make the high pressure and the low pressure in the circle uniform, ie bring the high pressure and the low pressure in equilibrium. Specifically, the high pressure refrigerant flows when the opening / closing valve 16 is opened in a low-pressure passage, whereby the high pressure drops to an even lower value when the opening / closing valve 16 is closed, as by the solid line H in the lower part of 4 shown. As a result, the low pressure rises to an even higher value than when the opening / closing valve 16 is closed as shown by the solid line L.

The high pressure and the low pressure in the circuit are between the time when the opening / closing valve 16 is opened, and the time when the compressor 11 is restarted (for the time t3) brought into equilibrium. This time t3 becomes the period for pressure equalization. The dashed lines b, c of the high pressure and the low pressure in the lower part of 4 show the pressure balance when the opening / closing valve 16 is not opened and closed (or controlled) as shown by the dotted line d, and shows a case where the high pressure and the low pressure are completely balanced at the same pressure of intermediate pressure between them.

In this embodiment, the high pressure and the low pressure in the circuit only for a duration t3 of the last half during a period for which the compressor 11 switched off, brought into balance. Therefore, the pressure equalization is terminated before the high pressure and the low pressure are brought to the same intermediate pressure. As a result, even if the pressure equalization is ended (when the compressor 11 is restarted), a pressure difference between the high pressure and the low pressure, as in 4 shown.

However, the pressure difference between the high pressure and the low pressure can be reduced by balancing the high pressure and the low pressure in the circuit. Accordingly, the for starting the compressor 11 required energy compared to a case where the compressor 11 is restarted while maintaining a large pressure difference between the high pressure and the low pressure, to a large extent be reduced.

In addition, the passage opening / closing mechanism becomes 17e the ejector pump 17 for a duration t2, which is a large part of this pressure equalization period t3, kept in the closed state. Therefore, it is possible to prevent the refrigerant at the nozzle portion 17a the ejector pump 17 Makes flow noises.

In 4 The point in time is when the passage opening / closing mechanism 17e the ejector pump 17 is returned to an open state, slightly ahead of time when the compressor 11 is restarted. However, this is because of the passage opening / closing mechanism 17e should be safely brought into an open state, before the compressor 11 is restarted. Accordingly, when the passage opening / closing mechanism 17e can be brought into an open state in an extremely short time, the passage opening / closing mechanism 17e also at the same time to start the compressor 11 be returned to the opening state.

In 4 become the opening / closing valve 16 and the passage opening / closing mechanism 17e both simultaneously brought into a closed state when the compressor 11 is switched off. However, it is also possible, a flow of the refrigerant into the ejector 17 to prevent in the opening / closing valve 16 is brought into a closed state. Therefore, the passage opening / closing mechanism can 17e also only a certain time after closing the opening / closing valve 16 in a closed state, as indicated by a broken line a in FIG 4 shown.

While a preferred specific example has been described in a case where the period of time during which the opening / closing valve 16 is in a closed state (first predetermined time t1) in the second control by the timer function of the control unit 25 Incidentally, there is a correlation that the smaller the heat load of the circuit is, the increasing degree of the internal temperature for a duration during which the compressor is set 11 is turned off the smaller and the duration during which the compressor 11 is turned off, the longer it is.

As in 5B shown, the time t1, during which the opening / closing valve 16 is in a closed state, also determined according to the outside air temperature Tam. For example, when the outside air temperature Tam is not higher than a first predetermined temperature Ta in a low temperature range, it is determined that the time t1 during which the opening / closing valve 16 in a closed state, A is (minutes); when the outside temperature Tam is higher than the first predetermined temperature Ta to not higher than a second predetermined temperature Tb in an intermediate temperature range, it is determined that the time t1 during which the opening / closing valve 16 in a closed state, B is (minutes); and when the outside temperature Tam is in a high-temperature region of more than the second predetermined temperature Tb, it is determined that the time t1 during which the opening / closing valve 16 is in a closed state, C is (minutes).

There is a relationship A>B> C between the valve closing times A, B and C, and the time t1 during which the opening / closing valve 16 is in a closed state, is made longer when the outside air temperature is lower (ie, the heat load in the circle is smaller). This allows the time t1, during which the opening / closing valve 16 is in a closed state, be determined according to the heat load condition at an appropriate time.

In 4 a case was described in which the compressor 11 is operated intermittently based on a change in the internal temperature Tr. However, it is also in a case where an occupant manually sets a circuit breaker in the control panel 27 pressed to the compressor 11 operate intermittently, only necessary, the functions of different types of parts in the 4 to control the manner shown.

Second Embodiment

In the first embodiment, the opening / closing valve 16 in operative connection with the process of switching off the compressor 11 closed. In the second embodiment, however, as in FIG 6 shown when the internal temperature Tr of the space to be cooled decreases to the lower limit setting temperature Toff, first, the opening / closing valve 16 closed before the compressor 11 is switched off. This will cause the compressor 11 for a certain time t4 is continuously operated with the upstream channel of the branch point Z and then turned off after that certain time t4 has elapsed.

Here, the specific time t4 is a duration of a pump-out operation in which the compressor 11 drawing in the refrigerant on the low pressure side of the circuit and moving the refrigerant to the high pressure side and holding the refrigerant on the high pressure side. By performing this pump-out operation, that in the first and second evaporators 18 . 21 collected refrigerant amount when the compressor 11 is stopped, compared to the first embodiment can be further reduced. Therefore, it is possible to more effectively prevent a danger that the liquid refrigerant to the compressor 11 is returned and compressed when the compressor 11 will be restarted next time.

For example, it is preferable that the pumping out time t4 is determined specifically according to the outside air temperature, as in FIG 7 shown. That is, when the outside air temperature is in a low temperature range of not higher than the first predetermined temperature Ta, it is determined that the pump down time t4 = G; when the outside air temperature is in an intermediate temperature range of more than the first predetermined temperature ta and not higher than the second predetermined temperature tb, it is determined that the pumping time t4 = H; and when the outside air temperature is in a high temperature range of higher than the second predetermined temperature Tb, it is determined that the pump down time t4 = I.

It gives a relation G> H> I between the pumping times G, H and I, and the pumping time t4 is determined to be longer, when the outside air temperature Tam becomes lower (i.e., the heat load becomes smaller in the circle). This allows the pumping time t4 to a suitable time can be determined according to the heat load condition.

(Third Embodiment)

In the first embodiment, the throttle mechanism 15 and the opening / closing valve 16 upstream of the branching point Z upstream of the ejector 17 arranged. In the third embodiment, however, as in FIG 8th dargstellt, the throttle mechanism 15 and the opening / closing valve 16 upstream of the ejector pump 17 is not provided in the first embodiment described above, but the opening / closing valve 16 is between the downstream side of the throttle mechanism 20 of the refrigerant branch channel 19 and the upstream side of the first evaporator 18 set.

Therefore, according to the third embodiment, the opening / closing valve closes 16 only the passage of the refrigerant branch channel 19 , Therefore, in the third embodiment, the opening / closing valve 16 and the passage opening / closing mechanism 17e the ejector pump 17 both simultaneously in operative connection with the process of turning off the compressor 11 set to a closed state. This allows the passage of the ejector 17 through the passage opening / closing mechanism 17e the ejector pump 17 be locked when the compressor 11 is switched off.

9 shows the operation of different types of parts, with the intermittent operation of the compressor 11 are operatively connected according to the third embodiment. The functionality can be equal to that of 4 except that the passage opening / closing mechanism 17e the ejector pump 17 at the same time to shut off the compressor 11 safely put into a closed state. In this regard shows in 9 a reference numeral t5 the time during which the passage opening / closing mechanism 17e the ejector pump 17 in a closed state is when the compressor 11 is switched off.

10A shows control examples in a case when the opening / closing valve 16 and the passage opening / closing mechanism 17e the ejector pump 17 be determined on the basis of the internal temperature Tr when the compressor 11 is turned off in the third embodiment. 10A has characteristics similar to 5A , and their specific description is omitted.

10B shows control examples in a case when the time t1 during which the opening / closing valve 16 is in a closed state, and the time t5 during which the passage opening / closing mechanism 17e the ejector pump 17 in a closed state is when the compressor 11 is turned off, be determined by the timer function in the third embodiment. 10B has the same characteristics as in 5B ie the time t1 during which the opening / closing valve 16 in a closed state is when the compressor 11 is switched off, is set longer when the outside air temperature Tam is lower. In the drawing, there is a relationship A>B> C between the valve closing timings A, B and C. In addition, the time t5 during which the passage opening / closing mechanism 17e the ejector pump 17 in a closed state is when the compressor 11 is switched off, also set longer when the outside air temperature Tam is lower. In the drawing, there is a relationship D>E> F between valve closing times D, E and F.

(Fourth Embodiment)

A fourth embodiment is a combination of the above third embodiment (circuit construction of FIG 8th ) and the pumping control of 6 (second embodiment).

11 shows the operation of different types of parts with the intermittent operation of the compressor 11 are operatively connected according to the fourth embodiment. When the inside temperature Tr decreases to the lower limit set temperature Toff, the open / close valve becomes 16 and the passage opening / closing mechanism 17e the ejector pump 17 both brought into a closed state simultaneously before the compressor 11 is switched off.

This allows the upstream portion of the first evaporator 18 of the refrigerant branch channel 19 be blocked and the inlet of the ejector 17 can be locked. The compressor 11 is operated for the designated time t4 with the channel held off and then turned off after that certain time t4 has passed.

Therefore, the compressor performs 11 a pumping out operation of the suction of the refrigerant on the low pressure side of the circuit and the movement of the refrigerant to the high pressure side for the predetermined time t4. However, it is possible that in the first and the second evaporator 18 . 21 in the period of time during which the compressor 11 is switched off, to reduce accumulated refrigerant more effectively.

Also, in the fourth embodiment, the time t4 of the pumping out operation can be set longer as the outside air temperature Tam becomes lower (ie, the heat load in the circuit becomes smaller) as in FIG 7 shown.

(Fifth Embodiment)

12 shows the fifth embodiment and corresponds to a circular structure in which a part of the circuit structure of the first embodiment is modified. That is, in the fifth embodiment, a channel switching mechanism 30 downstream of the first evaporator in the refrigerant branch channel 19 arranged.

In particular, this channel switching mechanism 30 composed of a three-way solenoid valve and switches between a first state in which the downstream part of the first evaporator 18 directly to the downstream side of the second evaporator 21 (the suction side of the compressor 11 ), and a second state in which the downstream part of the first evaporator 18 with the refrigerant suction port 17 connected is.

In the first embodiment, the first and second evaporators 18 . 21 combined with each other, and air is blown through the fan 22 that the first and the second evaporator 18 . 21 is common to the first and second evaporator 18 . 21 blown, creating the common room to be cooled 23 through the first and second evaporators 18 . 21 is cooled. However, the fifth embodiment also differs in this point from the first embodiment.

That is, in the fifth embodiment, the first and second evaporators are 18 . 21 formed from separate bodies and are in separate rooms to be cooled 23a . 23b arranged. Because of this, air is blown through separate fans 22a . 22b to the first and second evaporator 18 . 21 blown, causing the separate rooms 23a . 23b be cooled with different temperatures.

