JP5118441B2

JP5118441B2 - Air conditioner for vehicles

Info

Publication number: JP5118441B2
Application number: JP2007285042A
Authority: JP
Inventors: 謙一鈴木
Original assignee: Sanden Corp
Current assignee: Sanden Holdings Corp
Priority date: 2007-11-01
Filing date: 2007-11-01
Publication date: 2013-01-16
Anticipated expiration: 2027-11-01
Also published as: JP2009107605A

Description

本発明は、車両用空調装置に関するものである。 The present invention relates to a vehicle dual air conditioning equipment.

従来、上記した車両用空調装置としては、例えば、外部制御信号により容量可変としたコンプレッサを有する蒸気圧縮式冷凍サイクルを備えた車両用空調装置がある。
この車両用空調装置では、制御対象をコンプレッサの容量制御としていて、容量制御信号演算手段によりコンプレッサの容量制御信号を演算し、この容量制御信号によりコンプレッサを制御して、制御目的、例えば、蒸気圧縮式冷凍サイクルを構成するエバポレータの出口空気温度を制御するようになっている（例えば、特許文献１参照）。
特開平３−６３４４１号公報 Conventionally, as the above-described vehicle air conditioner , for example, there is a vehicle air conditioner provided with a vapor compression refrigeration cycle having a compressor whose capacity is variable by an external control signal.
In this vehicle air conditioner, the control target is the capacity control of the compressor, the capacity control signal calculation means calculates the compressor capacity control signal, the compressor is controlled by this capacity control signal, and the control purpose, for example, vapor compression The outlet air temperature of the evaporator constituting the refrigeration cycle is controlled (see, for example, Patent Document 1).
JP-A-3-63441

しかしながら、上記した従来の車両用空調装置において、コンプレッサの容量制御を行うことでエバポレータの出口空気温度を制御することができるものの、すなわち、一つの制御対象を制御することで一つの目的に応じた制御を実現することができるものの、この制御系では、複数の目的に対応するような制御を行うことはできない。
この際、ある条件でのみ、複数の制御目的のうちの一つの制御目的を実現するように成すことは可能であるが、この手法では、目的を達成するうえで必要となる条件選定及び判定条件等を導き出すための工数が多大なものになってしまうという問題がある。 However, Oite the conventional vehicle air conditioning equipment as described above, although it is possible to control the outlet air temperature of the evaporator by performing capacity control of the compressor, i.e., one object of the by controlling one controlled object However, in this control system, control corresponding to a plurality of purposes cannot be performed.
At this time, it is possible to achieve one control objective among a plurality of control objectives only under a certain condition. However, in this method, condition selection and determination conditions necessary to achieve the objective are achieved. There is a problem that the man-hours for deriving etc. become enormous.

本発明は、上記した従来の課題に着目してなされたもので、例えば、圧縮機の容量制御を行うことで、蒸発器の出口空気温度及び高圧側冷媒圧力をそれぞれの目的に応じて的確に制御することが可能である車両用空調装置を提供することを目的としている。 The present invention has been made in view of the conventional problems described above, in example embodiment, by performing the capacity control of the compressor, correctly according evaporator outlet air temperature and high-pressure side refrigerant pressure in the respective purposes An object of the present invention is to provide a vehicle air-conditioning apparatus that can be controlled in a simple manner.

上記した目的を達成するために、本発明の請求項１に係る発明は、外部からの制御信号により任意に容量を可変として冷媒を圧送するべく作動する外部可変容量圧縮機と、この外部可変容量圧縮機から吐出する高温高圧の冷媒を冷却する放熱器と、前記冷媒の気化熱を利用して車室内に吹出す空気を冷却する蒸発器を具備した蒸気圧縮式冷凍サイクルと、この蒸気圧縮式冷凍サイクルにおける前記外部可変容量圧縮機の容量制御信号を演算する容量制御信号演算手段を備え、この容量制御信号演算手段により演算された前記外部可変容量圧縮機の容量制御信号により該外部可変容量圧縮機を制御して、前記蒸気圧縮式冷凍サイクルを制御する車両用空調装置において、前記容量制御信号演算手段を複数設け、これらの容量制御信号演算手段により演算された複数の容量制御信号の中で、前記外部可変容量圧縮機からの冷媒吐出量を最小にする容量制御信号により前記外部可変容量圧縮機を制御して、前記蒸気圧縮式冷凍サイクルを制御するものとした構成としたことを特徴としており、この車両用空調装置の構成を前述の従来の課題を解決するための手段としている。 To achieve the above object, the invention according to claim 1 of the present invention includes an external variable displacement compressor operates to pumps the refrigerant optionally capacity by a control signal from the outside as a variable, the external variable capacitance A vapor compression refrigeration cycle comprising a radiator that cools the high-temperature and high-pressure refrigerant discharged from the compressor, an evaporator that cools the air blown into the vehicle interior using the heat of vaporization of the refrigerant, and the vapor compression type Capacity control signal calculation means for calculating a capacity control signal of the external variable capacity compressor in the refrigeration cycle is provided, and the external variable capacity compression is performed by the capacity control signal of the external variable capacity compressor calculated by the capacity control signal calculation means. In a vehicle air conditioner that controls the vapor compression refrigeration cycle by controlling a machine, a plurality of the capacity control signal calculation means are provided, and the capacity control signal calculation means includes Among the plurality of calculated capacity control signals, the external variable capacity compressor is controlled by a capacity control signal that minimizes the refrigerant discharge amount from the external variable capacity compressor, and the vapor compression refrigeration cycle is controlled. It is characterized by having a configuration to be controlled, and the configuration of the vehicle air conditioner is used as a means for solving the above-described conventional problems.

本発明の請求項２に係る車両用空調装置は、前記蒸気圧縮式冷凍サイクルの高圧側の冷媒圧力を検知する高圧側冷媒圧力検知手段を備え、前記容量制御信号演算手段における演算の制御入力として、少なくとも前記高圧側冷媒圧力検知手段により検知される高圧側冷媒圧力を含んでいる構成とし、本発明の請求項３に係る車両用空調装置は、前記蒸気圧縮式冷凍サイクルの蒸発器の出口空気温度又は蒸発器の温度を検知する蒸発器温度検知手段を備え、前記容量制御信号演算手段における演算の制御入力として、少なくとも前記高圧側冷媒圧力検知手段により検知される高圧側冷媒圧力及び前記蒸発器温度検知手段により検知される蒸発器の出口空気温度を含んでいる構成としている。 A vehicle air conditioner according to claim 2 of the present invention includes a high-pressure side refrigerant pressure detection unit that detects a high-pressure side refrigerant pressure of the vapor compression refrigeration cycle, and serves as a calculation control input in the capacity control signal calculation unit. The vehicle air conditioner according to claim 3 of the present invention includes at least an outlet air of the evaporator of the vapor compression refrigeration cycle. Evaporator temperature detection means for detecting the temperature or the temperature of the evaporator, and as a control input for calculation in the capacity control signal calculation means, at least the high pressure refrigerant pressure detected by the high pressure refrigerant pressure detection means and the evaporator The outlet air temperature of the evaporator detected by the temperature detecting means is included.

本発明の請求項４に係る車両用空調装置は、前記蒸気圧縮式冷凍サイクルの蒸発器の目標温度を設定する蒸発器目標温度設定手段と、前記蒸発器の温度を目標温度に制御するのに必要となる容量制御信号を演算する蒸発器温度用容量制御信号演算手段と、前記蒸気圧縮式冷凍サイクルの高圧側冷媒圧力の目標値を設定する高圧側冷媒圧力目標値設定手段と、前記高圧側冷媒圧力を目標値に制御するのに必要となる容量制御信号を演算する高圧側冷媒圧力用容量制御信号演算手段を備え、前記蒸発器温度用容量制御信号演算手段において、前記蒸発器目標温度設定手段により設定される蒸発器の目標温度と、前記蒸発器温度検知手段により検知される蒸発器の出口空気温度とを参照して、前記蒸発器の温度制御用容量制御信号が演算されると共に、前記高圧側冷媒圧力用容量制御信号演算手段において、前記高圧側冷媒圧力目標値設定手段により設定される冷凍サイクルの高圧側冷媒圧力目標値と、前記高圧側冷媒圧力検知手段により検知される高圧側冷媒圧力とを参照して、前記高圧側冷媒圧力の制御用容量制御信号が演算され、前記蒸発器の温度制御用容量制御信号と、前記高圧側冷媒圧力の制御用容量制御信号とを比較して、前記外部可変容量圧縮機からの冷媒吐出量を最小にする容量制御信号により前記外部可変容量圧縮機を制御し、前記蒸気圧縮式冷凍サイクルを制御するものとした構成としている。 According to a fourth aspect of the present invention, there is provided a vehicle air conditioner for controlling an evaporator target temperature setting means for setting a target temperature of an evaporator of the vapor compression refrigeration cycle, and for controlling the temperature of the evaporator to a target temperature. Capacitor temperature capacity control signal calculating means for calculating a required capacity control signal, high pressure side refrigerant pressure target value setting means for setting a target value of the high pressure side refrigerant pressure of the vapor compression refrigeration cycle, and the high pressure side A high-pressure side refrigerant pressure capacity control signal calculating means for calculating a capacity control signal required to control the refrigerant pressure to a target value; and in the evaporator temperature capacity control signal calculating means, the evaporator target temperature setting The capacity control signal for temperature control of the evaporator is calculated with reference to the target temperature of the evaporator set by the means and the outlet air temperature of the evaporator detected by the evaporator temperature detecting means. In the high pressure side refrigerant pressure capacity control signal calculation means, the high pressure side refrigerant pressure target value of the refrigeration cycle set by the high pressure side refrigerant pressure target value setting means and the high pressure detected by the high pressure side refrigerant pressure detection means. The capacity control signal for controlling the high-pressure side refrigerant pressure is calculated with reference to the side refrigerant pressure, and the capacity control signal for controlling the temperature of the evaporator is compared with the capacity control signal for controlling the high-pressure side refrigerant pressure. The external variable capacity compressor is controlled by a capacity control signal that minimizes the refrigerant discharge amount from the external variable capacity compressor, and the vapor compression refrigeration cycle is controlled.

