JP5118340B2 - Reciprocating compressor for refrigeration circuit - Google Patents

Reciprocating compressor for refrigeration circuit Download PDF

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JP5118340B2
JP5118340B2 JP2006325544A JP2006325544A JP5118340B2 JP 5118340 B2 JP5118340 B2 JP 5118340B2 JP 2006325544 A JP2006325544 A JP 2006325544A JP 2006325544 A JP2006325544 A JP 2006325544A JP 5118340 B2 JP5118340 B2 JP 5118340B2
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refrigerant
chamber
compression
pressure
intermediate pressure
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JP2008138589A (en
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清 寺内
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Sanden Corp
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Sanden Corp
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Priority to CNA2007800424327A priority patent/CN101535646A/en
Priority to PCT/JP2007/073169 priority patent/WO2008066156A1/en
Priority to US12/516,718 priority patent/US20100068085A1/en
Priority to EP07849947A priority patent/EP2088322A4/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/062—Cooling by injecting a liquid in the gas to be compressed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Sliding Valves (AREA)
  • Compressor (AREA)

Description

本発明は、特に自動車用空調システムのための冷凍回路の往復動型圧縮機に関する。   The present invention relates to a reciprocating compressor of a refrigeration circuit, particularly for an automotive air conditioning system.

この種の往復動型圧縮機はそのシリンダブロック内に複数のシリンダボアを備え、これらシリンダボア内にはピストンが往復動自在に嵌合され、ピストンはそのシリンダボア内に圧縮室を形成する。各ピストンは主軸の回転に伴い、シリンダボア内を順次往復運動し、これにより、圧縮室毎に冷媒の吸引から圧縮を経て吐出に至る一連のプロセスが実行される（特許文献１）。
特開2001-027177号公報 This type of reciprocating compressor has a plurality of cylinder bores in its cylinder block, and pistons are reciprocally fitted in these cylinder bores, and the pistons form a compression chamber in the cylinder bores. Each piston sequentially reciprocates in the cylinder bore with the rotation of the main shaft, thereby executing a series of processes from suction of refrigerant to compression through discharge in each compression chamber (Patent Document 1).
JP 2001-027177

一般的に、自動車用空調システムのための圧縮機には冷媒としてR134aが使用されているが、この冷媒は地球温暖化指数(GWP)が約１３００と非常に高い。このため、特許文献１の圧縮機は、冷媒として地球温暖指数が低い二酸化炭素を使用し、また、近年にあってはCF3Iを含んだ混合冷媒の使用をも提案されている。
前者の冷媒は圧縮時、その動作温度がR134aに比べて１５０℃を越える高温となり、圧縮機が受ける熱負荷は大きい。これに対して、後者の冷媒ではR134aでの場合と同程度の動作温度に抑えることができるものの、冷媒中含まれるCF3I中のC-I結合はその結合エネルギが低いために、冷媒自体がその動作温度にて分解し易い。 Generally, R134a is used as a refrigerant in a compressor for an air conditioning system for automobiles, and this refrigerant has a very high global warming index (GWP) of about 1300. For this reason, the compressor of Patent Document 1 uses carbon dioxide having a low global warming index as a refrigerant, and in recent years, the use of a mixed refrigerant containing CF 3 I has also been proposed.
When the former refrigerant is compressed, its operating temperature is higher than 150 ° C. compared to R134a, and the heat load received by the compressor is large. In contrast, with the latter refrigerant, the operating temperature can be suppressed to the same level as with R134a, but the CI bond in CF 3 I contained in the refrigerant has a low binding energy, so the refrigerant itself Easily decomposes at operating temperature.

本発明は上述の事情に基づいてなされたもので、その目的とするところは、冷媒の吐出温度の上昇を抑制し且つ冷媒の圧縮効率を高めることができる冷凍回路の往復動型圧縮機を提供することにある。   The present invention has been made based on the above-mentioned circumstances, and an object of the present invention is to provide a reciprocating compressor of a refrigeration circuit capable of suppressing an increase in refrigerant discharge temperature and enhancing refrigerant compression efficiency. There is to do.