Because here the refrigerant evaporation temperature of the first evaporator 18 lower than that of the second evaporator 21 is, the internal temperature of the first, through the first evaporator 18 to cool the room 23a lower than the inside temperature of the second, through the second evaporator 21 to cool the room 23b , For this reason, the second room to be cooled becomes 23b For example, used as a cooling chamber in a cooling device, and the first space to be cooled 23a For example, it is used as a cold chamber of the refrigerator.

temperature sensors 24a . 24b for detecting the internal temperatures Tr1, Tr2 are in the two rooms to be cooled 23a . 23b arranged. The detection signals of these two temperature sensors 24a . 24b become the control unit 25 ( 2 ), and the switching operation of the channel switching mechanism 30 and the functions of the other parts (compressor 11 , Ejector pump passage opening / closing mechanism 17e and opening / closing valve 16 ) are controlled by the control output of this control unit 25 controlled.

13 is an illustration of the operation of the fifth embodiment. Lower limit set temperatures Toff1, Toff2 and upper limit set temperatures Ton1, Ton2 are for the inside temperature Tr1 of the first room to be cooled 23a passing through the first temperature sensor 24a is detected, and the internal temperature Tr2 of the second room to be cooled 23b passing through the second temperature sensor 24b recorded. When the second inside temperature Tr2 lowers to the lower limit set temperature Toff2 at a time t10, the control unit turns on 25 the channel switching mechanism 30 from the second state to the first state. Therefore, the downstream side of the first evaporator becomes 18 directly to the downstream side (the suction side of the compressor 11 ) of the second evaporator 21 connected. At the same time the control unit brings 25 the passage opening / closing mechanism 17e the ejector pump 17 in a closed state. Therefore, the refrigerant flow is interrupted by the ejector and a refrigerant flow in the second evaporator 21 prevented.

As a result, the cooling operation of the second evaporator 21 stopped, and therefore the inside temperature Tr2 of the second room to be cooled starts 23b to get bigger. In contrast, the refrigerant flows continuously through the first evaporator 18 , and therefore, the internal temperature Tr1 of the first room to be cooled decreases 23a even after time t10 on.

When inside temperature Tr1 of the first room to be cooled 23a at the time t11 drops to the lower limit set temperature Toff1, the control unit brings 25 the compressor 11 in a shutdown state and at the same time brings the opening / closing valve 16 in a closed state. This closed state of the opening / closing valve 16 is continued for the time t1, whereby the refrigerant flows into the first evaporator and the second evaporator 21 is prevented. Therefore, the inside temperature Tr1 of the first room to be cooled starts 23a to rise from time t11.

Then the opening / closing valve returns 16 after the time t1 back to the open state. Because at this time the compressor 11 is kept switched off when the opening / closing valve 16 is opened, the high pressure and the low pressure of the circle changes in the Towards making the pressures equal, bringing them into balance. The high pressure and the low pressure of the circuit are balanced for the time t3 until the compressor 11 is restarted. In contrast, the through-opening / closing mechanism returns 17e the ejector pump 17 after the opening / closing valve 16 returns to the closed state and then elapses the time t2, back to the open state (time t2 <time t3).

When the indoor temperature Tr2 of the second room to be cooled 23b at the time t12 rises to the upper limit setting temperature Ton2, the control unit starts 25 again the compressor 11 and turns on the channel switching mechanism 30 from the first state to the second state. Therefore, the downstream side of the first evaporator becomes 18 with the refrigerant suction port 17b the ejector pump 17 connected.

Subsequently, the above operation is repeatedly performed, whereby the internal temperature Tr1 of the first room to be cooled 23a and the internal temperature Tr2 of the second room to be cooled 23b in a predetermined temperature range between their lower limit set temperatures Toff1, Toff2 and their upper limit set temperatures Ton1, Ton2. At the same time, the function and effect of preventing accumulation of the liquid refrigerant in the first and second evaporators 18 . 21 when the compressor 11 is switched off, be effected similar to the first embodiment.

Incidentally, in the above description of the operation, a description has been given of the effect that the compressor 11 is turned off when the internal temperature Tr1 of the first room to be cooled 23a to the lower limit temperature Toff1 drops. The compressor becomes more precise 11 turned off when an AND condition (predetermined condition) is satisfied that the internal temperature Tr1 of the first room to be cooled 23a (a space to be cooled) decreases to the lower limit set temperature Toff1 and that the inside temperature Tr2 of the second space to be cooled 23b (further room to be cooled) does not rise to the upper limit set temperature Ton2. This is because it is possible to determine a state in which the cooling effects of both the first and second evaporators 18 . 21 can be stopped by fulfilling this AND condition.

That is, when the internal temperature of one of these two rooms to be cooled 23a . 23b falls to the lower limit set temperature and the inside temperature of the other room does not rise to the upper limit set temperature, it is only necessary to use the compressor 11 off.

Next shows 13 an example in which the compressor 11 is restarted when the internal temperature Tr2 of the second room to be cooled 23b rises to the upper limit set temperature Ton2. When the indoor temperature Tr1 of the first room to be cooled 23a earlier to the upper limit set temperature Ton1 rises than the inside temperature Tr2 of the second space to be cooled 23b rises to the upper limit set temperature Ton2, it is only necessary to use the compressor 11 to start again at this time.

The baseline is that the compressor 11 is kept continuously shut off before both the internal temperature Tr1 of the first room to be cooled 23a as well as the internal temperature Tr2 of the second room to be cooled 23b do not rise to the upper limit set temperatures Ton1, Ton2, and that it is only necessary to use the compressor 11 to restart if one of the interior temperature Tr1 of the first room to be cooled 23a or the internal temperature Tr2 of the second room to be cooled 23b rises to one of the upper limit set temperature Ton1, Ton2.

In this regard, it is only necessary the blowers 22a . 22b the first and second room to be cooled 23a . 23b in operative connection with the intermittent refrigerant flow into the corresponding evaporators 18 . 21 to operate. In other words, it is only necessary the blower 22a of the first room to be cooled 23a in operative connection with the interruption of the refrigerant flow to the first evaporator 18 shut off and the blower 22a in connection with the restart of the compressor 11 to start again. Analogously, it is only necessary the blower 22b of the second room to be cooled 23b in communication with the interruption of the refrigerant flow in the second evaporator 21 shut off and the blower 22b in connection with the restart of the compressor 11 to start again.

(Sixth Embodiment)

16 shows the sixth embodiment, which is a modification of the fifth embodiment. In the sixth embodiment, the bypass channel 31 of the second evaporator, and a channel switching mechanism 30 is at the branch point of this bypass channel 31 and the second evaporator 21 arranged.

In particular, this channel switching mechanism 30 also constructed from a three-way solenoid valve and switches a first state in which the downstream side of the ejector 17 with the bypass channel 31 is connected, and a second state in which the downstream side of the ejector 17 with the second evaporation tap ready 21 connected is.

In particular, the operation of the sixth embodiment may be the same as that described above 13 shown to be performed. However, if the channel switching mechanism 30 at time t10 in 13 In the sixth embodiment, the second state is switched from the second state to the first state, the refrigerant flow in the second evaporator 21 interrupted. Therefore, it is not necessary at this time, the passage opening / closing mechanism 17e the ejector pump 17 to bring into a closed state, but the passage opening / closing mechanism 17e is kept open continuously.

If then at time t11 in 13 the compressor 11 shut off and the opening / closing valve 16 is closed, it is only necessary, the passage opening / closing mechanism 17e the ejector pump 17 to bring into a closed state. The other functions except the function of opening / closing the ejector 17 in the sixth embodiment may be the same as those in the fifth embodiment.

(Seventh Embodiment)

15 shows the seventh embodiment. In the seventh embodiment, a second branch channel 32 separately to a first branch channel 19 according to the refrigerant branch channel 19 arranged in the first to sixth embodiments.

This second branch channel 32 is between the downstream side of the opening / closing valve 16 and the suction side of the compressor 11 set, and the channel switching mechanism 30 is at the branch position of this branch channel 32 arranged. In particular, this channel switching mechanism 30 also constructed of a three-way solenoid valve and switches a first state in which the downstream side of the opening / closing valve 16 with the branch point Z upstream of the ejector 17 is connected, and a second state in which the downstream side of the opening / closing valve 16 with the second branch channel 32 connected is.

A throttling mechanism 33 is upstream of the second branch channel 32 arranged, and a third evaporator 34 is downstream of this throttle mechanism 33 arranged.

In the seventh embodiment, the first and second evaporators 18 . 21 combined with each other and together with the blower 22a and the temperature sensor 24a in the first room to be cooled 23a arranged. Next are the third evaporator 34 , the blower 22b and the temperature sensor 24b in the second room to be cooled 23b arranged.

16 is an illustration of the operation of the seventh embodiment. When the indoor temperature Tr2 of the second room to be cooled 23b decreases to the lower limit set temperature Toff2, the channel switching mechanism switches 30 in the first state in which the downstream side of the opening / closing valve 16 with the branch point Z upstream of the ejector 17 connected is. When the indoor temperature Tr2 of the second room to be cooled 23b rises to the upper limit set temperature Ton2, the channel switching mechanism switches 30 in the second state in which the downstream side of the opening / closing valve 16 connected to the second branch channel.

In contrast, the intermittent operation of the compressor 11 based on the internal temperatures Tr1, Tr2 of both the first and the second space to be cooled 23a . 23b certainly. In particular, the compressor is 11 switched off when the internal temperature Tr1 of the first room to be cooled 23a decreases to the lower limit setting temperature Toff1 and the inside temperature Tr2 of the second space to be cooled 23b does not rise to the upper limit set temperature Ton2, as at time t13 in FIG 16 shown.

The passage opening / closing mechanism 17e the ejector pump 17 and the opening / closing valve 16 be in operative connection with this process of switching off the compressor 11 brought into a closed state. The time t1 during which the opening / closing valve 16 is in a closed state, is the time t3, during which the pressure equalization takes place after the compressor 11 is switched off, and the time t2 during which the ejector pump 17 can be determined analogously to the first to sixth embodiments within the time t3 during which the pressure equilibrium is formed in a closed state.

(Eighth Embodiment)

17 shows an eighth embodiment, in which a third evaporator 34 and a bypass channel 35 this third evaporator 34 parallel downstream of the second evaporator 21 are arranged. The channel switching mechanism 30 is located at the branching position of this parallel circuit.

In particular, this channel switching mechanism 30 also constructed of a three-way solenoid valve and switches between a first state in which the downstream side of the two th evaporator 21 with the bypass channel 35 is connected, and a second state in which the downstream side of the second evaporator 21 with the third evaporator 34 connected is.

Also in the eighth embodiment, the first and second evaporators 18 . 21 combined with each other and are together with the blower 22a and the temperature sensor 24a in the first room to be cooled 23a arranged. The third evaporator 34 , the blower 22b and the temperature sensor 24b are in the second room to be cooled 23b arranged.

18 is an illustration of the operation of the eighth embodiment. The channel switching mechanism 30 switches the channel, the compressor 11 is operated intermittently, and the opening / closing valve 16 and the ejector pump 17 are opened and closed analogously to the operation in the seventh embodiment.