本発明の請求項５に係る車両用空調装置は、前記蒸発器温度検知手段により検知された蒸発器の出口空気温度又は蒸発器の温度が蒸発器目標温度に到達するための過渡状態における目標応答を算出し指定する蒸発器温度目標応答算出手段と、その目標応答における蒸発器温度目標応答値と前記蒸発器の出口空気温度又は蒸発器の温度との偏差を演算する蒸発器温度フィードバック制御入力演算手段と、前記蒸発温度目標応答算出手段により算出される目標応答における過渡特性を実現するのに必要なフィードフォワード制御入力を予測する蒸発器温度フィードフォワード制御入力予測手段と、前記高圧側冷媒圧力検知手段により検知された高圧側冷媒圧力と、前記高圧側冷媒圧力目標値設定手段により設定された高圧側冷媒圧力目標値とを参照して演算する高圧側冷媒圧力フィードバック制御入力演算手段と、前記高圧側冷媒圧力目標値設定手段により設定された高圧側冷媒圧力目標値を実現するのに必要なフィードフォワード制御入力を予測する高圧側冷媒圧力フィードフォワード制御入力予測手段を備え、前記蒸発器温度フィードバック制御入力演算手段において、前記蒸発器温度目標応答算出手段により算出される蒸発器温度目標応答値と、前記蒸発器温度検知手段により検知される蒸発器出口空気温度との偏差を参照して、蒸発器温度フィードバック制御入力が演算されると共に、前記蒸発器温度フィードフォワード制御入力予測手段において、蒸発器温度フィードフォワード制御入力が演算され、前記蒸発器温度用容量制御信号演算手段において、前記蒸発器温度フィードバック制御入力と、蒸発器温度フィードフォワード制御入力との和を参照して、前記蒸発器温度の容量制御信号が演算され、一方、前記高圧側冷媒圧力フィードバック制御入力演算手段において、前記高圧側冷媒圧力目標値設定手段により設定される高圧側冷媒圧力目標値と、前記高圧側冷媒圧力検知手段により検知される高圧側冷媒圧力とを参照して、高圧側冷媒圧力フィードバック制御入力が演算されると共に、前記高圧側冷媒圧力フィードフォワード制御入力予測手段において、高圧側冷媒圧力フィードフォワード制御入力が演算され、前記高圧側冷媒圧力用容量制御信号演算手段において、前記高圧側冷媒圧力フィードバック制御入力と、高圧側冷媒圧力フィードフォワード制御入力との和を参照して、高圧側冷媒圧力の容量制御信号が演算され、前記蒸発器の温度制御用容量制御信号と、前記高圧側冷媒圧力の制御用容量制御信号とを比較して、前記外部可変容量圧縮機からの冷媒吐出量を最小にする容量制御信号により前記外部可変容量圧縮機を制御し、前記蒸気圧縮式冷凍サイクルを制御するものとした構成としている。 The vehicle air conditioner according to claim 5 of the present invention is a target response in a transient state for the evaporator outlet air temperature or the evaporator temperature detected by the evaporator temperature detecting means to reach the evaporator target temperature. The evaporator temperature target response calculating means for calculating and specifying the value, and the evaporator temperature feedback control input calculation for calculating the deviation between the evaporator temperature target response value in the target response and the outlet air temperature of the evaporator or the evaporator temperature Means, an evaporator temperature feedforward control input predicting means for predicting a feedforward control input necessary for realizing a transient characteristic in the target response calculated by the evaporation temperature target response calculating means, and the high-pressure side refrigerant pressure detection And the high pressure side refrigerant pressure target value set by the high pressure side refrigerant pressure target value setting means. High-pressure side refrigerant pressure feedback control input calculation means for calculating the high-pressure side refrigerant pressure target value set by the high-pressure side refrigerant pressure target value setting means to predict the feedforward control input necessary to achieve the target value Refrigerant pressure feedforward control input predicting means, wherein the evaporator temperature feedback control input calculating means detects the evaporator temperature target response value calculated by the evaporator temperature target response calculating means and the evaporator temperature detecting means. The evaporator temperature feedback control input is calculated by referring to the deviation from the evaporator outlet air temperature, and the evaporator temperature feedforward control input predicting means calculates the evaporator temperature feedforward control input, In the evaporator temperature capacity control signal calculating means, the evaporator temperature fee is calculated. A capacity control signal of the evaporator temperature is calculated with reference to the sum of the back control input and the evaporator temperature feedforward control input. On the other hand, in the high pressure side refrigerant pressure feedback control input calculation means, the high pressure side refrigerant The high pressure side refrigerant pressure feedback control input is calculated with reference to the high pressure side refrigerant pressure target value set by the pressure target value setting means and the high pressure side refrigerant pressure detected by the high pressure side refrigerant pressure detecting means. The high-pressure side refrigerant pressure feedforward control input predicting means calculates a high-pressure side refrigerant pressure feedforward control input, and the high-pressure side refrigerant pressure capacity control signal calculating means calculates the high-pressure side refrigerant pressure feedback control input, Refer to the sum of the refrigerant pressure feed-forward control input and the capacity control signal for the high-pressure refrigerant pressure. A capacity that minimizes the refrigerant discharge amount from the external variable capacity compressor by comparing the capacity control signal for temperature control of the evaporator and the capacity control signal for control of the high-pressure side refrigerant pressure The external variable capacity compressor is controlled by a control signal, and the vapor compression refrigeration cycle is controlled.

本発明の請求項６に係る車両用空調装置は、前記外部可変容量圧縮機のトルクを推定又は検知するトルク推定手段と、前記外部可変容量圧縮機のトルクの目標値を設定するトルク目標値設定手段と、前記外部可変容量圧縮機のトルクを目標値に制御するのに必要となる容量制御信号を演算するトルク用容量制御信号演算手段を備え、前記トルク用容量制御信号演算手段において、前記トルク目標値設定手段により設定されるトルク目標値に基づいて、前記外部可変容量圧縮機のトルクを目標値に制御するのに必要なトルク用容量制御信号が演算され、前記蒸発器の温度制御用容量制御信号と、前記高圧側冷媒圧力の制御用容量制御信号と、前記トルク用容量制御信号とを比較して、前記外部可変容量圧縮機からの冷媒吐出量を最小にする容量制御信号により前記外部可変容量圧縮機を制御し、前記蒸気圧縮式冷凍サイクルを制御するものとした構成としている。 According to a sixth aspect of the present invention, there is provided a vehicular air conditioner that estimates or detects a torque of the external variable capacity compressor, and a torque target value setting that sets a target value of the torque of the external variable capacity compressor. And a torque capacity control signal calculating means for calculating a capacity control signal required to control the torque of the external variable capacity compressor to a target value, wherein the torque capacity control signal calculating means includes: Based on the torque target value set by the target value setting means, a torque capacity control signal necessary for controlling the torque of the external variable capacity compressor to the target value is calculated, and the temperature control capacity of the evaporator is calculated. A capacity that minimizes the refrigerant discharge amount from the external variable capacity compressor by comparing a control signal, a capacity control signal for controlling the high-pressure side refrigerant pressure, and the capacity control signal for torque The control an external variable displacement compressor has a structure in which shall control the vapor compression refrigeration cycle by control signals.

本発明の請求項７に係る車両用空調装置において、前記トルク目標値設定手段は、車両からの圧縮機トルク指令値を参照して、前記外部可変容量圧縮機のトルクの目標値を設定する構成としている。
本発明の請求項８に係る車両用空調装置において、前記蒸気圧縮式冷凍サイクルは、前記放熱器から吐出する高圧冷媒を断熱膨張させる膨張機構を具備し、前記高圧側冷媒圧力検知手段は、前記外部可変容量圧縮機から前記膨張機構までの冷媒内圧力を検知する構成としている。 In the vehicle air conditioner according to claim 7 of the present invention, the torque target value setting means sets a target value of the torque of the external variable capacity compressor with reference to a compressor torque command value from the vehicle. It is said.
In the vehicle air conditioner according to claim 8 of the present invention, the vapor compression refrigeration cycle includes an expansion mechanism that adiabatically expands the high-pressure refrigerant discharged from the radiator, and the high-pressure side refrigerant pressure detection means includes the A refrigerant internal pressure from an external variable capacity compressor to the expansion mechanism is detected.