上記の目的を達成するため、本発明は、弁板とシリンダヘッドとの間に形成され、それぞれ環状をなす吐出室及び吸入室と、複数のシリンダボア内にそれぞれ往復動自在に嵌合され、対応するシリンダボア内に圧縮室を形成し且つ主軸の回転を受けて往復動可能なピストンとを含み、ピストンの往復運動により、対応する圧縮室への冷媒の吸入から圧縮を経て吐出に至る一連のプロセスが実行される冷凍回路の往復動型圧縮機において、シリンダヘッド内に吐出室及び吸入室よりもシリンダヘッドの中央に位置して形成され、冷凍回路から冷媒の吐出圧よりも低く且つ圧縮室内にて圧縮過程にある冷媒の過渡圧よりも高い中間圧の冷媒の供給を受ける中間圧室と、中間圧室と圧縮室とを接続する接続通路と、接続通路に設けられ、冷媒の圧縮過程にて、各圧縮室内の冷媒の圧力が過渡圧と中間圧との間に達しているとき、中間圧室に対し各圧縮室を接続通路を通じて順次連通させるべく回転する回転弁とを具備し、この回転弁は、主軸と中間圧室との間には配置され、主軸に一体的に連結された一端を有する（請求項１）。 To achieve the above object, the present invention is formed between the valve plate and the cylinder head, a discharge chamber and the suction chamber forming a circular respectively fitted freely respectively reciprocate in a plurality of cylinder bores, corresponding to and a reciprocable piston receiving the rotation of the formed and spindle compression chamber into the cylinder bore, the reciprocation of the piston, a set of leading to discharge through the compression from the suction of the refrigerant into the corresponding compression chamber process in There reciprocating compressor of the refrigeration circuit to be performed, than the discharge chamber and the suction chamber in the cylinder head is formed located in the center of the cylinder head, and the compressed lower than the discharge pressure of the refrigeration circuit or al refrigerant an intermediate pressure chamber for receiving a supply of refrigerant higher intermediate pressure than transient pressure of the refrigerant in the indoor hand compression process, a connecting passage connecting the intermediate pressure chamber compression chamber, provided in the connecting passage, the compression of the refrigerant At extent, when the pressure of the refrigerant in each compression chamber has reached between the transient pressure and intermediate pressure, it comprises a rotary valve that rotates in order to sequentially communicated via the connecting passage to the compression chambers to the intermediate-pressure chamber The rotary valve is disposed between the main shaft and the intermediate pressure chamber, and has one end integrally connected to the main shaft .

上述した請求項１の往復動型圧縮機によれば、１つの圧縮室内にて冷媒が圧縮過程にあって、その圧縮室内の冷媒の圧力が過渡圧と中間圧との間に達しているとき、回転弁はその圧縮室と中間圧室とを接続通路を介して連通させる。それ故、中間圧室内の冷媒は中間圧と圧縮室内の圧力との間の差に基づき、その圧縮室内に噴射される。ここで、中間圧室内の冷媒は圧縮室内の冷媒温度よりも低いので、圧縮室内にて圧縮過程にある冷媒は中間圧室からの冷媒と混合されることで冷却される。 According to the above claims 1 reciprocating compressor, in the refrigerant at one compression chamber compression process, when the pressure of the refrigerant in the compression chamber has reached between the transient pressure and intermediate pressure The rotary valve causes the compression chamber and the intermediate pressure chamber to communicate with each other through a connection passage. Therefore, the refrigerant in the intermediate pressure chamber is injected into the compression chamber based on the difference between the intermediate pressure and the pressure in the compression chamber. Here, the refrigerant of the intermediate pressure chamber is lower than the refrigerant temperature in the compression chamber, the refrigerant in the compression process in the compression chamber is cooled by being mixed with refrigerant from the intermediate pressure chamber.