Ninth Embodiment

19 shows the ninth embodiment in which the third evaporator 34 parallel to the second evaporator 21 is arranged. The first evaporator 18 , the second evaporator 21 and the third evaporator 34 are in the separate rooms to be cooled 23a . 23b respectively. 23c arranged. The fans 22a . 22b and 22c and the temperature sensors 24a . 24b and 24c are individually in the respective rooms to be cooled 23a . 23b respectively. 23c arranged.

Also in the ninth embodiment, the lower limit set temperatures Toff1, Toff2 and Toff3 and the upper limit set temperatures Ton1, Ton2 and Ton3 are the same as those by the temperature sensors 24a . 24b and 24c recorded internal temperatures Tr1, Tr2 and Tr3 set.

In the ninth embodiment, it is recommended that the compressor 11 based on the temperature sensors 24a . 24b and 24c detected internal temperatures Tr1, Tr2 and Tr3 is operated intermittently in the following manner. That is, if any of the inside temperatures Tr1, Tr2 and Tr3 of the first to third spaces to be cooled 23a . 23b and 23c decreases to the respective lower limit set temperature, and none of the other two internal temperatures rises to their upper limit set temperatures, the compressor becomes 11 off.

Furthermore, the compressor can 11 for a period of time during which none of the interior temperatures Tr1, Tr2 and Tr3 of the first to third spaces 23a . 23b and 23c rises to its upper limit setting temperature after the compressor 11 is switched off, be switched off. When any of the inside temperatures Tr1, Tr2 and Tr3 rises to their upper limit set temperature, the operation of the compressor becomes 11 started again. In addition, the opening / closing valve can 16 and the ejector pump 17 be opened and closed on the basis of the same idea as in the embodiments described above.

(Tenth embodiment)

In the ninth embodiment described above, the third evaporator is 34 parallel to the second evaporator 21 arranged. In the tenth embodiment, however, as in 20 represented, the second branch channel 32 parallel to the series connection of the ejector pump 17 and the second evaporator 21 arranged, and a throttle mechanism 33 is upstream of this second branch channel 32 arranged, and the third evaporator 34 is downstream of this throttle mechanism 33 is arranged.

The first evaporator 18 , the second evaporator 21 and the third evaporator 34 are in separate rooms to be cooled 23a . 23b , and 23c arranged. The tenth embodiment is the same as the ninth embodiment in this point. Therefore, the compressor can 11 are operated intermittently in the same manner as in the ninth embodiment.

In the circuit constructions of the fifth to tenth embodiments ( 12 . 14 . 15 . 17 . 19 and 20 ) examples were shown in which the throttling mechanism 15 of the first embodiment not upstream of the opening / closing valve 16 is arranged. However, also in the fifth to tenth embodiments, as in the first embodiment, it is possible to have the effect of preventing a liquid impact phenomenon by disposing the throttle mechanism 15 upstream of the opening / closing valve 16 to create.

Eleventh Embodiment

In the first embodiment, the opening / closing valve 16 arranged upstream of the branch point Z. In the eleventh embodiment, however, as in 21 shown, an opening / closing valve 16 a three-way valve type arranged at the position of the branch point Z.

In particular, this opening / closing valve is the three-way valve type 16 also constructed from a solenoid valve. This opening / closing valve 16 switches between the valve opening state in which the downstream side (high pressure channel side) of the liquid collecting vessel 14 simultaneously with the upstream channel of the ejector 17 and the branch channel 19 is in communication, and a valve closing state in which the downstream side (high-pressure channel side) of the liquid collecting vessel from the upstream channel of the ejector 17 and the branch channel 19 is locked.

Accordingly, it is by switching the opening / closing valve 16 in operative connection with the process of switching off the compressor 11 in the valve-closing state, it is possible to produce the effect of preventing the refrigerant from making flow noises and to prevent backflow of the liquid refrigerant when the compressor 11 is started.

In the eleventh embodiment, the throttle mechanism 15 upstream of the opening / closing valve 16 be arranged to prevent a liquid splash phenomenon when the opening / closing valve 16 opened and closed.

(Twelfth embodiment)

In the in 8th illustrated third embodiment is the opening / closing valve 16 downstream of the throttle mechanism 20 in the refrigerant branch channel 19 arranged. In the twelfth embodiment, however, as in 22 shown, a first and a second throttle mechanism 20a . 20b in series in the refrigerant branch channel 19 arranged, and the opening / closing valve 16 is in the middle of the first and second throttling mechanism 20a . 20b arranged. This construction can also produce the same effect as the third embodiment.

Thirteenth Embodiment

23 shows the thirteenth embodiment, in which the opening / closing valve 16 upstream of the throttle mechanism 20 in the refrigerant branch channel 19 is arranged.

According to the thirteenth embodiment, the opening / closing valve 16 disposed upstream of the throttle mechanism, and it is therefore not expected that the effect of preventing the spill phenomenon can be generated when the opening / closing valve 1 is closed. However, it is also in the thirteenth embodiment by closing the opening / closing valve 16 when the compressor 11 in the same way, the effect of preventing the refrigerant from making flow noises and preventing backflow of the liquid refrigerant when the compressor is turned off is also possible 11 is started to generate.

(Fourteenth Embodiment)

24 shows the fourteenth embodiment and relates to the combination construction of a circuit structure. The fourteenth embodiment has the same circuit structure as the first embodiment.

The throttle mechanism 15 , the opening / closing valve 16 , the ejector 17 and the throttle mechanism 20 of the refrigerant branch channel 19 are together as an integral unit 40 combined. Here is the integral unit 40 an arrangement in which several parts 15 . 16 . 17 and 20 are assembled in advance into an integral structure. Therefore, the entirety of this integral unit 40 treated as a component.

The first and the second evaporator 18 . 21 are also integrated into a structure by soldering or the like as described above to be an integral unit 41 to build.

Therefore, by combining the integral unit 40 the ejector pump 17 and the like with the integral unit 41 the first and the second evaporator 18 . 21 these integral units 40 . 41 both be further combined in one unit.

This integration can be the overall size of both integral units 40 . 41 can therefore reduce a space when mounted in a vehicle. Besides, because both are integral units 40 . 41 can be mounted as a single unit, the assembly work of these units in the vehicle and the like are effectively performed.

In addition, because it is only necessary, a refrigerant inlet 42 and a refrigerant outlet 43 for the totality of both integral units 40 . 41 To put a refrigerant pipe connection easily connected to an external unit.

(Fifteenth Embodiment)

In the first to fourteenth embodiments, the circuit structure in which the liquid collecting vessel has been described 14 downstream of the radiator 13 is arranged. In the fifteenth embodiment, as in FIG 25 represented, the liquid collecting vessel 14 not provided, but a memory 44 A vapor-liquid separator which separates the vapor and the liquid of the refrigerant and discharges the vapor-phase refrigerant is on the suction side of the compressor 11 arranged. The present invention can be found in the Circuit structure with the memory 44 be carried out as follows.

When a refrigerant having a high pressure higher than the supercritical pressure such as carbon dioxide (CO ₂ ) is used as the refrigerant, the ejector cycle device becomes 10 to a circuit with supercritical pressure, and therefore, the high pressure refrigerant only radiates heat in a supercritical pressure state and is not condensed. Therefore, it makes no sense in this circuit with supercritical pressure that the liquid receiver 14 downstream of the refrigerant radiator 13 is arranged, and so can a circular structure with the memory 44 , as in 25 shown used in the fifteenth embodiment.

Sixteenth Embodiment

While the circular structures with the several evaporators 18 . 21 . 34 in the first to fifteenth embodiments, the sixteenth embodiment relates to a circuit configuration with only one evaporator 18 , as in 26 shown.

The memory used as a vapor-liquid separator 44 is downstream of the ejector 17 arranged, and the vapor and the liquid of the refrigerant are through this memory 44 separated, and the separate vapor-phase refrigerant is in the suction side of the compressor 11 initiated. It is a branch passage 45 for connecting a liquid-phase refrigerant outlet of the memory 44 with the refrigerant suction port 17b the ejector pump 17 provided, and the evaporator 18 is in this branch channel 45 arranged.

This evaporator 18 is located upstream of the refrigerant suction port 17b and therefore corresponds to the first evaporator 18 in the first to fifteenth embodiments, wherein the opening / closing valve 16 upstream of the ejector pump 17 is arranged.

Also, in the sixteenth embodiment, it is by closing the opening / closing valve 16 when the compressor 11 is turned off, it is possible to produce the same effect as in the first embodiment and the like. In the sixteenth embodiment, the ejector is 17 not with the channel switching mechanism 17e provided, but if necessary with the channel switching mechanism 17e be provided.

(Seventeenth Embodiment)

The seventeenth embodiment is a modification of the sixteenth embodiment. As in 27 shown, is the opening / closing valve 16 omitted, but the ejector 17 is with the channel switching mechanism 17e Mistake. By bringing the channel switching mechanism into a closed state when the compressor 11 is turned off, it is possible to produce the same effect as in the first embodiment.

In this regard, in the sixteenth and seventeenth embodiments, examples have been shown in which the throttle mechanism 15 omitted in the first embodiment. However, it is needless to say that the throttling mechanism 15 also in the sixteenth and seventeenth embodiments upstream of the opening / closing valve 16 or upstream of the channel switching mechanism.

In the embodiments described above, the control unit close 25 and the opening / closing element 16 . 17e the cooling circuit in response to the shutdown of the compressor, which is caused by the intermittent operation for the compressor. Alternatively, the control unit 25 and the opening / closing element 16 . 17e also close the cooling circuit in response to a shutdown of the electrical power supply. Shutdown may occur when the power switch is turned off, such as an ignition switch of a vehicle or in the event of a power failure. In this case, the compressor stops simultaneously with the shutdown. Therefore, the cooling circuit is closed, even if the compressor is turned off in this case. This turn-off operation may be used in addition to or instead of the operation provided by the above-described embodiments. In addition, the shutdown operation may also be applied to a refrigeration system having a variable displacement compressor or a refrigerating system having a compressor driven by an electric motor. The turn-off operation can be achieved by means of a valve or an electromagnetic actuator with a normally closed function. For example, the valve 16 with a valve body, a biasing member biasing the valve body in a closing direction, such as a spring, and an electromagnetic solenoid operating the valve body when energized in an opening direction. Alternatively, the control unit 25 a turn-off control means for controlling the opening / closing member 16 . 17e in a closed position after the power supply is stopped. In this case, the control circuit has with the control unit 25 a backup power supply, such as a battery or capacitor, having a capacity that is at least sufficient to the controller 25 and the opening / closing element 16 . 17e to keep in function until a closing process is completed. The opening / closing lement 16 . 17e may also include a position hold actuator that is driven by a motor such as a stepper motor.

(Eighteenth Embodiment)

Hereinafter, the eighteenth embodiment of the present invention will be described in detail with reference to FIG 28 to 31 described. 28 FIG. 12 is a schematic diagram of an ejector cycle device according to the eighteenth embodiment of the present invention, and shows an example in which the present invention is applied to a refrigeration cycle of a vehicle-mounted refrigeration unit. FIG. The ejector cycle device has a refrigerant circulation passage for circulating a refrigerant, and the compressor 11 for sucking and compressing the refrigerant is disposed in the refrigerant circulation passage.