本発明の請求項９に係る車両用空調装置は、複数の各種容量制御信号演算手段において、外気温度に相関のある物理量、蒸発器への送風量に相関のある物理量、車両の速度に相関のある物理量、車両原動機の回転数に相関のある物理量の少なくとも一つを検知して、容量制御信号演算の入力とすることとした構成としている。
本発明の請求項１０に係る車両用空調装置は、前記蒸気圧縮式冷凍サイクルの冷媒として二酸化炭素を用いた構成としている。 According to a ninth aspect of the present invention, there is provided a vehicle air conditioner, wherein a plurality of various capacity control signal calculating means correlates with a physical quantity correlated with an outside air temperature, a physical quantity correlated with an air flow rate to an evaporator, and a vehicle speed. At least one of a physical quantity and a physical quantity correlated with the rotational speed of the vehicle prime mover is detected and used as an input for capacity control signal calculation.
The vehicle air conditioner according to claim 10 of the present invention has a configuration using carbon dioxide as a refrigerant of the vapor compression refrigeration cycle.

本発明の請求項１〜５に係る制御装置は、上記した構成としているので、外部可変容量圧縮機の容量制御を行うことで、蒸発器の出口空気温度及び高圧側冷媒圧力をそれぞれの目的に応じて的確に制御することが可能であり、その結果、快適性の向上及びサイクル保護の両立を実現できるという非常に優れた効果がもたらされる。 Control device according to claim 1-5 of the present invention, since the configuration described above, by performing the capacity control of the external compressor, the purpose of each outlet air temperature and the high-pressure side refrigerant pressure of the evaporator As a result, it is possible to control accurately, and as a result, it is possible to achieve a very excellent effect of achieving both improvement in comfort and cycle protection.

本発明の請求項６，７に係る車両用空調装置は、上記した構成としたから、外部可変容量圧縮機の容量制御を行うことで、蒸発器の出口空気温度，高圧側冷媒圧力及び圧縮機トルクをそれぞれの目的に応じて的確に制御することが可能であり、その結果、快適性の向上及びサイクル保護の両立を実現できるという非常に優れた効果がもたらされる。
本発明の請求項８に係る車両用空調装置は、上記した構成としたから、より正確な高圧側冷媒圧力を検出することが可能であるという非常に優れた効果がもたらされる。 Since the vehicular air conditioner according to claims 6 and 7 of the present invention has the above-described configuration, by controlling the capacity of the external variable capacity compressor, the outlet air temperature of the evaporator, the high-pressure side refrigerant pressure, and the compressor The torque can be accurately controlled in accordance with each purpose, and as a result, it is possible to achieve a very excellent effect of achieving both improvement in comfort and cycle protection.
Since the vehicular air conditioner according to the eighth aspect of the present invention has the above-described configuration, a very excellent effect that it is possible to detect the high-pressure refrigerant pressure more accurately is brought about.

本発明の請求項９に係る車両用空調装置は、上記した構成としたから、蒸発器の出口空気温度，高圧側冷媒圧力及び圧縮機トルクの制御をより高精度に実現できるという非常に優れた効果がもたらされる。
本発明の請求項１０に係る車両用空調装置は、上記した構成としたから、環境に好適な冷凍回路とすることができるという非常に優れた効果がもたらされる。 Since the vehicle air conditioner according to claim 9 of the present invention has the above-described configuration, it is extremely excellent that the control of the outlet air temperature of the evaporator, the high-pressure side refrigerant pressure, and the compressor torque can be realized with higher accuracy. The effect is brought about.
Since the vehicle air conditioner according to the tenth aspect of the present invention has the above-described configuration, a very excellent effect that a refrigeration circuit suitable for the environment can be obtained.

以下、本発明の実施形態を図面に基づいて説明する。
図１〜図４は、本発明の一実施形態による車両用空調装置を示している。
図１は、自然系冷媒である二酸化炭素を用いた蒸気圧縮式冷凍回路を有する車両用空調装置の機械的な構成部分を示している。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 to 4, that shows the vehicle air conditioner according to an embodiment of the present invention.
FIG. 1 shows mechanical components of a vehicle air conditioner having a vapor compression refrigeration circuit using carbon dioxide, which is a natural refrigerant.

この車両用空調装置の冷凍回路は、クラッチ制御により容量が可変制御可能な可変容量式圧縮機４と、この可変容量式圧縮機４から吐出する高圧冷媒の圧力を検出する高圧側冷媒圧力検出手段５と、可変容量式圧縮機４からの高圧冷媒及び外部空気の熱交換により冷媒を冷却する放熱器６と、放熱器冷却ファン７と、高温部８ａ及び低温部８ｂを具備して放熱器６から吐出する高圧冷媒が高温部８ａを通過する内部熱交換器８と、この内部熱交換器８を通して送られてくる高圧冷媒を断熱膨張させる膨張機構９と、この膨張機構９から送られる冷媒により後述するように空調の空気を冷却するエバポレータ（蒸発器）１０と、このエバポレータ１０から吐出する冷媒を気液分離して液冷媒を貯留すると共に気冷媒を内部熱交換器８の低温部８ｂを通して可変容量式圧縮機４に戻す気液分離器１１を備えており、可変容量式圧縮機４は、プーリ２，２及びベルト３を介して伝達される車両のエンジン１の出力によって作動するようになっている。 The refrigeration circuit of the vehicle air conditioner includes a variable capacity compressor 4 whose capacity can be variably controlled by clutch control, and a high pressure side refrigerant pressure detecting means for detecting the pressure of the high pressure refrigerant discharged from the variable capacity compressor 4. 5, a radiator 6 that cools the refrigerant by heat exchange between the high-pressure refrigerant from the variable capacity compressor 4 and external air, a radiator cooling fan 7, a high-temperature part 8 a, and a low-temperature part 8 b. The internal heat exchanger 8 through which the high-pressure refrigerant discharged from the high-temperature portion 8a passes, the expansion mechanism 9 for adiabatically expanding the high-pressure refrigerant sent through the internal heat exchanger 8, and the refrigerant sent from the expansion mechanism 9 As will be described later, an evaporator (evaporator) 10 that cools air for air conditioning, and a refrigerant discharged from the evaporator 10 is gas-liquid separated to store the liquid refrigerant and the gas refrigerant is stored in the low temperature portion 8 of the internal heat exchanger 8. The gas-liquid separator 11 is returned to the variable displacement compressor 4 through the variable displacement compressor 4 so that the variable displacement compressor 4 is operated by the output of the vehicle engine 1 transmitted through the pulleys 2 and 2 and the belt 3. It has become.

なお、可変容量式圧縮機４の駆動源には、電動モータを用いることができる。また、膨張機構９として、電子式膨張弁や、温度式膨張弁や、差圧式膨張弁を用いることができる。
上記冷凍回路のエバポレータ１０は、車室内へ空調の空気を送る通風ダクト１４内に配置してあって、この通風ダクト１４の入口側には、内気導入口１５ｉ側からの空気導入量と外気導入口１５ｏ側からの空気導入量との割合を制御する内外気切替ダンパ１６が設けてあり、この内外気切替ダンパ１６は、インテークダンパアクチュエータ１３により作動が制御されるものとなっている。この通風ダクト１４において、導入された空気は、ブロワファン１７によって吸引され、下流側のエバポレータ１０に向けて圧送される。 An electric motor can be used as a drive source for the variable capacity compressor 4. As the expansion mechanism 9, an electronic expansion valve, a temperature expansion valve, or a differential pressure expansion valve can be used.
The evaporator 10 of the refrigeration circuit is disposed in a ventilation duct 14 that sends air for air conditioning into the passenger compartment. The amount of air introduced from the inside air inlet 15i and the outside air introduction are introduced into the inlet side of the ventilation duct 14. An inside / outside air switching damper 16 for controlling the ratio of the amount of air introduced from the side of the port 15o is provided, and the operation of the inside / outside air switching damper 16 is controlled by an intake damper actuator 13. In the ventilation duct 14, the introduced air is sucked by the blower fan 17 and is pumped toward the evaporator 10 on the downstream side.

また、エバポレータ１０の出口近傍には、エバポレータ出口空気温度センサ（蒸発器温度検知手段）１２が設けてあり、エバポレータ１０の下流側（図示右側）には、加熱器としてのヒータコア１９が設けてある。このヒータコア１９の近傍には、エアミックスダンパアクチュエータ１８により開度を制御可能なエアミックスダンパ２０が設けてあり、ヒータコア１９を通過する空気とバイパスする空気との割合を調節して、ダンパ２１，２２，２３によりそれぞれ開度を制御可能な吹出口２４，２５，２６から車室内に吹き出させるようにしている。 Further, an evaporator outlet air temperature sensor (evaporator temperature detecting means) 12 is provided in the vicinity of the outlet of the evaporator 10, and a heater core 19 as a heater is provided on the downstream side (right side in the drawing) of the evaporator 10. . An air mix damper 20 whose opening degree can be controlled by an air mix damper actuator 18 is provided in the vicinity of the heater core 19, and the ratio between the air passing through the heater core 19 and the bypassing air is adjusted to adjust the damper 21, The air outlets 22, 23 are blown into the passenger compartment from the air outlets 24, 25, 26 whose opening degree can be controlled.