また、上述の目的は、シリンダボア内に往復動自在に嵌合されてシリンダボア内に圧縮室を形成し且つ主軸の回転を受けて往復動可能なピストンを含み、ピストンの往復運動により、圧縮室への冷媒の吸入から圧縮を経て吐出に至る一連のプロセスが実行される冷凍回路の往復動型圧縮機を前提としたとき、冷凍回路から冷媒の吐出圧よりも低く且つ圧縮室内に圧縮過程にある冷媒の過渡圧よりも高い中間圧の冷媒の供給を受ける中間圧室と、中間圧室と圧縮室とを接続する接続通路と、接続通路に設けられ、冷媒の圧縮過程にて、圧縮室内の冷媒の圧力が過渡圧と中間圧との間にあるとき、接続通路を開く回転弁であって、主軸とは独立したモータにより回転される回転弁とを具備した往復動型圧縮機（請求項２）や、請求項２の回転弁を電磁弁に置換した往復動型圧縮機（請求項３）によっても達成可能である。
更にまた本発明の往復動型圧縮機は、斜板を備えた容量可変機構を更に含むことができ（請求項４）、そして、冷媒は二酸化炭素（請求項５）であるか又はC-I結合を有する化合物を含むことができる（請求項６）。 The above-described object includes a piston that is reciprocally fitted in a cylinder bore to form a compression chamber in the cylinder bore and that can be reciprocated by the rotation of the main shaft. Assuming a reciprocating compressor of a refrigeration circuit in which a series of processes from suction of refrigerant to discharge through compression is executed, the refrigerant is under compression from the refrigerant discharge pressure and in the compression chamber An intermediate pressure chamber that receives supply of refrigerant having an intermediate pressure higher than the transient pressure of the refrigerant, a connection passage that connects the intermediate pressure chamber and the compression chamber, and a connection passage are provided in the compression chamber. A reciprocating compressor comprising a rotary valve that opens a connection passage when the refrigerant pressure is between a transient pressure and an intermediate pressure, and that is rotated by a motor independent of the main shaft. 2) and a rotary valve according to claim 2 It can also be achieved by substituted reciprocating compressor to solenoid valve (claim 3).
Furthermore, the reciprocating compressor of the present invention can further include a variable capacity mechanism having a swash plate (Claim 4 ), and the refrigerant is carbon dioxide (Claim 5 ) or has a CI coupling. It can contain the compound which has (claim 6 ).

請求項１〜６の冷凍回路の往復動型圧縮機は、冷媒の圧縮過程にて、圧縮室に中間圧室〜低温の冷媒が噴射されるので、圧縮機からの吐出冷媒の温度上昇が抑制され、冷媒に二酸化炭素やC-I結合を有する化合物を含むことができ、地球温暖化防止に大きく貢献する。また、圧縮過程での圧縮室への冷媒の噴射は、冷媒の圧縮効率を高め、冷凍回路のエネルギ効率向上に大きく寄与する。 In the reciprocating compressor of the refrigeration circuit according to any one of claims 1 to 6 , since the intermediate-pressure chamber to the low-temperature refrigerant are injected into the compression chamber during the refrigerant compression process, an increase in the temperature of the refrigerant discharged from the compressor is suppressed. In addition, the refrigerant can contain carbon dioxide or a compound having a CI bond, which greatly contributes to the prevention of global warming. Moreover, the injection of the refrigerant into the compression chamber during the compression process increases the compression efficiency of the refrigerant and greatly contributes to the improvement of the energy efficiency of the refrigeration circuit.

図１は、自動車用空調システムの冷凍回路を概略的に示す。
冷凍回路は冷媒の循環経路２を備え、この循環経路２に圧縮機４、凝縮器６、第１膨脹弁８、気液分離器１０、第２膨脹弁１２及び蒸発器１４が順次介挿されている。圧縮機４は冷媒を凝縮器６に向けて吐出し、吐出された冷媒は循環経路２を通じて循環する。ここで、循環経路２は、圧縮機４の吐出ポートから凝縮器６を経て第１膨脹弁８に至る高圧域２Ｈと、第１膨脹弁８から気液分離器１０、第２膨脹弁１２及び蒸発器１４を経て圧縮機４の吸入ポートに至る低圧域２Ｌとを有し、図１中、吸入ポート及び吐出ポートは参照符号４ａ，４ｂで示されている。 FIG. 1 schematically shows a refrigeration circuit of an automotive air conditioning system.
The refrigeration circuit includes a refrigerant circulation path 2, and a compressor 4, a condenser 6, a first expansion valve 8, a gas-liquid separator 10, a second expansion valve 12, and an evaporator 14 are sequentially inserted in the circulation path 2. ing. The compressor 4 discharges the refrigerant toward the condenser 6, and the discharged refrigerant circulates through the circulation path 2. Here, the circulation path 2 includes a high pressure region 2 H extending from the discharge port of the compressor 4 through the condenser 6 to the first expansion valve 8, and the gas-liquid separator 10 and the second expansion valve 12 from the first expansion valve 8. And a low pressure region 2 L that reaches the suction port of the compressor 4 through the evaporator 14. In FIG. 1, the suction port and the discharge port are denoted by reference numerals 4 a and 4 b.