In this embodiment, this compressor 11 rotated and driven by a vehicle engine (not shown) via a belt or the like. A refrigerant cooler 13 is refrigerant downstream from the compressor 11 arranged. The refrigerant cooler 13 exchanges heat between that of the compressor 11 discharged high-pressure refrigerant and by a cooling fan (not shown) blown outside air (air outside a vehicle compartment), thereby to cool the high-pressure refrigerant.

The ejector pump 17 is at a section further down the refrigerant than the refrigerant radiator 13 arranged. This ejector pump 17 is a pulse transport pump, that is, a pressure reducing means for reducing the pressure of the liquid refrigerant, and transports a fluid by a entrainment effect. The ejector pump 17 is with the nozzle section 17a provided, which is the passage area of the refrigerant cooler 13 flowing high-pressure refrigerant and throttles to reduce the pressure of the high-pressure refrigerant, thereby expanding the refrigerant in an isentropic manner, and the suction section 17b , which in the same space as the refrigerant outlet of the nozzle section 17a is disposed, a vapor-phase refrigerant sucks from the first evaporator to be described later 18 at.

Further, a diffuser section 17d , the pressure increasing portion of the ejector 17 forms, refrigerant flow downstream of the nozzle portion 17a and the suction section 17b arranged. This diffuser section 17d is formed in such a shape that the passage area of the refrigerant gradually becomes larger, and performs an action of reducing the speed of the refrigerant flow to thereby increase the pressure of the refrigerant, that is, an action of converting the speed energy of the refrigerant into pressure energy.

That from the diffuser section 17d the ejector pump 17 escaping refrigerant flows into the second evaporator 21 , The second evaporator is disposed in an air passage of a cooling unit (not shown) in a cooling box R, and performs a function of cooling the inside of the cooling box R. In particular, air in the cooling box R is through an electrically driven fan 18a in the cooling unit (see 32 ) to the second evaporator 21 blown and through the ejector 17 reduced in pressure. Then, the low-pressure refrigerant absorbs heat from the air in the refrigerator box R in the second evaporator 21 and evaporates, whereby the air in the cooling box R is cooled to achieve a cooling performance.

That in the second evaporator 21 vaporizing vapor phase refrigerant is passed through the compressor 11 sucked and circulated again in the refrigerant circulation passage. In the ejector cycle device of this embodiment, the branch passage is 19 formed at a section between the radiator 13 and the ejector pump 17 of the refrigerant circulation passage branches and reunites with the refrigerant circulation path.

A throttle element 116 for reducing the refrigerant pressure is in this refrigerant branch channel 19 arranged, and the first evaporator 18 is at a section of refrigerant downstream of this throttle device 116 arranged. This first evaporator 18 is near the second evaporator 21 arranged in such a way that it is in series with the second evaporator 21 in an air flow section and in the air passage of the cooling unit (not shown) in the cooling box R downstream of the second evaporator 21 lies. This first evaporator 18 Cools the air in the cooler, through the second evaporator 21 is cooled, continue. In this embodiment, the compressor 11 and the tire removal member 121 (Defrosting element) by a control signal from an electric control unit (control unit, hereinafter referred to as "ECU") 25 electrically controlled.

Next, a construction according to the eighteenth embodiment of the present invention will now be described. In an air duct of the cooling unit (not shown) is an electric heating element 121 (Tire removal element), the first and the second evaporator 18 . 21 heats up to the first and the second evaporator 18 . 21 adhering frost, airflow on the first and second evaporators 18 . 21 arranged.

The first evaporator 18 having a low evaporation temperature and easily deposits frost thereon and whose temperature does not rise slightly, is compatible with a first evaporator temperature sensor (first evaporator temperature detection element) 122 for detecting the temperature, such as a thermistor provided. For example, this first evaporator temperature sensor 122 be mounted on a portion of the temperature rise in the first evaporator 18 most resists. The measurement signal of the first evaporator temperature sensor 122 becomes the ECU 25 and when the frost removal control of melting and removing on the first and second evaporators 18 . 21 deposited frost, becomes the frost removal element 121 energized and by an output signal from the ECU 25 controlled.

Next, the operation of the present embodiment having the above structure will be described. When the compressor 11 is driven by the vehicle engine, the refrigerant that has been compressed and brought into a high temperature / high pressure state is discharged in a direction indicated by an arrow and flows into the radiator 13 , In the cooler 13 The high-temperature refrigerant is cooled by outside air and condensed. That from the radiator 13 effluent liquid-phase refrigerant flows through the refrigerant circulation passage and branches into a flow through the refrigerant branch passage 19 ,

The flow of the refrigerant flowing through the refrigerant circulation passage flows into the ejector 17 and the refrigerant passes through the nozzle section 17a reduced in pressure and stretched. Therefore, the pressure energy of the refrigerant through the nozzle portion becomes 17a converted into the velocity energy, and the refrigerant is from the jet port of this nozzle portion 17a ejected at a high speed. Here, in the first evaporator 18 vaporized vapor phase refrigerant from the suction section 17b sucked by a pressure drop of the refrigerant.

That of the nozzle section 17a ejected refrigerant and that through the suction section 17b sucked in refrigerant will be downstream of the nozzle section 17a mixed together and flow into the diffuser section 17d , In this diffuser section 17d the passage area becomes larger to convert the velocity energy (expansion energy) of the refrigerant into pressure energy, and thus the pressure of the refrigerant through the diffuser portion 17d to increase. That from the diffuser section 17d the ejector pump 17 escaping refrigerant flows into the second evaporator 21 ,

In the second evaporator 21 The refrigerant absorbs heat from air in the cool box, which is passed through the electrically driven blower 18a (please refer 32 ) is blown and evaporated. The vapor phase refrigerant after evaporation is passed through the compressor 11 sucked and compressed and flows again through the refrigerant circulation channel. In contrast, this is due to the refrigerant branch channel 19 flowing refrigerant through the throttle device 116 reduced in pressure, whereby it is brought into a low pressure state. This low pressure refrigerant is in the first evaporator 18 with the by the electrically driven blower 18a blown air in heat exchange (see 32 ) and further absorbs heat from the air in the icebox while the refrigerant passes through the second evaporator 21 flows and evaporates. This leads the first evaporator 18 the cooling operation of the interior of the cooler through, and from the first evaporator 18 effluent vapor phase refrigerant is in the intake section 17b the ejector pump 17 sucked.

Next, the frost removing operation (defrosting operation) will be described. 29 FIG. 12 is a diagram showing examples of the settings of the time interval between the frost removal operations relative to an outside air temperature Tam. In this embodiment, the time interval between the frost removal operations is varied and set to a value in relation to the outside air temperature. 30 FIG. 15 is a time chart of a frost removal control (defrosting control) in the ejector cycle device in FIG 28 , 31 FIG. 15 is an illustration of examples of the settings of a predetermined temperature T for determining the end of the frost removal operation relative to the outside air temperature Tam. FIG.

When the integrated operating time of the compressor 11 a specific time. is achieved, one at the first and the second evaporator 18 . 21 To remove adhering and deposited frost, the compressor 11 shut off and the Reifentfernungselement 121 switched on to the first and the second evaporator 18 . 21 to heat, thereby removing frost. The integrated operating time of the compressor 11 can, as in 29 shown to be varied in connection with the outside air temperature Tam. For example, if the outside air temperature is not higher than 15 ° C (T1), the integrated operating time of the compressor is 11 A (hours); if the outdoor air temperature Tam is higher than 15 ° C (T1) and not higher than 30 ° C (T2), the integrated operating time is B (hours); and when the outside air temperature Tam is higher than 30 ° C (T2), the integrated operation time C is (hours). These hours are set in the relationship A>B> C.

If the reading of the on the evaporator 18 attached first evaporator temperature sensor 122 reaches the predetermined temperature T, the operation of the Reifentfernungselements 121 stopped and the compressor 11 restarted to start a cooling process again. Here, the predetermined temperature T corresponding to the outside air temperature Tam as well as the integrated operating time of the compressor 11 be varied, as in 30 shown. For example, when the outside air temperature Tam is not higher than 15 ° C (T1), the predetermined temperature T for ending the frost removal operation is 8 ° C (a); when the outside air temperature Tam is higher than 15 ° C (T1) and not higher than 30 ° C (T1), the predetermined temperature T for ending the frost removal operation is 10 ° C (b); and when the outside air temperature Tam is higher than 30 ° C (T2), the predetermined temperature T for ending the frost removal operation is 10 ° C (c). The temperatures are set in the relationship a>b> c.

Next, the features and effects of this embodiment will be described. The present embodiment includes the compressor 11 that sucks and compresses the refrigerant; the cooler 13 , the heat from that of the compressor 11 discharged high-pressure refrigerant radiates; the ejector pump 17 that the pressure of the refrigerant downstream of the radiator 13 reduces, thereby expanding the refrigerant, and the refrigerant from the first evaporator 18 sucks; the second evaporator 21 that's out of the ejector 17 escaping refrigerant evaporates to thereby achieve a cooling capacity; the first evaporator 18 that through the ejector 17 sucked refrigerant evaporates to thereby achieve a cooling performance; the tire removal element 121 including the first and second evaporators 18 . 21 heats to thereby at the first and the second evaporator 18 . 21 remove adherent hoop; the first evaporator temperature sensor 122 , which is the temperature of the first evaporator 18 detected; and the ECU 25 , The ECU 25 controls the frost removal operation of the first and second evaporators 18 . 21 to thereby remove frost, and stops the frost removal operation by heating by means of the frost removal member 121 when passing through the first evaporator temperature sensor 122 detected temperature of the first evaporator 18 reaches the predetermined temperature T for terminating the defrosting operation.

In this embodiment, the first evaporator is 18 having a low evaporation temperature and on which frost is easily precipitated and which resists a temperature rise, with the first evaporator temperature sensor 122 Mistake. According to this embodiment, the first evaporator 18 heated until the first evaporator 18 reaches the predetermined temperature T. Therefore, frost never remains on the first and second evaporators 18 . 21 but can be safely removed. Therefore, it is possible to lower the cooling capacity by that on the first and second evaporators 18 . 21 To prevent adhering and deposited on the hoop.

Further, when the frost removal operation of the second evaporator 21 is finished, the heating with the Reifentfernungselement 121 stopped. Therefore, it is possible to eliminate excessive heating and to limit a temperature rise of the space R to be cooled as well as the power consumption required for removing the frost to minimum amounts. In addition, the Reifentfernungselement 121 airflow on the first and second evaporators 18 . 21 arranged. According to this arrangement, flows through the Reifentfernungselement 121 generated heat to an air downstream side and therefore can the first and the second evaporator 18 . 21 heat with high efficiency.

Further, the frost removal element 121 built from the electric heating element. Accordingly, it is easy to use the electric heating element 121 to use as a heater to remove frost. The ECU 25 performs heating of the first and second evaporators 18 . 21 by means of the tire removal element 121 by. Accordingly, it is by heating the first and second evaporators 18 . 21 using the frost removal element 121 in a state when the compressor 11 shut off, possible to finish removing frost in a short time.

In addition, will the predetermined temperature T corresponding to the outside air temperature Tam varies. Normally the airborne one fluctuates Moisture content, and therefore varies the adherent amount of frost according to the outside air temperature Tam. Therefore, the predetermined temperature T is also corresponding the outside air Tam varies to safely remove the hoop.