車室内に配置される車両用空調装置のメインコントローラ３１には、外気温度センサ３２からの外気温度信号と、日射センサ３３からの日射量信号と、車室内温度センサ３４からの車内温度信号と、高圧側圧力検出手段５の高圧側冷媒圧力信号と、蒸発器出口空気温度センサ１２からの蒸発器出口空気温度信号がそれぞれ入力され、このメインコントローラ３１からは、可変容量式圧縮機４の駆動を制御するクラッチコントローラ３５へのクラッチ制御信号３９と、可変容量式圧縮機４への圧縮機容量制御信号３６と、エアミックスダンパアクチュエータ１８へのエアミックスダンパ制御信号３７と、インテークダンパアクチュエータ１３への内外気切替ダンパ制御信号３８がそれぞれ出力されるようになっている。 The main controller 31 of the vehicle air conditioner disposed in the vehicle interior includes an outside air temperature signal from the outside air temperature sensor 32, a solar radiation amount signal from the solar radiation sensor 33, a vehicle interior temperature signal from the vehicle interior temperature sensor 34, The high pressure side refrigerant pressure signal of the high pressure side pressure detecting means 5 and the evaporator outlet air temperature signal from the evaporator outlet air temperature sensor 12 are inputted, respectively, and the main controller 31 drives the variable capacity compressor 4. A clutch control signal 39 to the clutch controller 35 to be controlled, a compressor capacity control signal 36 to the variable displacement compressor 4, an air mix damper control signal 37 to the air mix damper actuator 18, and an intake damper actuator 13 An inside / outside air switching damper control signal 38 is output.

次に、上記した車両用空調装置のメインコントローラ３１により実行される制御について説明する。
本実施形態の車両用空調装置のメインコントローラ３１では、図２に示すように、エバポレータ出口空気温度用容量制御信号演算手段４１及び高圧側冷媒圧力用容量制御信号演算手段５１により、エバポレータ出口空気温度用容量制御信号及び高圧側冷媒圧力用容量制御信号をそれぞれ算出し、これらのエバポレータ出口空気温度用容量制御信号及び高圧側冷媒圧力用容量制御信号をコンプレッサ容量制御信号演算手段６１で比較して、可変容量式圧縮機４からの冷媒吐出量を最小にする容量制御信号によりこの可変容量式圧縮機４を制御するものとなっている。 Next, control executed by the main controller 31 of the vehicle air conditioner described above will be described.
In the main controller 31 of the vehicle air conditioner according to the present embodiment, as shown in FIG. 2, the evaporator outlet air temperature is controlled by the evaporator outlet air temperature capacity control signal calculating means 41 and the high-pressure refrigerant pressure capacity control signal calculating means 51. The capacity control signal for high pressure side and the capacity control signal for high pressure side refrigerant pressure are respectively calculated, and the capacity control signal for evaporator outlet air temperature and the capacity control signal for high pressure side refrigerant pressure are compared by the compressor capacity control signal calculating means 61, The variable capacity compressor 4 is controlled by a capacity control signal that minimizes the refrigerant discharge amount from the variable capacity compressor 4.

詳述すれば、図３に示すように、エバポレータ出口空気温度用容量制御信号演算手段４１は、エバポレータ出口空気温度センサ１２により検知されたエバポレータ１０の出口空気温度がエバポレータ１０目標温度に到達するための過渡状態における目標応答を算出し指定するエバポレータ温度目標応答算出手段（蒸発器温度目標応答算出手段）４２と、その目標応答におけるエバポレータ温度目標応答値とエバポレータ１０の出口空気温度との偏差を演算するエバポレータ出口空気温度フィードバック制御入力演算手段（蒸発器温度フィードバック制御入力演算手段）４３と、このエバポレータ温度目標応答算出手段４２により算出される目標応答における過渡特性を実現するのに必要なフィードフォワード制御入力を予測するエバポレータ出口空気温度フィードフォワード制御入力予測手段（蒸発器温度フィードフォワード制御入力予測手段）４４を備えている。 More specifically, as shown in FIG. 3, the evaporator outlet air temperature capacity control signal calculating means 41 is configured so that the outlet air temperature of the evaporator 10 detected by the evaporator outlet air temperature sensor 12 reaches the evaporator 10 target temperature. An evaporator temperature target response calculation means (evaporator temperature target response calculation means) 42 for calculating and specifying a target response in the transient state of the engine, and calculating a deviation between the evaporator temperature target response value and the outlet air temperature of the evaporator 10 in the target response The evaporator outlet air temperature feedback control input calculating means (evaporator temperature feedback control input calculating means) 43 and the feedforward control necessary for realizing the transient characteristics in the target response calculated by the evaporator temperature target response calculating means 42 An evaporator that predicts input And a mouth air temperature feedforward control input prediction unit (evaporator temperature feedforward control input prediction means) 44.

エバポレータ出口空気温度応答目標値制御手段４２において、エバポレータ出口空気温度応答目標値（Tef）は、エバポレータ出口空気温度目標値（Tet）を参照して、以下の演算式（１）により算出される。
Tef＝（TL1×Tet＋Tc1×Tef(前回値)）／（Tc1＋TL1）演算式（１）
但し、TL1は制御周期であり、Tc1はエバポレータ出口空気温度応答性指定値である。 In the evaporator outlet air temperature response target value control means 42, the evaporator outlet air temperature response target value (Tef) is calculated by the following arithmetic expression (1) with reference to the evaporator outlet air temperature target value (Tet).
Tef = (TL1 x Tet + Tc1 x Tef (previous value)) / (Tc1 + TL1) Formula (1)
However, TL1 is a control cycle, and Tc1 is an evaporator outlet air temperature response specification value.

また、エバポレータ出口空気温度フィードフォワード制御入力予測手段４４において、エバポレータ出口空気温度フィードフォワード目標値（Tetc）と、外気温度（Tamb）と、車速（VS）と、ブロワ電圧（BLV）と、エンジン回転数（Ne）とを参照して、以下の演算式（２）により、エバポレータ出口空気温度フィードフォワード制御入力（Icff_te）を予測する。 In addition, in the evaporator outlet air temperature feedforward control input prediction means 44, the evaporator outlet air temperature feedforward target value (Tetc), the outside air temperature (Tamb), the vehicle speed (VS), the blower voltage (BLV), and the engine speed With reference to the number (Ne), the evaporator outlet air temperature feedforward control input (Icff_te) is predicted by the following arithmetic expression (2).

Icffte＝f(Tetc，Tamb，Ne，VS，BLV) 演算式（２）
ここで、エバポレータ出口空気温度フィードフォワード目標値（Tetc）は、エバポレータ出口空気温度目標値（Tet）を参照して、以下の演算式（３）により算出されるものとする。
Tetc＝(TL2×Tet＋Tcte×Tetc(前回値))／(Tcte＋TL2) 演算式（３）
但し、TL2は制御周期であり、Tcteはエバポレータ出口空気温度フィードフォワード指定値である。 Icffte = f (Tetc, Tamb, Ne, VS, BLV) Equation (2)
Here, the evaporator outlet air temperature feedforward target value (Tetc) is calculated by the following arithmetic expression (3) with reference to the evaporator outlet air temperature target value (Tet).
Tetc = (TL2 x Tet + Tcte x Tetc (previous value)) / (Tcte + TL2) Formula (3)
However, TL2 is a control cycle, and Tcte is an evaporator outlet air temperature feedforward specified value.

さらに、エバポレータ出口空気温度フィードバック制御入力演算手段４３において、エバポレータ出口空気温度フィードバック制御入力値(Icfb_te)は、エバポレータ出口空気温度応答目標値(Tef)と、エバポレータ出口空気温度(Teva)を参照して、以下のような比例演算及び積分演算を行う。
Icfb_te＝Pte(比例演算値)＋Ite(積分演算値) 演算式（４）
Pte＝Kp1×(Teva−Tef) 演算式（５）
Ite＝Ite_n-1＋Kp1/Ti1×(Teva−Tef) 演算式（６）
但し、Kp1は比例ゲインであり、Ti1は積分時間であり、Ite_n-1はIteの前回演算値である。 Further, in the evaporator outlet air temperature feedback control input calculation means 43, the evaporator outlet air temperature feedback control input value (Icfb_te) is determined by referring to the evaporator outlet air temperature response target value (Tef) and the evaporator outlet air temperature (Teva). The following proportional and integral calculations are performed.
Icfb_te = Pte (proportional value) + Ite (integral value) Formula (4)
Pte = Kp1 × (Teva−Tef) Formula (5)
Ite = Ite_n-1 + Kp1 / Ti1 x (Teva-Tef) Formula (6)
However, Kp1 is a proportional gain, Ti1 is an integration time, and Ite_n-1 is a previous calculation value of Ite.