図２は圧縮機４の詳細を示す。
圧縮機４は可変容量式の往復動型であって、そのハウジング１６は図２でみて左側からエンドプレート１８、センタケーシング２０及びシリンダヘッド２２を含み、これらは一体的に結合されている。
センタケーシング２０はその内部にエンドプレート１８に隣接したクランク室２４を有し、一方、センタケーシング２０のシリンダヘッド２２側の部位はシリンダブロック２６として形成されている。 FIG. 2 shows details of the compressor 4.
The compressor 4 is a variable capacity reciprocating type, and its housing 16 includes an end plate 18, a center casing 20, and a cylinder head 22 from the left side as viewed in FIG. 2, and these are integrally coupled.
The center casing 20 has a crank chamber 24 adjacent to the end plate 18 in the interior thereof, while a portion of the center casing 20 on the cylinder head 22 side is formed as a cylinder block 26.

センタケーシング２０内には圧縮ユニット２８が配置され、この圧縮ユニット２８はシリンダブロック２６内に形成された複数のシリンダボア３０を備え、これらシリンダボア３０はシリンダブロック２６の軸線回りに等間隔を存して配置され、シリンダブロック２６を貫通している。各シリンダボア３０内にはピストン３２が摺動自在に嵌合され、このピストン３２はシリンダボア３０内に圧縮室３３を形成する。なお、図２には、シリンダボア３０及びピストン３２が１個ずつのみ示されている。 The center casing 2 within 0 compression unit 28 is arranged, the compression unit 28 is provided with a plurality of cylinder bores 30 formed in the cylinder block 26, these bores 30 resides equidistant around the axis of the cylinder block 26 And penetrates the cylinder block 26. A piston 32 is slidably fitted in each cylinder bore 30, and the piston 32 forms a compression chamber 33 in the cylinder bore 30. In FIG. 2, only one cylinder bore 30 and one piston 32 are shown.

一方、クランク室２４内にはシリンダブロック２６の軸線と同軸にして主軸３４が配置され、この主軸３４はシリンダブロック２６に軸受３６を介して回転自在に支持された内端と、エンドプレート１８から軸受３８及びシールユニット４０を介してハウジング１６の外側に延出する外端とを有する。主軸３４の外端は自動車のエンジンから駆動力を受け、主軸３４は回転駆動可能である。 On the other hand, the crank chamber 24 is disposed the main shaft 34 and coaxially with the axis of the cylinder block 26, and the inner end the main shaft 34 is rotatably supported via a bearing 36 to the cylinder block 26, from the end plate 18 It has an outer end that extends to the outside of the housing 16 via a bearing 38 and a seal unit 40. The outer end of the main shaft 34 receives a driving force from the engine of the automobile, and the main shaft 34 can be rotationally driven.

クランク室２４内にて、主軸３４にはロータ４２が取り付けられており、このロータ４２は主軸３４と一体に回転し、エンドプレート１８にスラスト軸受４４を介して回転自在に支持されている。
また、クランク室２４内には主軸３４を囲むようにして斜板４６が配置され、この斜板４６はロータ４２にリンク４８を介して連結されている。リンク４８は主軸３４に対する斜板４６の傾動を許容し、これにより、斜板４６の傾斜角が可変されるようになっている。 In the crank chamber 24, a rotor 42 is attached to the main shaft 34, and the rotor 42 rotates integrally with the main shaft 34 and is rotatably supported by the end plate 18 via a thrust bearing 44.
A swash plate 46 is disposed in the crank chamber 24 so as to surround the main shaft 34, and the swash plate 46 is connected to the rotor 42 via a link 48. The link 48 allows the swash plate 46 to tilt with respect to the main shaft 34, and thereby the tilt angle of the swash plate 46 can be varied.