(Nineteenth embodiment)

32 FIG. 12 is a schematic diagram of an ejector cycle device according to the nineteenth embodiment of the present invention. FIG. The features of the nineteenth embodiment, which is different from the eighteenth embodiment described above, include the compressor 11 that sucks and compresses the refrigerant; the cooler 13 that the heat of the compressor 11 discharged high-pressure refrigerant radiates; the ejector pump 17 that the Pressure of the refrigerant downstream of the cooler 13 reduces, thereby expanding the refrigerant, and the refrigerant from the first evaporator 18 sucks; the second evaporator 21 that's out of the ejector 17 escaping refrigerant vaporizes, thereby showing a cooling performance; the first evaporator 18 that through the ejector 17 to be sucked refrigerant evaporates, thereby showing a cooling performance, and one in series with the air passage of the second evaporator 21 arranged air duct and adjacent to the second evaporator 21 is arranged in such a way that the second evaporator 21 is arranged upstream of him; the tire removal element 121 including the first and second evaporators 18 . 21 heats up to the first and the second evaporator 18 . 21 remove adherent hoop; an evaporator temperature sensor 123 (second evaporator temperature sensor), which is the temperature of the second evaporator 21 detected; and the ECU 25 , The ECU 25 controls the frost removal process for heating the first and second evaporators 18 . 21 thereby to remove the frost thereon, and ends the frost removal operation by means of the frost removal member 121 when passing through the second evaporator temperature sensor 123 detected temperature of the second evaporator 21 reaches the predetermined temperature T.

In the present embodiment, in which the second evaporator 21 is located on the air upstream side, where the frost is easily separated, is the second evaporator temperature sensor 123 on the upstream side of the second evaporator 21 arranged. Accordingly, the first and second evaporators become 18 . 21 heated until the temperature of the upstream air side of the second evaporator 21 On the air upstream side, where the frost is easily adhered, becomes T or higher at the predetermined temperature, so that it is possible to reliably remove the frost without frost on the first and second evaporators 18 . 21 to leave. Therefore, it is possible to prevent a drop in the cooling performance caused by that at the first and second evaporators 18 . 21 adhering and deposited on the mature is caused.

Further, when the frost removal operation of the second evaporator 21 At the upstream side of the airflow and at which the frost is easily adhered, the frost removal operation with the frost removal member is finished 121 stopped. Therefore, it is possible to eliminate excessive heating and limit a temperature rise of the space R to be cooled and the amount of power consumption required for removing the frost to a minimum.

Twentieth Embodiment

33 FIG. 12 is a schematic diagram of an ejector cycle device in the twentieth embodiment of the present invention. FIG. In the twentieth embodiment, the ejector cycle device includes the compressor 11 that sucks and compresses the refrigerant; the cooler 13 that the heat of the compressor 11 discharged high-pressure refrigerant radiates; the ejector pump 17 that the pressure of the refrigerant downstream of the radiator 13 reduces, thereby expanding the refrigerant, and the refrigerant from the first evaporator 18 sucks; the second evaporator 21 that's out of the ejector 17 escaping refrigerant vaporizes, thereby showing a cooling performance; the first evaporator 18 that enters the refrigerant suction port of the ejector 17 to be sucked refrigerant evaporated, thereby showing a cooling performance; a memory 118 , the refrigerant downstream of the second evaporator 21 is arranged; the tire removal element 121 including the first and second evaporators 18 . 21 heats to the at the first and the second evaporator 18 . 21 remove adherent hoop; a storage temperature sensor 124 that the temperature of the store 118 detected; and the ECU 25 , The ECU 25 performs a defrosting operation of the first and the evaporator 18 . 21 to thereby remove the hoop and terminate the hoop removal operation with the hoop removing member 121 when passing through the store temperature sensor 124 detected temperature of the outer wall of the memory 118 reaches a predetermined temperature T.

In the present embodiment, the memory 118 downstream of the second evaporator 21 arranged to respond to load fluctuations, and the storage tank temperature sensor 124 is at the store 118 in which the liquid low-temperature refrigerant collects and to which the frost easily adheres.

According to this embodiment, the first and second evaporators become 18 . 21 heated until the outside wall temperature of the store 118 where the frost is easily adhered, becomes T or higher at the predetermined temperature, whereby it is possible to reliably remove frost without frost on the first and second evaporators 18 . 21 to leave. Therefore, it is possible to prevent a drop in the cooling performance caused by that at the first and second evaporators 18 . 21 adhering and deposited on the mature is caused.

In addition, when the tire removal operation of the memory 118 at which the frost is easily adhered is finished, the frost removal process through the frost removal element 121 stopped. Therefore, it can make it possible to eliminate excessive heating and to limit a temperature increase of the space R to be cooled and an increase in the amount of energy required to remove the frost to a minimum.

(Twenty-First Embodiment)

34 FIG. 12 is a schematic diagram of an ejector cycle device in the twenty-first embodiment of the present invention. FIG. 35 FIG. 15 is a time chart of a frost removal control in the ejector cycle device in FIG 34 , This embodiment, different from the above eighteenth to twentieth embodiments, will now be described. In the twenty-first embodiment, a first evaporator temperature sensor 122 , a second evaporator temperature sensor 123 and the storage temperature sensor 124 as several temperature sensors 122 to 124 provided, which are attached to several sections. In addition, the ECU performs 25 heating the first and second evaporators 18 . 21 to remove the hoop thereon and terminates the hoop removing operation by the hoop removing member 121 if all through the multiple temperature sensors 122 to 124 detected temperatures reach the predetermined temperature T or more.

In this embodiment, the plurality of temperature sensors 122 to 124 attached to the above multiple sections with the easily deposited on the hoop, because the degree of adhesion of the hoop varies according to the operating conditions in the above-mentioned sections, where the frost is easily adhered.

According to this embodiment, the ECU performs 25 heating the first and second evaporators 18 . 21 through, until all of the multiple sections attached multiple temperature sensors 122 to 124 reach the predetermined temperature T or more. Therefore, it is possible to reliably remove the frost without ripening on the first and second evaporators 18 . 21 and therefore to prevent a drop in the cooling capacity caused by the at the first and the second evaporator 18 . 21 adhering and deposited on the mature is caused.

In addition, when the frost removal operation is terminated at the plural portions where frost is easily adhered, heating by the frost removal member is stopped 121 stopped. Therefore, it is possible to eliminate excessive heating and to effectively limit an increase in the temperature of the space R to be cooled and the amount of power consumption required to remove the frost.

Twenty-Second Embodiment

36 FIG. 12 is a schematic diagram of an ejector cycle device in the twenty-second embodiment of the present invention. FIG. 37 FIG. 15 is a time chart of a frost removal control in the ejector cycle device in FIG 36 , This embodiment, which differs from the above embodiments, will now be described. In the twenty-second embodiment, the frost removal member includes a refrigerant stream downstream of the radiator 13 arranged three-way valve (channel switching element 120 ) and a Heißgaszuführkanal 119 for supplying the refrigerant from the three-way valve 120 to the refrigerant upstream side of the first evaporator 18 , Next switches the ECU 25 the refrigerant flow through the three-way valve 120 to the hot gas supply channel 119 in a state when the compressor 11 is in operation, and performs the heating of the first and the second evaporator 18 . 21 by means of the high-temperature refrigerant.

That is, in a normal operation ( 1 ) is the refrigerant from the radiator 13 to the nozzle 17a the ejector pump 17 initiated. In contrast, in the Reifentfernungsbetrieb ( 2 ) of the first and second evaporators 18 . 21 the refrigerant from the radiator 13 through the hot gas supply channel 119 ,

According to this embodiment, the frost removal operation (defrosting operation) of the first and second evaporators 18 . 21 be carried out without using a heating element. Therefore, it is possible to reduce the size of the frost removal member and thereby reduce the cost.

(Twenty-third Embodiment)

38 FIG. 12 is a schematic diagram of an ejector cycle device according to the twenty-third embodiment. FIG. The twenty-third embodiment differs from the ejector cycle devices of the above-described eighteenth to twenty-second embodiments in that a refrigerant branch passage 19 from the refrigerant circulation passage to a liquid refrigerant storage portion of the storage 118 branches. Also in this case, this ejector cycle device can also produce the same effect as the above eighteenth to twenty-second embodiments.

Twenty-fourth Embodiment

Hereinafter, the twenty-fourth embodiment of the present invention will be described in FIG Detail using 39A and 39B described. 39A FIG. 12 is a schematic diagram of an ejector cycle device of the twenty-fourth embodiment of the present invention; and FIG 39B is a side view from a through an arrow A in 39A shown direction. In this embodiment, a hydrocarbon (CH) -based refrigerant is used as the refrigerant.

In this embodiment, the compressor 11 and the electrically driven fan 18 is electrically controlled by a control signal from the electric control unit (control unit, hereinafter referred to as ECU). Next, the structure according to the twenty-fourth embodiment will be described. Several tire removal elements 121 for heating the first and second evaporators 18 . 21 are arranged to be connected to the first and the second evaporator 18 . 21 remove adherent hoop. For example, as tire removal elements 121 electric heaters, such as non-contact glass tube heaters, upstream of the first and second evaporators 18 . 21 and at a position between the first and second evaporators 18 . 21 arranged in the air channel of a cooling unit (not shown) combined in one unit.

In addition, in this embodiment, the first evaporator 18 having a low evaporation temperature and therefore easily precipitates frost with an evaporator temperature sensor (evaporator temperature detecting element) 122 , such as a thermistor, for detecting the temperature. For example, this evaporator temperature sensor 122 arranged in a section of a temperature rise in the first and second evaporator 18 . 21 most resists.

The measuring signal of the evaporator temperature sensor 122 becomes the ECU 25 and when the frost removal control of melting and removing at the first and second evaporators 18 . 21 adhered and deposited on the frost, the Reifentfernungselement 121 switched on and by an output signal from the ECU 25 controlled.

In this embodiment, the cooling process and the frost removal process may be similar to the control operation of FIG 29 to 31 be performed in the eighteenth embodiment.

In this embodiment, the ejector cycle device includes the compressor 11 that sucks and compresses the refrigerant; the cooler 13 that the heat of the compressor 11 discharged high-pressure refrigerant radiates; the ejector pump 17 that the pressure of the refrigerant downstream of the radiator 13 reduces to thereby expand the refrigerant, and draws in the refrigerant; the second evaporator 21 that's out of the ejector 17 escaping refrigerant vaporizes, thereby showing a cooling performance; the refrigerant branch channel 19 which is from the cooling circuit to the compressor 11 , the cooler 13 , the ejector pump 17 and the second evaporator 21 branches off and the ejector 17 Can suck in refrigerant; the first evaporator 18 which is in the refrigerant branch channel 19 is arranged and the refrigerant evaporates to thereby show a cooling performance; the Reifentfernungselemente 121 containing the first and the second evaporator 18 . 21 heat to the first and second evaporators 18 . 21 remove adherent hoop; and the ECU 25 that the tire removal element 121 heating the first and second evaporators 18 . 21 perform to thereby remove the hoop.