そして、このエバポレータ出口空気温度用容量制御信号演算手段４１では、上記した演算結果に基づいて、以下の演算式（７）によりエバポレータ出口空気温度用容量制御信号（Ic_te）を算出する。
Ic_te＝Icff_te＋Icfb_te 演算式（７）
一方、高圧側冷媒圧力用容量制御信号演算手段５１は、高圧側冷媒圧力検知手段５により検知された高圧側冷媒圧力と、予め高圧側冷媒圧力目標値設定手段により設定された高圧側冷媒圧力目標値とを参照して演算する高圧側冷媒圧力フィードバック制御入力演算手段５３と、高圧側冷媒圧力目標値を実現するのに必要なフィードフォワード制御入力を予測する高圧側冷媒圧力フィードフォワード制御入力予測手段５２を備えている。 Then, the evaporator outlet air temperature capacity control signal calculating means 41 calculates the evaporator outlet air temperature capacity control signal (Ic_te) by the following calculation formula (7) based on the above calculation result.
Ic_te = Icff_te + Icfb_te Formula (7)
On the other hand, the high-pressure side refrigerant pressure capacity control signal calculation means 51 includes a high-pressure side refrigerant pressure detected by the high-pressure side refrigerant pressure detection means 5, and a high-pressure side refrigerant pressure target preset by the high-pressure side refrigerant pressure target value setting means. High-pressure side refrigerant pressure feedback control input calculation means 53 for calculating with reference to the value, and high-pressure side refrigerant pressure feedforward control input prediction means for predicting a feedforward control input necessary to realize the high-pressure side refrigerant pressure target value 52.

この高圧側冷媒圧力フィードフォワード制御入力予測手段５２において、高圧側冷媒圧力目標値（Pdt）と、外気温度（Tamb）と、エンジン回転数（Ne）と、車速（VS）と、ブロワ電圧（BLV）を参照して、以下の演算式（８）により、フィードフォワード制御入力（Icff_pd）を予測する。
Icff_pd＝f(Pdt，Tamb，Ne，VS，BLV) 演算式（８）
また、高圧側冷媒圧力用フィードバック制御入力演算手段５３において、高圧側冷媒圧力フィードバック制御入力値(Icfb_pd)は、高圧側冷媒圧力目標値(Pdt)と、高圧側冷媒圧力(Pd)とを参照して、以下のような比例演算及び積分演算を行う。 In the high pressure side refrigerant pressure feedforward control input prediction means 52, the high pressure side refrigerant pressure target value (Pdt), the outside air temperature (Tamb), the engine speed (Ne), the vehicle speed (VS), and the blower voltage (BLV) ), The feedforward control input (Icff_pd) is predicted by the following arithmetic expression (8).
Icff_pd = f (Pdt, Tamb, Ne, VS, BLV) Equation (8)
In the high pressure side refrigerant pressure feedback control input calculation means 53, the high pressure side refrigerant pressure feedback control input value (Icfb_pd) refers to the high pressure side refrigerant pressure target value (Pdt) and the high pressure side refrigerant pressure (Pd). Then, the following proportional and integral calculations are performed.

Icfb_pd＝比例演算値 (Ppd)＋積分演算値 (Ipd) 演算式（９）
この場合、比例演算値（Ppd）及び積分演算値（Ipd）については、以下のような演算を行う。
Ppd＝Kp2×(Pdt−Pd) 演算式（１０）
Ipd＝Ipd_n-1＋Kp2/Ti2×(Pdt−Pd) 演算式（１１）
但し、Kp2は比例ゲインであり、Ti2は積分時間であり、Ipd_n-1はIpd(積分演算値)の前回演算値である。 Icfb_pd = proportional calculation value (Ppd) + integral calculation value (Ipd) Formula (9)
In this case, the following calculation is performed for the proportional calculation value (Ppd) and the integral calculation value (Ipd).
Ppd = Kp2 x (Pdt-Pd) Formula (10)
Ipd = Ipd_n-1 + Kp2 / Ti2 x (Pdt-Pd) Formula (11)
However, Kp2 is a proportional gain, Ti2 is an integration time, and Ipd_n-1 is a previous calculation value of Ipd (integration calculation value).

そして、この高圧側冷媒圧力用容量制御信号演算手段５１では、上記した演算結果に基づいて、以下の演算式（１２）により、高圧側冷媒圧力用容量制御信号（Ic_pd）を算出する。
Ic_pd＝Icff_pd＋Icfb_pd 演算式（１２）
コンプレッサ容量制御信号演算手段６１では、図４に示すように、上記のようにして算出されたエバポレータ出口空気温度用容量制御信号（Ic_te）と高圧側冷媒圧力用容量制御信号（Ic_pd）とを参照し、以下の要領により、コンプレッサ容量制御信号（Ict）を比較演算する。 Then, the high-pressure side refrigerant pressure capacity control signal calculating means 51 calculates a high-pressure side refrigerant pressure capacity control signal (Ic_pd) by the following arithmetic expression (12) based on the above calculation result.
Ic_pd = Icff_pd + Icfb_pd Arithmetic expression (12)
As shown in FIG. 4, the compressor capacity control signal calculation means 61 refers to the evaporator outlet air temperature capacity control signal (Ic_te) and the high-pressure refrigerant pressure capacity control signal (Ic_pd) calculated as described above. Then, the compressor displacement control signal (Ict) is compared and calculated according to the following procedure.

Ic_te＜Ic_pdならば、Ict＝Ic_teとし、一方、Ic_te＞Ic_pdならば、Ict＝Ic_pdとして、これで算出されたコンプレッサ容量制御信号（Ict）をメインコントローラ３１の容量制御コントローラ部３１ａへの出力とする。
ここで、クラッチを含む場合において、上記コンプレッサ容量制御信号（Ict）を参照して、メインコントローラ３１のクラッチコントローラ部３１ｂへの出力を制御する。 If Ic_te <Ic_pd, Ict = Ic_te. On the other hand, if Ic_te> Ic_pd, Ict = Ic_pd, and the compressor capacity control signal (Ict) calculated in this way is output to the capacity controller 31a of the main controller 31. To do.
Here, when a clutch is included, the output of the main controller 31 to the clutch controller 31b is controlled with reference to the compressor displacement control signal (Ict).

次に、上記した制御演算値に基づいて行うコンプレッサの容量制御要領を図５に示すフローチャートを参照して説明する。
まず、ステップＳ１において、外気温度（Tamb）と、車速（VS）と、ブロワ電圧（BLV）と、エンジン回転数（Ne）と、エバポレータ出口空気温度（Teva）と、高圧側冷媒圧力（Pd）を読み込む。 Next, the compressor capacity control procedure performed based on the control calculation value will be described with reference to the flowchart shown in FIG.
First, in step S1, the outside air temperature (Tamb), vehicle speed (VS), blower voltage (BLV), engine speed (Ne), evaporator outlet air temperature (Teva), and high-pressure side refrigerant pressure (Pd) Is read.

次いで、ステップＳ２及びステップＳ３において、エバポレータ出口空気温度目標値（Tet）及び高圧側冷媒圧力（Pdt）の設定をそれぞれ行った後、ステップＳ４において、
エバポレータ出口空気温度応答目標値制御手段４２によるエバポレータ出口空気温度応答目標値(Tef)の算出を行う。
続いて、ステップＳ５において、エバポレータ出口空気温度フィードフォワード制御入力予測手段４４によるエバポレータ出口空気温度フィードフォワード制御入力(Icff_te)の算出を行い、ステップＳ６において、エバポレータ出口空気温度フィードバック制御入力演算手段４３によるエバポレータ出口空気温度フィードバック制御入力(Icfb_te)の算出を行う。 Next, in step S2 and step S3, after setting the evaporator outlet air temperature target value (Tet) and the high-pressure side refrigerant pressure (Pdt), respectively, in step S4,
The evaporator outlet air temperature response target value control means 42 calculates the evaporator outlet air temperature response target value (Tef).
Subsequently, in step S5, the evaporator outlet air temperature feedforward control input predicting means 44 calculates the evaporator outlet air temperature feedforward control input (Icff_te). In step S6, the evaporator outlet air temperature feedforward control input calculating means 43 calculates. Evaporator outlet air temperature feedback control input (Icfb_te) is calculated.

そして、ステップＳ７において、エバポレータ出口空気温度を制御するための容量制御信号（Ic_te）の算出をエバポレータ出口空気温度用容量制御信号演算手段４１において行う。
一方、ステップＳ８において、高圧側冷媒圧力フィードフォワード制御入力予測手段５２による高圧側冷媒圧力フィードフォワード制御入力（Icff_pd）の算出を行い、ステップＳ９において、高圧側冷媒圧力フィードバック制御入力演算手段５３による高圧側冷媒圧力フィードバック制御入力（Icfb_pd）の算出を行う。 Then, in step S7, a capacity control signal (Ic_te) for controlling the evaporator outlet air temperature is calculated in the evaporator outlet air temperature capacity control signal calculating means 41.
On the other hand, in step S8, the high-pressure side refrigerant pressure feedforward control input predicting means 52 calculates the high-pressure side refrigerant pressure feedforward control input (Icff_pd). In step S9, the high-pressure side refrigerant pressure feedback control input calculating means 53 calculates the high pressure. The side refrigerant pressure feedback control input (Icfb_pd) is calculated.