更に、斜板４６にはラジアル軸受５０及びスラスト軸受５２を介して揺動板５４が支持され、揺動板５４の自転は自転阻止機構（図示しない）により阻止されている。このような揺動板５４と前述した各ピストン３２とはピストンロッド５６の両端にそれぞれ連結され、これらピストンロッド５６の両端は玉継手として構成されている。
上述したように主軸３４が回転されると、この回転力はロータ４２、斜板４６、揺動板５４及びピストンロッド５６を介し、公知の如くピストン３２の往復運動に変換される。 Further, the swash plate 46 supports a swing plate 54 via a radial bearing 50 and a thrust bearing 52, and the rotation of the swing plate 54 is blocked by a rotation blocking mechanism (not shown). Such a swing plate 54 and each of the pistons 32 described above are respectively connected to both ends of a piston rod 56, and both ends of the piston rod 56 are configured as ball joints.
As described above, when the main shaft 34 is rotated, this rotational force is converted into a reciprocating motion of the piston 32 through the rotor 42, the swash plate 46, the swing plate 54 and the piston rod 56 as is well known.

一方、図２から明らかなようにシリンダブロック２６とシリンダヘッド２２との間には弁板５８がガスケット（図示しない）を介して挟み込まれ、この弁板５８にはシリンダボア３０毎、つまり、圧縮室３３毎に割り当てられた吸入孔６０及び吐出孔６２を有する。
弁板５８とシリンダヘッド２２との間には吸入室６４、吐出室６６及び中間圧室６８が互いに独立して形成されている。 On the other hand, as is apparent from FIG. 2, a valve plate 58 is sandwiched between the cylinder block 26 and the cylinder head 22 via a gasket (not shown), and the valve plate 58 is provided for each cylinder bore 30, that is, in the compression chamber. It has a suction hole 60 and a discharge hole 62 assigned to each 33.
Between the valve plate 58 and the cylinder head 22, a suction chamber 64, a discharge chamber 66 and an intermediate pressure chamber 68 are formed independently of each other.

ここで、中間圧室６８はシリンダヘッド２２の中央に位置付けられ、吐出室６６及び吸入室６４は中間圧室６８を順次囲む環状をなしている。
吸入室６４は吸入孔６０にそれぞれ連通する一方、前述した吸入ポート４ａを通じて循環経路２の低圧域２Ｌに接続されている。なお、吸入ポート４ａはシリンダヘッド２２に形成されている。 Here, the intermediate pressure chamber 68 is positioned at the center of the cylinder head 22, and the discharge chamber 66 and the suction chamber 64 have an annular shape that sequentially surrounds the intermediate pressure chamber 68.
Suction chamber 64 while each communicating with the suction hole 60 is connected to a low pressure area 2 L of the circulation path 2 through the suction port 4a described above. The suction port 4a is formed in the cylinder head 22.

一方、吐出室６６は吐出孔６２にそれぞれ連通する一方、前述した吐出ポート４ｂを通じて循環経路２の高圧域２Hに接続され、吐出ポート４ｂもまたシリンダヘッド２２に形成されている。
前述した吸入孔６０及び吐出孔６２は吸入弁７０及び吐出弁７２により開閉可能となっている。これら吸入弁７０及び吐出弁７２は何れもリード弁からなり、弁板５８の両面に分けて配置されている。なお、参照符号７３は吐出弁７２のためのバルブリテーナをそれぞれ示す。 On the other hand, the discharge chamber 66 while respectively communicating with the discharge hole 62, is connected to the high pressure zone 2 H of the circulation path 2 through the discharge port 4b described above, the discharge port 4b are also formed in the cylinder head 22.
The suction hole 60 and the discharge hole 62 described above can be opened and closed by a suction valve 70 and a discharge valve 72. Each of the intake valve 70 and the discharge valve 72 is a reed valve, and is arranged separately on both surfaces of the valve plate 58. Reference numeral 7 3 denotes a valve retainer for the discharge valve 72.

更に、前述した中間圧室６８は導入ポート７４を介して導入経路７６に接続されており、この導入経路７６は前述した気液分離器１０に接続されている（図１）。導入経路７６は気液分離器１０から気相状態の冷媒を導き、導入ポート７４を通じて中間圧室６８に導入させる。
一方、中間圧室６８と主軸３４との間には円筒状の回転弁７８が配置されており、この回転弁７８は弁板５８を気密に貫通し、そして、シリンダブロック２６内に回転自在に嵌合されている。回転弁７８は主軸３４と同軸上に位置付けられ、主軸３４側の一端は主軸３４に一体的に結合されている。従って、回転弁７８は主軸３４と一体に回転する。 Further, the intermediate pressure chamber 68 described above is connected to the introduction path 76 via the introduction port 74, and this introduction path 76 is connected to the gas-liquid separator 10 described above (FIG. 1). The introduction path 76 guides the gas-phase refrigerant from the gas-liquid separator 10 and introduces it into the intermediate pressure chamber 68 through the introduction port 74.
On the other hand, a cylindrical rotary valve 78 is disposed between the intermediate pressure chamber 68 and the main shaft 34, and the rotary valve 78 passes through the valve plate 58 in an airtight manner and is rotatable in the cylinder block 26. It is mated. The rotary valve 78 is positioned coaxially with the main shaft 34, and one end on the main shaft 34 side is integrally coupled to the main shaft 34. Therefore, the rotary valve 78 rotates integrally with the main shaft 34.