According to this embodiment, the frost removal member 121 arranged so that it is both the first evaporator 18 having a low evaporation temperature, as well as the second evaporator 21 The airflow on the first evaporator heats. Therefore, even at a low set heating temperature, it is possible to reliably remove the frost without leaving frost, and therefore to prevent a drop in the cooling performance caused by that at the first and second evaporators 18 . 21 adherent and deposited on the rim would cause.

In addition, the Reifentfernungselemente 121 each upstream of the first and second evaporators 18 . 21 arranged. According to this embodiment, flows through the Reifentfernungselement 121 generated heat downstream and therefore, the first and the second evaporator 18 . 21 be heated with high efficiency. In this embodiment, the Reifentfernungselemente 121 built from electrical heating elements.

Next leads the ECU 25 heating the first and second evaporators 18 . 21 using the electric heating elements 121 in a state through when the compressor 11 is switched off. Accordingly, the first and second evaporators 18 . 21 through the electric heating elements 121 be heated in a state when the compressor 11 is switched off. Therefore, it is possible to finish the removal of frost within a short time. Besides, the refrigerant in this embodiment is a cold Hydrocarbon-based agent of a highly flammable refrigerant. The highly flammable refrigerant contains a hydrocarbon-based refrigerant (refrigerant substance with hydrogen and carbon and existing in nature and the like), and this hydrocarbon-based refrigerant contains R600a with isobutene and R290 with propane.

For example, R600a catches fire at a temperature of about 460 ° C to 494 ° C. However, if a glass tube heating element as an electric heating element 121 is used, the ignition temperature is reduced to a temperature of about 200 ° C to 300 ° C. If a pipe heater as an electric heating element 121 is used for heating an object in contact with the object, the ignition temperature is reduced to a temperature of about 100 ° C. Therefore, R600a can be used as a highly flammable refrigerant.

Twenty-fifth Embodiment

40A FIG. 12 is a schematic diagram of an ejector cycle device of the twenty-fifth embodiment of the present invention; and FIG 40B is a side view from a through an arrow B in 40A shown direction. This embodiment is with the ECU 25 provided the heating of the first and the second evaporator 18 . 21 using the frost removal element 121 performs. In this embodiment, an electric heating element 121 as a Reifentfernungselement 121 used, and this is in contact with both the first and the second evaporator 18 . 21 arranged. For example, the electric heating element 121 a pipe heating element of the contact type.

In this embodiment, the electric heating element 121 arranged so that it is both the first evaporator 18 which has a low evaporation temperature and therefore easily develops frost, as well as the second evaporator 21 which is located upstream and therefore easily deposits frost on its upstream side and easily causes clogging in contact. Accordingly, it is even at a low set heating temperature of the electric heating element 121 it is possible to reliably remove the frost without leaving frost, and thereby prevent a drop in the cooling performance caused by that at the first and second evaporators 18 . 21 adherent and deposited on the rim would cause.

In the 40A . 40B The illustrated ejector cycle device differs from the ejector cycle device of the above twenty-fourth embodiment in that the refrigerant branch passage 19 from the refrigerant circulation passage from the liquid refrigerant storage portion of the storage 118 branches. The construction of the heating element 121 can also be used in this type of Ejektorpumpenkreisvorrichtung for performing the Reifentfernungsvorgangs. In addition, the electric heating element 121 on both sides of the first and second evaporators 18 . 21 can be arranged or can only on one of both sides of the first and the second evaporator 18 . 21 to be ordered.

Twenty-sixth Embodiment

41A and 41B FIG. 12 are schematic diagrams of the arrangement example of the first and second evaporators. FIG 18 . 21 in the twenty-sixth embodiment of the present invention, wherein 41A a front view and 41B is a side view.

According to this embodiment, an electric heating element 121 provided that both the first evaporator 18 , which is of low evaporation temperature and therefore easily develops frost, as well as the second evaporator 21 which is arranged upstream of the airflow and on the upstream side of which frost is easily separated and which can easily cause clogging. Therefore, even with a low set heating temperature, it is possible to reliably remove the frost without leaving frost. In addition, it is possible to prevent a drop in the cooling performance caused by that at the first and second evaporators 18 . 21 adhering and deposited on the mature is caused.

In addition, the frost by means of an electric heating element 121 having the same size as a conventional single evaporator, so that it is possible to effectively use an installation space and effectively remove the frost from the plural evaporators.

Further, one of the first and second evaporators 18 . 21 with the electric heating element 121 and the other of them is provided with an element that easily absorbs radiant heat, for example, with an aluminum plate (radiant heat-absorbing member) 128 , which is painted black, and the radiant heat from the electric heating element 121 gets to the aluminum plate 128 issued.

According to this embodiment, the electric heating element 121 for heating one of the first and second evaporators 18 . 21 provided, and the other of them is over the aluminum plate 128 for absorbing radiant heat from the electric heating element ge heated. Therefore, even at a low set heating temperature, it is possible to reliably remove the frost without leaving frost, and to prevent a drop in the cooling performance caused by any one of the first and second evaporators 18 . 21 adherent and deposited on the rim would cause. It is also recommended that the surface itself of the other first evaporator 18 coated with a black paint so as to provide the surface with a feature of easily absorbing radiant heat.

(XXVII Embodiment)

42A . 42B FIG. 12 are schematic views of the arrangement example of the first and second evaporators. FIG 18 . 21 and the electric heating element 121 in the twenty-seventh embodiment of the present invention, wherein 42A a front view and 42B is a side view. In this embodiment, the electric heating element 121 at one of the first and second evaporators 18 . 21 mounted, and the heat of the electric heating element 121 is delivered to the other evaporator by convection.

According to this embodiment, the electric heating element 121 for heating one of the first and second evaporators 18 . 21 provided, and the other evaporator is by convection of the electric heating element 121 heated. Therefore, even at a low set heating temperature, it is possible to reliably remove frost without leaving frost. In addition, convection is forced convection by the electrically driven blower (air blower). 18A used. Accordingly, it is possible to perform the convection effectively and reliably.

(Twenty-Eighth Embodiment)

43A and 43B FIG. 12 are schematic diagrams of the arrangement example of the first and second evaporators. FIG 18 . 21 and the frost removal member 121 in the twenty-eighth embodiment of the present invention. 43A shows a normal operation, and 43B shows a Reifentfernungsvorgang (defrosting operation). The difference between this embodiment and the above embodiments is that the first and second evaporators 18 . 21 are arranged in the up / down direction and that the electric heating element 121 in a lower position of the evaporators 18 . 21 is arranged so that a natural convection is used as convection. Accordingly, it is also possible to effectively use the natural convection.

44A and 44B . 45A and 45B such as 46A and 46B FIG. 12 are schematic diagrams of the arrangement examples of the first and second evaporators. FIG 18 . 21 and the electric heating element 121 , In the twenty-fourth embodiment, the electric heating element 121 airflow on the first and second evaporators 18 . 21 and at a position between the combined first and second evaporators 18 . 21 arranged. As in 44A and 44B however, the electric heating element may be shown 121 also upstream and downstream of the combined first and second evaporators 18 . 21 be positioned.

Although a case has been described in the twenty-fourth embodiment in which the first and second evaporators 18 . 21 are integrated in a unit, can further, as in 45A and 45B shown, the first evaporator 18 and the second evaporator 21 also be separate units. In addition, the twenty-fifth embodiment is the electric heating element 121 provided with the sides of both the second evaporator 21 as well as the first evaporator 18 is in contact and this heats. As in 46A and 46B shown, the electric heating element 121 but also between the second evaporator 21 and the first evaporator 18 be positioned in such a way that it is in contact with both of them and heats them.

(Twenty-Ninth Embodiment)

The construction of the twenty-ninth embodiment will be described by using 47A and 47B described. First, the first and second evaporators 18 . 21 connected in such a way that heat through an element 128 can be transmitted to transfer heat. In particular, parts of heat transfer ribs ( 128 ) of the first and second evaporators 18 . 21 together as an element 128 integrated to transfer heat.

In an in 47A illustrated embodiment, a reference numeral 128a a heat exchange fin, the first and the second evaporator 18 . 21 is common, and 128b shows a heat exchange fin for the second evaporator 21 , and 128c denotes a heat exchange fin for the first evaporator 18 , The electric heating element 121 as the frost removal element, the first and second evaporators 18 . 21 heats, so on the first and the second evaporator 18 . 21 adhere removing the frost is at the surface of the air duct upstream of the integrated first and second evaporators 18 . 21 fastened in such a way that it is integrated with the ribs 128a in contact.

In this embodiment, an evaporator temperature sensor (evaporator temperature detecting element) is 122 , such as a thermistor, for detecting the temperature at the first evaporator 18 attached, which has a low evaporation temperature and on which frost easily separates. Preferably, this evaporator temperature sensor 122 attached to a portion of the temperature rise in the integrated first and second evaporators 18 . 21 most resists. The measuring signal of the evaporator temperature sensor 122 becomes the ECU 25 entered. When the frost removal control for melting at the first and the second evaporator 18 . 21 adhered and deposited on the frost to remove the hoop, is the electric heating element 121 switched on and by an output signal from the ECU 25 controlled.

Next, the features and effects of this embodiment will be described. First, the first and second evaporators 18 . 21 connected together in such a way that they heat through integrated ribs (elements for transferring heat) 128a transfer. The electric heating element 121 heats the first and the second evaporator 18 . 21 so as to remove the frost adhering to this and the ECU 25 performs heating of the first and second evaporators 18 . 21 using the electric heating element 121 to thereby remove the hoop.

Accordingly, for example, even if only one electric heating element 121 air upstream and the upstream surface of the second evaporator 21 In order to thereby remove frost, the first evaporator arranged downstream of the air heats 18 through the second evaporator 21 over the integrated ribs 128a transferred heat heated, thereby removing frost from it.

In this way it is possible to use both the first evaporator 18 which has a low evaporation temperature and therefore easily develops frost, as well as the second evaporator 21 , which is arranged on the air flow, using an electric heating element 121 to heat and therefore to remove the frost in a short time with high efficiency. In addition, even at the low set heating temperature, it is possible to remove the frost from the first and second evaporators 18 . 21 reliably to remove without leaving frost, and therefore to prevent a drop in the cooling power that would be caused by the adhering to them and deposited on them mature. In addition, it is also possible to control the electric heating element 121 to simplify.

Furthermore, the integrated ribs 128a with the electric heating element 121 brought into contact. This makes it easy to heat from the integrated ribs 128a on the first evaporator 18 transferred to. Next is the amount of heat conduction of the integrated fins 128a determined in such a way that one through the first and the second evaporator 18 . 21 required cooling capacity is compatible with a required Reifentfernungsleistung them.

48 FIG. 12 is a graph of a change in cooling performance and a change in the tire removal power (defrosting power DP) relative to the heat conduction amount of the integrated fins 128a , When, at the time of a cooling operation, a difference in the evaporation temperature between the first and second evaporators 18 . 21 Heat is generated between them via the integrated ribs 128a transfer. Here, when the heat conduction amount is excessively large, the frost removal performance (defrosting power DP) is improved by heat transfer, but the liquid refrigerant of the first evaporator 18 , which is used for cooling air and has a low evaporation temperature, is for cooling the second evaporator 21 used. In this case, the cooling capacity (RC) is deteriorated.