そして、ステップＳ１０において、高圧側冷媒圧力を制御するための容量制御信号（Ic_pd）の算出を高圧側冷媒圧力用容量制御信号演算手段５１において行う。
上記したステップを実行した後、ステップＳ１１において、容量制御信号判定手段によりエバポレータ出口空気温度用容量制御信号（Ic_te）と高圧側冷媒圧力用容量制御信号（Ic_pd）との比較演算を行い、Ic_te＜Ic_pdならば、ステップＳ１２において、エバポレータ出口空気温度用容量制御信号（Ic_te）をコンプレッサ容量制御信号（Ict）と設定してメインコントローラ３１へ出力し、一方、Ic_te＞Ic_pdならば、ステップＳ１３において、高圧側冷媒圧力用容量制御信号（Ic_pd）をコンプレッサ容量制御信号（Ict）と設定してメインコントローラ３１へ出力する。 In step S10, the capacity control signal (Ic_pd) for controlling the high-pressure side refrigerant pressure is calculated by the high-pressure side refrigerant pressure capacity control signal calculating means 51.
After executing the above steps, in step S11, the capacity control signal determination means performs a comparison operation between the evaporator outlet air temperature capacity control signal (Ic_te) and the high pressure side refrigerant pressure capacity control signal (Ic_pd), and Ic_te < If Ic_pd, in step S12, the evaporator outlet air temperature capacity control signal (Ic_te) is set as the compressor capacity control signal (Ict) and output to the main controller 31, while if Ic_te> Ic_pd, in step S13. The high-pressure side refrigerant pressure capacity control signal (Ic_pd) is set as the compressor capacity control signal (Ict) and output to the main controller 31.

上記したように、この実施形態に係る車両用空調装置では、エバポレータ出口空気温度及び高圧側冷媒圧力のそれぞれ目標値に応じて、各々の容量制御信号を演算し、そして、出力して、可変容量式圧縮機４の容量を制御するようにしているので、エバポレータ出口空気温度及び高圧側冷媒圧力をそれぞれの目的に応じて、的確に制御することができ、すなわち、エバポレータ出口空気温度の安定性を確保することができるだけでなく、高圧側冷媒圧力を適切に制御して高圧側冷媒圧力の上昇を抑制することができ、その結果、快適性の向上及びサイクル保護の両立を実現し得ることとなる。 As described above, in the vehicle air conditioner according to this embodiment, each capacity control signal is calculated and output according to the target values of the evaporator outlet air temperature and the high-pressure side refrigerant pressure, and the variable capacity Since the capacity of the compressor 4 is controlled, the evaporator outlet air temperature and the high-pressure side refrigerant pressure can be accurately controlled according to the respective purposes, that is, the stability of the evaporator outlet air temperature can be controlled. In addition to ensuring, it is possible to appropriately control the high-pressure side refrigerant pressure to suppress an increase in the high-pressure side refrigerant pressure, and as a result, it is possible to achieve both improved comfort and cycle protection. .

図６〜図９は、本発明の他の実施態様に係る車両用空調装置のメインコントローラ３１の制御内容を示している。
本実施形態の車両用空調装置のメインコントローラ３１では、図６及び図７に示すように、エバポレータ出口空気温度用容量制御信号演算手段４１及び高圧側冷媒圧力用容量制御信号演算手段５１により、エバポレータ出口空気温度用容量制御信号及び高圧側冷媒圧力用容量制御信号をそれぞれ算出するのに加えて、トルク用容量制御信号演算手段７１によって、可変容量式圧縮機４のトルクを目標値に制御するのに必要なトルク用容量制御信号を算出し、これらのエバポレータ出口空気温度用容量制御信号，高圧側冷媒圧力用容量制御信号及びトルク用容量制御信号をコンプレッサ容量制御信号演算手段６１で比較して、可変容量式圧縮機４からの冷媒吐出量を最小にする容量制御信号によりこの可変容量式圧縮機４を制御するものとなっている。 FIGS. 6-9 has shown the control content of the main controller 31 of the vehicle air conditioner which concerns on the other embodiment of this invention.
In the main controller 31 of the vehicle air conditioner according to the present embodiment, as shown in FIGS. 6 and 7, the evaporator outlet air temperature capacity control signal calculation means 41 and the high-pressure refrigerant pressure capacity control signal calculation means 51 In addition to calculating the outlet air temperature capacity control signal and the high-pressure side refrigerant pressure capacity control signal, the torque capacity control signal calculation means 71 controls the torque of the variable capacity compressor 4 to a target value. The capacity control signal for torque required for the above is calculated, and the capacity control signal for evaporator outlet air temperature, the capacity control signal for high-pressure side refrigerant pressure, and the capacity control signal for torque are compared by the compressor capacity control signal calculation means 61, The variable capacity compressor 4 is controlled by a capacity control signal that minimizes the refrigerant discharge amount from the variable capacity compressor 4. There.

トルク用容量制御信号演算手段７１は、トルク推定手段により推定又は検知された可変容量式圧縮機４のトルクと、予めトルク目標値設定手段により設定された可変容量式圧縮機４のトルクの目標値とを参照して演算するコンプレッサトルクフィードバック制御入力演算手段７３と、可変容量式圧縮機４のトルクの目標値を実現するのに必要なフィードフォワード制御入力を予測するコンプレッサトルクフィードフォワード制御入力予測手段７２を備えている。 The torque capacity control signal calculation means 71 is the torque of the variable capacity compressor 4 estimated or detected by the torque estimation means and the target value of the torque of the variable capacity compressor 4 preset by the torque target value setting means. Compressor torque feedback control input calculation means 73 for calculating with reference to the above, and compressor torque feedforward control input prediction means for predicting the feedforward control input necessary to realize the target value of the torque of the variable displacement compressor 4 72.

このコンプレッサトルクフィードフォワード制御入力予測手段７２において、コンプレッサトルク目標値（Trqt）と、外気温度（Tamb）と、エンジン回転数（Ne）と、車速（VS）と、ブロワ電圧（BLV）を参照して、以下の演算式（１３）により、フィードフォワード制御入力（Icff_tr）を予測する。
Icff_tr＝f(Trqt，Tamb，Ne，VS，BLV) 演算式（１３）
また、コンプレッサトルクフィードバック制御入力演算手段７３において、コンプレッサトルクフィードバック制御入力値(Icfb_tr)は、コンプレッサトルク目標値（Trqt）と、コンプレッサトルク推定値（Trq_E）とを参照して、以下のような比例演算及び積分演算を行う。 In this compressor torque feedforward control input prediction means 72, the compressor torque target value (Trqt), the outside air temperature (Tamb), the engine speed (Ne), the vehicle speed (VS), and the blower voltage (BLV) are referred to. Thus, the feedforward control input (Icff_tr) is predicted by the following arithmetic expression (13).
Icff_tr = f (Trqt, Tamb, Ne, VS, BLV) Equation (13)
In the compressor torque feedback control input calculation means 73, the compressor torque feedback control input value (Icfb_tr) is proportional to the compressor torque target value (Trqt) and the compressor torque estimated value (Trq_E) as follows: Perform calculations and integration calculations.

Icfb_tr＝比例演算値 (Ptr)＋積分演算値 (Itr) 演算式（１４）
この場合、比例演算値（Ptr）及び積分演算値（Itr）については、以下のような演算を行う。
Ptr＝Kp3×(Trqt−Trq_E) 演算式（１５）
Itr＝Itr_n-1＋Kp3/Ti3×(Trqt−Trq_E ) 演算式（１６）
但し、Kp3は比例ゲインであり、Ti3は積分時間であり、Itr_n-1はItr(積分演算値)の前回演算値である。 Icfb_tr = Proportional calculation value (Ptr) + Integral calculation value (Itr) Formula (14)
In this case, the following calculation is performed for the proportional calculation value (Ptr) and the integral calculation value (Itr).
Ptr = Kp3 × (Trqt−Trq_E) Formula (15)
Itr = Itr_n-1 + Kp3 / Ti3 × (Trqt−Trq_E) Formula (16)
However, Kp3 is a proportional gain, Ti3 is an integration time, and Itr_n−1 is a previous calculation value of Itr (integration calculation value).

そして、このトルク用容量制御信号演算手段７１は、上記した演算結果に基づいて、以下の演算式（１７）により、トルク用容量制御信号（Ic_tr）を算出する。
Ic_tr＝Icff_tr＋Icfb_tr 演算式（１７）
コンプレッサ容量制御信号演算手段６１では、図７に示すように、上記のようにして算出されたエバポレータ出口空気温度用容量制御信号（Ic_te）と、高圧側冷媒圧力用容量制御信号（Ic_pd）と、トルク用容量制御信号（Ic_tr）とを参照し、以下の要領により、コンプレッサ容量制御信号（Ict）を比較演算する。 Then, the torque capacity control signal calculation means 71 calculates a torque capacity control signal (Ic_tr) by the following calculation expression (17) based on the above calculation result.
Ic_tr = Icff_tr + Icfb_tr arithmetic expression (17)
In the compressor capacity control signal calculating means 61, as shown in FIG. 7, the evaporator outlet air temperature capacity control signal (Ic_te) calculated as described above, the high pressure side refrigerant pressure capacity control signal (Ic_pd), Referring to the torque capacity control signal (Ic_tr), the compressor capacity control signal (Ict) is compared and calculated in the following manner.

Ic_te＜Ic_pdで且つIc_te＜Ic_trならば、Ict＝Ic_teとし、
Ic_pd＜Ic_teで且つIc_pd＜Ic_trならば、Ict＝Ic_pdとし、
Ic_tr＜Ic_teで且つIc_tr＜Ic_pdならば、Ict＝Ic_trとして、これで算出されたコンプレッサ容量制御信号（Ict）をメインコントローラ３１の容量制御コントローラ部３１ａへの出力とする。 If Ic_te <Ic_pd and Ic_te <Ic_tr, then Ict = Ic_te,
If Ic_pd <Ic_te and Ic_pd <Ic_tr, then Ict = Ic_pd,
If Ic_tr <Ic_te and Ic_tr <Ic_pd, it is assumed that Ict = Ic_tr, and the compressor capacity control signal (Ict) thus calculated is output to the capacity control controller 31a of the main controller 31.

ここで、クラッチを含む場合において、上記コンプレッサ容量制御信号（Ict）を参照して、メインコントローラ３１のクラッチコントローラ部３１ｂへの出力を制御する。
次に、上記した制御演算値に基づいて行うコンプレッサの容量制御要領を図８及び図９に示すフローチャートを参照して説明する。なお、このフローチャートにおいて、ステップＳ１〜ステップＳ１３では、先の実施形態と同じ制御を行うので、その説明は省略する。 Here, when a clutch is included, the output of the main controller 31 to the clutch controller 31b is controlled with reference to the compressor displacement control signal (Ict).
Next, the compressor capacity control procedure performed based on the control calculation value will be described with reference to the flowcharts shown in FIGS. In this flowchart, since the same control as that in the previous embodiment is performed in steps S1 to S13, the description thereof is omitted.

ステップＳ１４において、コンプレッサトルク目標値（Trqt）の設定を行った後、ステップＳ１５において、コンプレッサトルクフィードフォワード制御入力予測手段７２によるコンプレッサトルクフィードフォワード制御入力（Icff_tr）の算出を行い、ステップＳ１６において、コンプレッサトルクフィードバック制御入力演算手段７３によるコンプレッサトルクフィードバック制御入力（Icfb_tr）の算出を行う。 After the compressor torque target value (Trqt) is set in step S14, the compressor torque feedforward control input (Icff_tr) is calculated by the compressor torque feedforward control input predicting means 72 in step S15. In step S16, the compressor torque feedforward control input (Icff_tr) is calculated. The compressor torque feedback control input calculation means 73 calculates a compressor torque feedback control input (Icfb_tr).

そして、ステップＳ１７において、コンプレッサトルクを制御するための容量制御信号（Ic_tr）の算出をコンプレッサトルク用容量制御信号演算手段７１において行う。
上記したステップを実行した後、ステップＳ１１において、容量制御信号判定手段によりエバポレータ出口空気温度用容量制御信号（Ic_te）と、高圧側冷媒圧力用容量制御信号（Ic_pd）と、コンプレッサトルク用容量制御信号（Ic_tr）との比較演算を行い、Ic_te＜Ic_pdで且つIc_te＜Ic_trならば、ステップＳ１２において、エバポレータ出口空気温度用容量制御信号（Ic_te）をコンプレッサ容量制御信号（Ict）と設定してメインコントローラ３１へ出力する。 In step S17, the compressor torque capacity control signal calculation means 71 calculates a capacity control signal (Ic_tr) for controlling the compressor torque.
After performing the above-described steps, in step S11, the capacity control signal determination means causes the evaporator outlet air temperature capacity control signal (Ic_te), the high-pressure side refrigerant pressure capacity control signal (Ic_pd), and the compressor torque capacity control signal. (Ic_tr) is compared, and if Ic_te <Ic_pd and Ic_te <Ic_tr, in step S12, the evaporator outlet air temperature capacity control signal (Ic_te) is set as the compressor capacity control signal (Ict) and the main controller To 31.

このとき、ステップＳ１１において、Ic_te＞Ic_pd及び／又は Ic_tr＜Ic_teならば、ステップＳ１８に進み、このステップＳ１８において、Ic_pd＜Ic_teで且つIc_pd＜Ic_trならば、ステップＳ１３において、高圧側冷媒圧力用容量制御信号（Ic_pd）をコンプレッサ容量制御信号（Ict）と設定してメインコントローラ３１へ出力する。
そして、ステップＳ１８において、Ic_tr＜Ic_pdならば、ステップＳ１９において、コンプレッサトルク用容量制御信号（Ic_ tr ）をコンプレッサ容量制御信号（Ict）と設定してメインコントローラ３１へ出力する。 At this time, if Ic_te> Ic_pd and / or Ic_tr <Ic_te in step S11, the process proceeds to step S18. If Ic_pd <Ic_te and Ic_pd <Ic_tr in step S18, the high-pressure side refrigerant pressure capacity is determined in step S13. The control signal (Ic_pd) is set as the compressor capacity control signal (Ict) and output to the main controller 31.
If Ic_tr <Ic_pd at step S18, the compressor torque capacity control signal (Ic_tr) is set as the compressor capacity control signal (Ict) and output to the main controller 31 at step S19.

上記したように、この実施形態に係る車両用空調装置では、エバポレータ出口空気温度，高圧側冷媒圧力及びコンプレッサトルクのそれぞれ目標値に応じて、各々の容量制御信号を演算し、そして、出力して、可変容量式圧縮機４の容量を制御するようにしているので、エバポレータ出口空気温度，高圧側冷媒圧力及びコンプレッサトルクをそれぞれの目的に応じて、的確に制御することができ、すなわち、エバポレータ出口空気温度の安定性を確保することができると共に、高圧側冷媒圧力を適切に制御して高圧側冷媒圧力の上昇を抑制することができ、加えて、コンプレッサトルクをも適切に制御し得ることとなり、その結果、快適性の向上及びサイクル保護の両立を実現し得ることとなる。 As described above, in the vehicle air conditioner according to this embodiment, each capacity control signal is calculated and output according to the target values of the evaporator outlet air temperature, the high-pressure side refrigerant pressure, and the compressor torque. Since the capacity of the variable capacity compressor 4 is controlled, the evaporator outlet air temperature, the high-pressure side refrigerant pressure, and the compressor torque can be accurately controlled according to the respective purposes, that is, the evaporator outlet. As well as ensuring the stability of the air temperature, it is possible to appropriately control the high-pressure side refrigerant pressure to suppress an increase in the high-pressure side refrigerant pressure, and in addition to appropriately control the compressor torque. As a result, both improvement in comfort and cycle protection can be realized.

上記した実施形態では、車両用空調装置の蒸気圧縮式冷凍回路における冷媒として二酸化炭素を用いた場合を示しているが、冷媒としてフロン系のものを採用してもよい。
また、上記した実施形態では、蒸気圧縮式冷凍回路が、クラッチ制御により容量可変とした可変容量式圧縮機４を装備している場合を示しているが、クラッチレスのものを用いてもよい。 In the above-described embodiment, the case where carbon dioxide is used as the refrigerant in the vapor compression refrigeration circuit of the vehicle air conditioner is shown, but a fluorocarbon refrigerant may be adopted.
In the above-described embodiment, the vapor compression refrigeration circuit is provided with the variable displacement compressor 4 having a variable capacity by clutch control. However, a clutchless type may be used.

本発明の一実施形態に係る車両用空調装置の概略構成説明図である。It is a schematic structure explanatory view of a vehicle air-conditioner according to an embodiment of the present invention. 図１の車両用空調装置の制御における根幹を成す部分のブロック図である。It is a block diagram of the part which comprises the basis in control of the vehicle air conditioner of FIG. 図１の車両用空調装置の制御における基本構成の前半側を示すブロック図である。It is a block diagram which shows the first half side of the basic composition in control of the vehicle air conditioner of FIG. 図１の車両用空調装置の制御における基本構成の後半側を示すブロック図である。It is a block diagram which shows the latter half side of the basic composition in control of the vehicle air conditioner of FIG. 図１の車両用空調装置の制御要領を示すフローチャートである。It is a flowchart which shows the control point of the vehicle air conditioner of FIG. 本発明の他の実施形態に係る車両用空調装置の制御における基本構成の前半側を示すブロック図である。It is a block diagram which shows the first half side of the basic composition in control of the vehicle air conditioner which concerns on other embodiment of this invention. 図６の車両用空調装置の制御における基本構成の後半側を示すブロック図である。It is a block diagram which shows the latter half side of the basic composition in control of the vehicle air conditioner of FIG. 図６の車両用空調装置の制御要領の前半側を示すフローチャートである。It is a flowchart which shows the first half side of the control point of the vehicle air conditioner of FIG. 図６の車両用空調装置の制御要領の後半側を示すフローチャートである。It is a flowchart which shows the second half side of the control point of the vehicle air conditioner of FIG.