In this way, it is preferable for improving the cooling capacity (RC), the first and the second evaporator 18 . 21 completely separate. However, if the heat conduction amount is excessively small, the heat at the time of removing frost can not be transmitted, and therefore the frost removal performance (defrosting power DP) is reduced by a large amount. In this way, the cooling capacity (RC) and the frost removal power (DP) are opposite to each other in terms of the heat conduction amount. In the evaporator of this embodiment, the heat conduction amount is determined in such a manner that the required cooling capacity (RC) is compatible with the required frost removal performance (DP). Regarding the amount of heat conduction through the integrated ribs 128a it is also possible to calculate the amount of heat transfer as a number of integrated ribs 128a or the like instead of the amount of heat conduction when the environmental conditions of the temperature and the amount of air in the evaporator are at the same levels.

Next, the heat exchange ribs 128 used as elements for transferring heat. These are part or all of the heat exchange ribs 128 containing the first and the second evaporator 18 . 21 form, which are integrated with each other, according to the above required amount of heat conduction. Accordingly, it is possible to construct the above construction without adding a new component, and therefore to reduce the cost.

In 47A and 47B is the second evaporator 21 with the first evaporator 18 in contact. However, it is also recommended that both evaporators 18 . 21 in their main bodies are separated from each other and only in the integrated ribs 128a integrated with each other. Furthermore, in 47A and 47B the integrated ribs 128a evenly arranged, but it is also advisable to respond to system-dependent frost formation caused by the design of the evaporator and the design of the air duct by the connection method, the number of connected parts and the arrangement of the integrated ribs 128a is caused.

In addition, these integrated ribs 128a for transferring heat from the second evaporator 21 on the first evaporator 18 used. Therefore, these integrated ribs can 128a within the scope of this feature in material, size and shape and molding process also from the other heat exchange ribs 128b . 128c be different and different from the sizes of the evaporators.

Thirtieth Embodiment

49A FIG. 12 is a schematic diagram of an ejector cycle device in the thirtieth embodiment of the present invention; and FIG 49B is a side view from a through an arrow B in 49A illustrated direction. In the thirtieth embodiment, a holding member 124 for holding the first and second evaporators 18 . 21 used as an element for transferring heat. In this embodiment, the holding element 124 for holding the first and second evaporators 18 . 21 is used as a heat transfer member according to the amount of the required heat conduction described above. Thereby, the above construction can be formed without adding a new component, and this can reduce the cost.

In the 49A The illustrated ejector cycle device differs from the ejector cycle device of the twenty-ninth embodiment in that the refrigerant branch passage 19 from the refrigerant circulation passage from the liquid refrigerant storage portion of the accumulator 118 branches. Next are the electric heating element 121 and the holding element 124 only on one side of the first and the second evaporator 18 . 21 attached, but can also be attached to both sides (see 49B ). In addition, the retaining element 124 openings 124a for passing air through convection (see 49A ).

(XXXI Embodiment)

50A and 50B FIG. 12 are schematic diagrams of the arrangement example of the first and second evaporators. FIG 18 . 21 and the electric heating element 121 in the thirty-first embodiment. Here is 50A a front view and 50B a side view. The thirty-first embodiment differs from the above respective embodiments in that side plates 125 at both ends of the first and second evaporators 18 . 21 are designed to be used as elements for transferring heat. In this embodiment, the side plates become 25 at both ends of the first and second evaporators 18 . 21 are used as elements for transferring heat according to the amount of the required heat conduction described above. This can form the above construction even without adding a new component and therefore reduce costs.

(XXXII Embodiment)

51A and 51B FIG. 12 are schematic diagrams of the arrangement example of the first and second evaporators. FIG 18 . 21 and the electric heating element 121 in the thirty-second embodiment. Here is 51A a front view and 51B a side view. The thirty-second embodiment differs from the above respective embodiments in that heat transfer members 126 as elements for transferring heat in the first and second evaporators 18 . 21 are formed. In this embodiment, the heat transfer plates (heat transfer elements) 126 with respect to the amount of the above-described required heat conduction in the first and second evaporators 18 . 21 educated.

(Further embodiments)

The present invention is not limited to the above embodiments, but may be variously modified as described below. For example, the above embodiments may be combined with each other. In addition, although the ejectors Circular device of the present invention is used in the above embodiments for a vehicle-mounted cooling device, the ejector cycle device is used not only for the refrigeration / cooling device and the air conditioning / air cooling device, but also as a vapor compression circuit, such as a heat pump unit for a water heater and a household refrigerator.

In addition, either a supercritical pressure circuit or a subcritical pressure circuit using a flon-based refrigerant, a hydrocarbon (HC) -based refrigerant, a carbon dioxide (CO ₂ ) -based refrigerant, may be used as the refrigerant. Herein, the term flon means a general term of an organic compound with fluorine, chlorine and hydrogen, and the flon is generally used as a refrigerant. The Flon-based refrigerant includes hydrogen, chlorine, fluorine and carbon (HCFC) based refrigerant as well as hydrogen, fluorine and carbon (HFC) based refrigerants.

Further, in the thirtieth embodiment, the memory 118 upstream of the compressor 11 arranged and only the vapor phase refrigerant is in the compressor 11 directed. However, it is also advisable to use a construction in which a vapor-liquid separator upstream of the second evaporator 21 is arranged and in the only liquid refrigerant in the second evaporator 21 can flow. In addition, it is also advisable to arrange a collecting vessel which separates the vapor and the liquid of the refrigerant, and only the liquid-phase refrigerant to the downstream side, downstream of the cooler 13 passes.

The compressor 11 may be a variable displacement compressor. Alternatively, it is also recommended that a compressor 11 is used with fixed displacement and that the operation of this compressor 11 is controlled with a fixed displacement according to an ON / OFF control by an electromagnetic switch to the ratio of the ON / OFF operation of the compressor 11 to thereby control the refrigerant discharge capacity of the compressor 11 to regulate. Next, if an electrically driven compressor as a compressor 11 is used, the refrigerant discharge capacity also by controlling the rotational speed of the electric driven compressor 11 to be controlled.

Also, for the ejector pump 17 a variable flow ejector pump is used. In this case, the opening area of the refrigerant passage of the nozzle portion 17a the ejector pump 17 be controlled so that the pressure of the nozzle section 17a discharged refrigerant and the flow rate of the sucked vapor-phase refrigerant based on the degree of superheat of the refrigerant at the outlet of the second evaporator 21 to be controlled.

Further, in the above embodiment, an example has been described in which a fixed throttle device 116 , such as a capillary tube, with a constant restriction orifice upstream of the first evaporator 18 is arranged. However, it is also advisable to use a variable throttle, which the flow rate of the refrigerant according to fluctuations in the heat load of the first evaporator 18 can vary. In addition, it is also advisable to use an element (eg, an expansion valve) that has a mechanism for detecting the degree of superheat at the outlet of the first evaporator 18 has and the restriction opening, such as the throttle device 116 , controls.

In addition, in the above first to seventeenth embodiments, the temperatures (internal temperatures) of the spaces to be cooled become 23 . 23a . 23b . 23c the respective evaporators 18 . 21 . 34 through the temperature sensors 24 . 24a . 24b and 24c detected. However, instead of these internal temperatures, temperatures related to the internal temperatures, such as surface temperature of the evaporator, may be detected.

While the Invention with reference to preferred embodiments thereof described it is self-evident that the invention is not limited to the preferred embodiments and constructions limited is. The invention is also intended to be various modifications and equivalent Cover arrangements. While the various elements of the preferred embodiments in different Combinations and configurations are shown which are preferred are lie as well other combinations and configurations including more, less or just a single element also within the scope of the Invention.

Claims (53)

Ejector cycle device, with a compressor ( 11 ), which sucks and compresses a refrigerant; a cooler ( 13 ), the heat of the compressor ( 11 ) emitted high-pressure refrigerant radiates; a downstream of the radiator ejector ( 17 ) for decompressing and expanding the refrigerant from the radiator, the ejectors pump a refrigerant suction port ( 17b ) for sucking the refrigerant by a high-speed refrigerant flow when the refrigerant is expanded, mixing the refrigerant sucked from the refrigerant suction port with the high-speed refrigerant stream, and braking the mixed refrigerant flow, thereby increasing the pressure of the mixed refrigerant flow; an evaporator ( 18 ) disposed in a refrigerant branch passage connected to the refrigerant suction port; an opening / closing element ( 16 . 17e ), which opens and closes a refrigerant flow and can prevent a flow of the refrigerant into the evaporator; and a control unit ( 25 ), which brings the opening / closing element in a closed period in a period for which the operation of the compressor is stopped. The ejector cycle device according to claim 1, wherein the evaporator connected to the refrigerant suction port is used as a first evaporator (FIG. 18 ), wherein the ejector cycle device further comprises a second evaporator (12) disposed downstream of the ejector. 24 ) having. An ejector cycle device according to claim 2, wherein which is the first evaporator and the second evaporator are arranged to cool one Room to cool. An ejector cycle device according to claim 2, wherein which is the first evaporator and the second evaporator are arranged to cool separate rooms to be cooled. An ejector cycle device according to any one of claims 1 to 4, further comprising a temperature sensing element (16). 24 . 24a . 24b ) for detecting a temperature with respect to a temperature of a space to be cooled with the evaporator, wherein the control unit intermittently controls the operation of the compressor based on the temperature detected by the temperature detection element. An ejector cycle device according to any one of claims 1 to 5, in which the refrigerant branch channel branches off at a branch point upstream of the ejector and connected to the refrigerant suction port is. An ejector cycle device according to claim 6, wherein said opening / closing member is located upstream of said branch point (Fig. 2 ) arranged opening / closing valve ( 16 ). An ejector cycle device according to claim 6, wherein said opening / closing member has a three-way valve (13) disposed at said branching point (Z). 16 ). An ejector cycle device according to any one of claims 1 to 6, wherein the opening / closing member includes an opening / closing valve (16) disposed upstream of the evaporator in the refrigerant branch passage (16). 16 ). An ejector cycle device according to any one of claims 1 to 5, wherein said opening / closing member includes a passage opening / closing mechanism (16) disposed in said ejector pump itself ( 17e ). An ejector cycle device according to any one of claims 1 to 10, in which the control unit, the opening / closing element in the period, for the compressor is off, from the closed state to an open state controls and then starts the operation of the compressor again. An ejector cycle device according to any one of claims 1 to 5, wherein said opening / closing member has an opening / closing valve (12) disposed upstream of said evaporator connected to said refrigerant suction port (10). 16 ) and a passage opening / closing mechanism (FIG. 17e ) contains; and the control unit the opening / closing valve ( 16 ) in the period for which the compressor is turned off, from a closed state to an open state, thereby balancing the pressure in a refrigerant cycle, and then resetting the port opening / closing mechanism to an open state and then resuming the operation of the compressor starts. An ejector cycle device according to any one of claims 1 to 12, in which the control unit, the opening / closing element before switching off the compressor from an open state to a closed state controls and the compressor for a certain time (t4) in a state when the opening / closing element is closed, keeps in an operating state and then the compressor off. An ejector cycle device according to any one of claims 1 to 13, further comprising a throttle mechanism ( 15 . 20 . 20a ) disposed upstream of the opening / closing member and reducing the pressure of the refrigerant upstream of the opening / closing member in such a manner that the refrigerant is put into two phases of a vapor and a liquid. An ejector cycle device according to claim 1, wherein the ejector and the orifice tion / closing valve are combined together at least as an integrated unit. Ejector cycle device, with a compressor ( 11 ), which sucks and compresses a refrigerant; a cooler ( 13 ), which radiates heat of the high-pressure refrigerant discharged from the compressor; an ejector pump ( 17 ) having a nozzle section ( 17a ) for reducing the pressure of the refrigerant downstream of the radiator to expand the refrigerant, and drawing the refrigerant out of the nozzle portion by a jet flow of the refrigerant; a first evaporator ( 18 ) evaporating the refrigerant to be sucked into the refrigerant suction port of the ejector, so as to have a cooling capacity; a second evaporator ( 21 ) that vaporizes the refrigerant discharged from the ejector to have a cooling performance; a tire removal element ( 119 . 120 . 121 ) heating the first and second evaporators so as to perform a frost removal operation in which frost adhering to the first and second evaporators is removed; an evaporator temperature sensing element ( 122 . 123 ), the temperature of at least one of the first evaporator ( 18 ) and the second evaporator ( 21 ) detected; and a control unit ( 251 controlling the frost removing member to heat the first and second evaporators and perform the frost removal operation when the temperature detected by the evaporator temperature detecting element reaches a predetermined temperature. An ejector cycle device according to claim 16, wherein said evaporator temperature sensing element (16) 122 ) is arranged to the temperature of the first evaporator ( 18 ) capture; and the control unit controls the frost removal member to perform the frost removal operation when the temperature of the first evaporator detected by the evaporator temperature detection element reaches a predetermined temperature. An ejector cycle device according to claim 16, wherein said evaporator temperature sensing element (16) 123 ) is arranged to detect the temperature of the second evaporator; and the control unit controls the frost removal member to perform the frost removal operation when the temperature of the second evaporator detected by the evaporator temperature detection element reaches a predetermined temperature. An ejector cycle device according to claim 16, further comprising a memory ( 118 ), the refrigerant downstream of the second evaporator ( 21 ) is arranged; and a storage temperature sensing element ( 124 ), which detects a temperature of the memory, wherein the evaporator temperature detection element comprises a first evaporator temperature sensor ( 122 ) arranged to detect a temperature of the first evaporator, and a second evaporator temperature sensor ( 123 ) arranged to detect a temperature of the second evaporator; and the control unit controls the frost removal element to perform the frost removal operation when a temperature detected by any one of the storage temperature detection element and the first and second evaporator temperature sensors reaches a predetermined temperature or more. An ejector cycle device according to any one of claims 16 to 19, wherein the Reifentfernungselement airflow on the first and the second evaporator is arranged. An ejector cycle device according to any one of claims 16 to 19, wherein the frost removal element comprises an electrical heating element ( 121 ) owns. An ejector cycle device according to claim 21, in which the control unit performs the tire removal operation of the first and the second evaporator in a state in the compressor is switched off. An ejector cycle apparatus as claimed in any one of claims 16 to 20, wherein the frost removal member comprises channel switching means (12) disposed downstream of the radiator. 120 ) and a Heißgaszuführkanal ( 119 ), through which a high-temperature refrigerant is passed from the channel switching means to a refrigerant upstream side of the second evaporator; and the control unit controls the channel switching means to switch a refrigerant passage to the hot gas supply passage in a state in which the compressor is in operation, and performs the frost removing operation of the first and second evaporators using the high-temperature refrigerant. An ejector cycle device according to any one of claims 16 to 23, in which the control unit corresponding to the predetermined temperature an outside air temperature varied. Ejektorpumpenkreisvorrichtung, with a compressor ( 11 ), which sucks and compresses a refrigerant; a cooler ( 13 ), which radiates heat of the high-pressure refrigerant discharged from the compressor; an ejector pump ( 17 ) having a nozzle section ( 17a ) for reducing the pressure of the refrigerant downstream of the radiator to expand the refrigerant, and drawing the refrigerant out of the nozzle portion by a jet flow of the refrigerant; a first evaporator ( 18 ) evaporating the refrigerant to be sucked into a refrigerant suction port of the ejector to have a cooling capacity; a second evaporator ( 21 ) which vaporizes the refrigerant discharged from the ejector to have a cooling capacity; a memory ( 118 ) disposed downstream of the second evaporator; a tire removal element ( 119 . 120 . 121 ) heating the first and second evaporators so as to perform a frost removing operation in which frost adhering to the first and second evaporators is removed; a storage temperature sensing element ( 124 ) that detects a temperature of the memory; and a control unit ( 25 ) controlling the frost removal member to heat the first and second evaporators and perform the frost removing operation when a temperature of an outer wall of the accumulator detected by the accumulator temperature detecting element reaches a predetermined temperature. Ejector cycle device according to claim 25, wherein the frost removal element is airflow on the first and of the second evaporator is arranged. An ejector cycle device according to claim 25 or 26, wherein the frost removal element comprises an electrical heating element ( 121 ) having. Ejector cycle device according to claim 27, in which the control unit performs the tire removal operation of the first and the second evaporator in a state when the Compressor is switched off. An ejector cycle device according to claim 25, wherein the frost removal element comprises channel switching means (12) disposed downstream of the radiator. 120 ) and a Heißgaszuführkanal ( 119 ), by which the high-temperature refrigerant is supplied from the channel switching means to a refrigerant upstream side of the second evaporator; and the control unit controls the passage switching means in a state when the compressor is in operation to switch a refrigerant passage to the hot gas supply passage, and performs the tire removing operation of the first and second evaporators using the high-temperature refrigerant. An ejector cycle device according to any one of claims 25 to 29, in which the control unit corresponding to the predetermined temperature an outside air temperature varied. An ejector cycle device according to any one of claims 16 to 30, wherein the Reifentfernungselement of several heating sections is constructed; and the control unit the first and the second Evaporator controls to the Reifentfernungsvorgang the first and the second evaporator. An ejector cycle device according to any one of claims 16 to 30, in which the tire removal member both the first and also contacted the second evaporator to the first and the to heat the second evaporator in the Reifentfernungsvorgang. An ejector cycle device according to any one of claims 16 to 30, in which the Reifel removal element is arranged so that in the tire removal process, both the first and the second Evaporator heats. Ejector cycle device, with a compressor ( 11 ), which sucks and compresses a refrigerant; a cooler ( 13 ), which radiates heat of the high-pressure refrigerant discharged from the compressor; an ejector pump ( 17 ) having a nozzle section ( 17a ) for reducing the pressure of the refrigerant downstream of the radiator to expand the refrigerant, and drawing the refrigerant out of the nozzle portion by a jet flow of the refrigerant; a first evaporator ( 21 ) evaporating the refrigerant discharged from the ejector; a refrigerant branch channel ( 19 ) branched from a refrigeration cycle including the compressor, the radiator, the ejector and the first evaporator, and refrigerant into a refrigerant suction port (FIG. 17b ) introduces the ejector pump; a second evaporator ( 18 ) disposed in the refrigerant branch passage and vaporizing the refrigerant; and a tire removal element ( 121 ) arranged to heat the first and second evaporators so as to perform a frost removing operation in which frost adhering to the first and second evaporators is removed; and a control unit ( 25 ) which controls the frost removal member to perform the frost removal operation of the first and second evaporators. An ejector cycle apparatus according to claim 34, wherein said frost removal member is comprised of a plurality of heating sections (16). 121 ) for heating the first and second evaporators in the frost removal process. An ejector cycle device according to claim 34 or 35, wherein the Reifentfernungselement airflow on each of the is positioned first and second evaporator. An ejector cycle device according to claim 34, in which the tire removal element is positioned so that it contacts both the first and second evaporators. An ejector cycle device according to claim 34, in which the tire removal element is positioned so that It heats both the first and the second evaporator. An ejector cycle apparatus according to claim 34, wherein said frost removal member is provided on one side of said first and second evaporators, further comprising a radiant heat absorbing member (16) provided on the other one of said first and second evaporators (Figs. 128 ), so that radiant heat is transported from the frost removal member to the radiant heat absorbing member. An ejector cycle device according to claim 34, wherein the frost removal element is on one side of the first and the second evaporator, so that the heat from the frost removal element to the other of the first and the second evaporator by convection is transported. Ejector cycle device according to claim 40, further comprising an air blowing unit positioned so that she performs the convection. Ejector cycle device according to claim 40, in which the first and the second evaporator in a vertical Direction are arranged and the Reifentfernungselement at a lower Position of the first and second evaporator arranged is to perform a natural convection in the Reifentfernungsvorgang. An ejector cycle device according to any one of claims 34 to 42, wherein the frost removal element comprises an electrical heating element (16). 121 ) having. An ejector cycle device according to any one of claims 34 to 43, in which the control unit the Reifentfernungsvorgang the first of the second evaporator by the frost removal member in a state performs when the compressor is off. An ejector cycle device according to claim 34, at which the refrigerant a flammable refrigerant is. An ejector cycle device according to any one of claims 16 to 45, further comprising a heat conducting element ( 124 - 126 . 128 ) connecting the first evaporator and the second evaporator to transfer heat between the first evaporator and the second evaporator. Ejector cycle device, with a compressor ( 11 ), which sucks and compresses a refrigerant; a cooler ( 13 ), which radiates heat of the high-pressure refrigerant discharged from the compressor; an ejector pump ( 17 ) having a nozzle section ( 17a ) for reducing the pressure of the refrigerant downstream of the radiator to expand the refrigerant, and drawing the refrigerant out of the nozzle portion by a jet flow of the refrigerant; a first evaporator ( 21 ) evaporating the refrigerant discharged from the ejector; a refrigerant branch channel ( 19 ) branched from a refrigeration cycle including the compressor, the radiator, the ejector and the first evaporator, and refrigerant into a refrigerant suction port (FIG. 17b ) introduces the ejector pump; a second evaporator ( 18 ) disposed in the refrigerant branch passage and vaporizing the refrigerant; a heat conduction element ( 124 - 126 . 128 ) connecting the first evaporator and the second evaporator to transfer heat between the first evaporator and the second evaporator; and a tire removal element ( 121 ) arranged to heat the first and second evaporators to remove frost adhering to the first and second evaporators. An ejector cycle device according to claim 47, in which the heat conduction element so is arranged to contact the Reifentfernungselement. An ejector cycle device according to claim 47 or 48, further comprising a control unit ( 25 ) for controlling a frost removal operation of the first and second evaporators, wherein a heat conduction amount of the heat conduction member is set in such a manner that a cooling power required by the first and second evaporators is compatible with a frost removal performance required in the frost removal operation of the first and second evaporators. An ejector cycle device according to any one of claims 47 to 49, wherein the heat conduction member is heat exchange fins (16). 128 ) disposed in the first and second evaporators. Ejector cycle device according to one of claims 47 to 49, in which the heat-conducting element is a retaining element ( 24 ) for holding the first and second evaporators. An ejector cycle device according to any one of claims 47 to 49, wherein the heat conduction member comprises side plates (Figs. 125 ) attached to lateral ends of the first and second evaporators. Ejector cycle device according to one of Claims 47 to 49, in which the heat-conducting element ( 126 ) is positioned in the first and second evaporators.