Explanation of symbols

４可変容量式圧縮機
５高圧側冷媒圧力検知手段
６放熱器
９膨張機構
１０エバポレータ（蒸発器）
１２エバポレータ出口空気温度センサ（蒸発器温度検知手段）
４１エバポレータ出口空気温度用容量制御信号演算手段（蒸発器温度用容量制御信号演算手段）
４２エバポレータ温度目標応答算出手段（蒸発器温度目標応答算出手段）
４３エバポレータ出口空気温度フィードバック制御入力演算手段（蒸発器温度フィードバック制御入力演算手段）
４４エバポレータ出口空気温度フィードフォワード制御入力予測手段（蒸発器温度フィードフォワード制御入力予測手段）
５１高圧側冷媒圧力用容量制御信号演算手段
５２高圧側冷媒圧力フィードフォワード制御入力予測手段
５３高圧側冷媒圧力フィードバック制御入力演算手段
６１コンプレッサ容量制御信号演算手段
７１トルク用容量制御信号演算手段
７２コンプレッサトルクフィードフォワード制御入力予測手段
７３コンプレッサトルクフィードバック制御入力演算手段 4 Variable capacity compressor 5 High pressure side refrigerant pressure detection means 6 Radiator 9 Expansion mechanism 10 Evaporator
12 Evaporator outlet air temperature sensor (evaporator temperature detection means)
41 Evaporator outlet air temperature capacity control signal calculation means (evaporator temperature capacity control signal calculation means)
42 Evaporator temperature target response calculation means (evaporator temperature target response calculation means)
43 Evaporator outlet air temperature feedback control input calculation means (evaporator temperature feedback control input calculation means)
44 Evaporator outlet air temperature feedforward control input prediction means (evaporator temperature feedforward control input prediction means)
51 High-pressure side refrigerant pressure capacity control signal calculation means 52 High-pressure side refrigerant pressure feedforward control input prediction means 53 High-pressure side refrigerant pressure feedback control input calculation means 61 Compressor capacity control signal calculation means 71 Torque capacity control signal calculation means 72 Compressor torque Feedforward control input prediction means 73 Compressor torque feedback control input calculation means

Claims

An external variable capacity compressor that operates to pump the refrigerant at an arbitrarily variable capacity according to an external control signal, a radiator that cools the high-temperature and high-pressure refrigerant discharged from the external variable capacity compressor, and vaporization of the refrigerant A vapor compression refrigeration cycle equipped with an evaporator for cooling the air blown into the passenger compartment using heat;
Capacity control signal calculation means for calculating a capacity control signal of the external variable capacity compressor in this vapor compression refrigeration cycle,
In the vehicle air conditioner that controls the external variable capacity compressor by the capacity control signal of the external variable capacity compressor calculated by the capacity control signal calculation means to control the vapor compression refrigeration cycle,
A plurality of the capacity control signal calculation means are provided,
Among the plurality of capacity control signals calculated by these capacity control signal calculation means, the external variable capacity compressor is controlled by a capacity control signal that minimizes the refrigerant discharge amount from the external variable capacity compressor, A vehicle air conditioner that controls the vapor compression refrigeration cycle.

Comprising a high-pressure side refrigerant pressure detecting means for detecting a refrigerant pressure on the high-pressure side of the vapor compression refrigeration cycle,
2. The vehicle air conditioner according to claim 1 , wherein at least a high-pressure side refrigerant pressure detected by the high-pressure side refrigerant pressure detection unit is included as a calculation control input in the capacity control signal calculation unit.

Evaporator temperature detection means for detecting the outlet air temperature of the evaporator of the vapor compression refrigeration cycle or the temperature of the evaporator,
The calculation control input in the capacity control signal calculation means includes at least the high pressure side refrigerant pressure detected by the high pressure side refrigerant pressure detection means and the outlet air temperature of the evaporator detected by the evaporator temperature detection means. The vehicle air conditioner according to claim 2 .

An evaporator target temperature setting means for setting a target temperature of the evaporator of the vapor compression refrigeration cycle;
An evaporator temperature capacity control signal calculating means for calculating a capacity control signal required to control the temperature of the evaporator to a target temperature;
High pressure side refrigerant pressure target value setting means for setting a target value of the high pressure side refrigerant pressure of the vapor compression refrigeration cycle;
A high-pressure side refrigerant pressure capacity control signal calculating means for calculating a capacity control signal required to control the high-pressure side refrigerant pressure to a target value;
In the evaporator temperature capacity control signal calculation means, refer to the evaporator target temperature set by the evaporator target temperature setting means and the outlet air temperature of the evaporator detected by the evaporator temperature detection means. A capacity control signal for temperature control of the evaporator is calculated,
In the high pressure side refrigerant pressure capacity control signal calculation means, the high pressure side refrigerant pressure target value of the refrigeration cycle set by the high pressure side refrigerant pressure target value setting means and the high pressure side detected by the high pressure side refrigerant pressure detection means With reference to the refrigerant pressure, a capacity control signal for controlling the high-pressure side refrigerant pressure is calculated,
The capacity control signal for controlling the temperature of the evaporator and the capacity control signal for controlling the high-pressure side refrigerant pressure are compared, and the external capacity control signal that minimizes the refrigerant discharge amount from the external variable capacity compressor The vehicle air conditioner according to claim 3 , wherein a variable capacity compressor is controlled to control the vapor compression refrigeration cycle.

An evaporator temperature target response calculating means for calculating and specifying a target response in a transient state for the evaporator outlet air temperature or the evaporator temperature to reach the evaporator target temperature detected by the evaporator temperature detecting means;
An evaporator temperature feedback control input computing means for computing a deviation between the evaporator temperature target response value in the target response and the outlet air temperature of the evaporator or the temperature of the evaporator;
Evaporator temperature feedforward control input predicting means for predicting a feedforward control input necessary for realizing a transient characteristic in the target response calculated by the evaporation temperature target response calculating means;
A high-pressure side refrigerant pressure feedback control input that is calculated by referring to the high-pressure side refrigerant pressure detected by the high-pressure side refrigerant pressure detection means and the high-pressure side refrigerant pressure target value set by the high-pressure side refrigerant pressure target value setting means. Computing means;
High pressure side refrigerant pressure feedforward control input predicting means for predicting a feedforward control input necessary for realizing the high pressure side refrigerant pressure target value set by the high pressure side refrigerant pressure target value setting means,
In the evaporator temperature feedback control input calculating means, a deviation between an evaporator temperature target response value calculated by the evaporator temperature target response calculating means and an evaporator outlet air temperature detected by the evaporator temperature detecting means is calculated. Referring to the evaporator temperature feedback control input is calculated,
In the evaporator temperature feedforward control input predicting means, an evaporator temperature feedforward control input is calculated,
In the evaporator temperature capacity control signal calculation means, referring to the sum of the evaporator temperature feedback control input and the evaporator temperature feedforward control input, the evaporator temperature capacity control signal is calculated,
On the other hand, in the high pressure side refrigerant pressure feedback control input calculation means, the high pressure side refrigerant pressure target value set by the high pressure side refrigerant pressure target value setting means and the high pressure side refrigerant pressure detected by the high pressure side refrigerant pressure detection means And the high-pressure side refrigerant pressure feedback control input is calculated,
In the high pressure side refrigerant pressure feedforward control input prediction means, a high pressure side refrigerant pressure feedforward control input is calculated,
In the high pressure side refrigerant pressure capacity control signal calculating means, a high pressure side refrigerant pressure capacity control signal is calculated by referring to the sum of the high pressure side refrigerant pressure feedback control input and the high pressure side refrigerant pressure feedforward control input. ,
The capacity control signal for controlling the temperature of the evaporator and the capacity control signal for controlling the high-pressure side refrigerant pressure are compared, and the external capacity control signal that minimizes the refrigerant discharge amount from the external variable capacity compressor The vehicle air conditioner according to claim 4 , wherein a variable capacity compressor is controlled to control the vapor compression refrigeration cycle.

Torque estimation means for estimating or detecting the torque of the external variable capacity compressor;
Torque target value setting means for setting a target value of torque of the external variable capacity compressor;
A torque capacity control signal calculating means for calculating a capacity control signal required to control the torque of the external variable capacity compressor to a target value;
In the torque capacity control signal calculation means, a torque capacity control signal necessary for controlling the torque of the external variable capacity compressor to a target value based on the torque target value set by the torque target value setting means. Is calculated,
The capacity control signal for temperature control of the evaporator, the capacity control signal for control of the high-pressure side refrigerant pressure, and the capacity control signal for torque are compared, and the refrigerant discharge amount from the external variable capacity compressor is minimized. The vehicle air conditioner according to claim 5 , wherein the external variable capacity compressor is controlled by a capacity control signal to control the vapor compression refrigeration cycle.

7. The vehicle air conditioner according to claim 6 , wherein the torque target value setting means sets a target value of torque of the external variable capacity compressor with reference to a compressor torque command value from the vehicle.

The vapor compression refrigeration cycle includes an expansion mechanism that adiabatically expands the high-pressure refrigerant discharged from the radiator, and the high-pressure side refrigerant pressure detection means is an internal pressure of refrigerant from the external variable capacity compressor to the expansion mechanism. The vehicle air conditioner according to any one of claims 1 to 7 , wherein the vehicle air conditioner is detected.

In a plurality of various capacity control signal calculation means, physical quantities that are correlated with the outside air temperature, physical quantities that are correlated with the air flow to the evaporator, physical quantities that are correlated with the speed of the vehicle, and physical quantities that are correlated with the rotational speed of the vehicle prime mover. The vehicle air conditioner according to any one of claims 1 to 8 , wherein at least one is detected and used as an input of a capacity control signal calculation.

The vehicle air conditioner according to any one of claims 1 to 9 , wherein carbon dioxide is used as a refrigerant of the vapor compression refrigeration cycle.