具体的には、主軸３４からは回転弁７８に嵌合する駆動ピン８０が突設され、この駆動ピン８０がキー８２を介して回転弁７８に連結されている。また、回転弁７８の他端はシリンダヘッド２２に対してリング状のスラスト軸受８４を介して回転自在に支持されている。
更に、回転弁７８内には内部通路８６が形成され、この内部通路８６は回転弁７８の外周面に開口する一端と、中間圧室６８に連通した他端とを有する。図２から明らかなように内部通路８６の一端は弁板５８の近傍に位置付けられている。 Specifically, a drive pin 80 that fits into the rotary valve 78 protrudes from the main shaft 34, and the drive pin 80 is connected to the rotary valve 78 via a key 82. The other end of the rotary valve 78 is rotatably supported by the cylinder head 22 via a ring-shaped thrust bearing 84.
Further, an internal passage 86 is formed in the rotary valve 78, and this internal passage 86 has one end that opens to the outer peripheral surface of the rotary valve 78 and the other end that communicates with the intermediate pressure chamber 68. As is clear from FIG. 2, one end of the internal passage 86 is positioned in the vicinity of the valve plate 58.

そして、シリンダブロック２６内には、圧縮室３３毎に接続通路としての弁孔８８が形成されている。これら弁孔８８は弁板５８側のシリンダボア３０の上端部にて、対応する圧縮室３３に開口する一端と、回転弁７８の外周面に臨んで開口する他端とを有する。これら弁孔８８の他端は回転弁７８の周方向に等間隔を存し、且つ、回転弁７８が回転されたとき、内部通路８６の一端開口が形成する回転軌跡上に位置付けられている。   In the cylinder block 26, a valve hole 88 is formed as a connection passage for each compression chamber 33. These valve holes 88 have one end that opens to the corresponding compression chamber 33 and the other end that opens toward the outer peripheral surface of the rotary valve 78 at the upper end of the cylinder bore 30 on the valve plate 58 side. The other ends of these valve holes 88 are equally spaced in the circumferential direction of the rotary valve 78, and are positioned on a rotation locus formed by one end opening of the internal passage 86 when the rotary valve 78 is rotated.

従って、回転弁７８が主軸３４とともに回転されたとき、内部通路８８の一端開口、即ち、前述した中間圧室６８は各圧縮室３３にその弁孔８８を通じて順次に連通する。即ち、回転弁７８は主軸３４の回転に伴い、各圧縮室３３と組みをなす弁孔８８を順次開閉することができる。
前述したように主軸３４の回転を受けて、シリンダボア３０内にて、そのピストン３２が順次往復運動するとき、各圧縮室３３では循環経路２の低圧域２Ｌに連なる吸入室６４から吸入孔６０及び吸入弁７０を通じて冷媒が吸入され、そして、吸入冷媒は圧縮され、高圧の冷媒が圧縮室３３から吐出孔６２及び吐出弁７２を通じて吐出室６６に吐出される。この結果、圧縮機４から循環経路２の高圧域２Ｈを通じ、凝縮器６に向けて供給される。 Accordingly, when the rotary valve 78 is rotated together with the main shaft 34, one end opening of the internal passage 88, that is, the above-described intermediate pressure chamber 68 communicates sequentially with each compression chamber 33 through the valve hole 88. That is, the rotary valve 78 can sequentially open and close the valve holes 88 that form a pair with the compression chambers 33 as the main shaft 34 rotates.
In response to rotation of the main shaft 34 as described above, in the cylinder bore 30, when the piston 32 is sequentially reciprocated, the suction holes from the suction chamber 64 communicating with the low pressure area 2 L of each of the compression chambers 33 in the circulation path 2 60 Then, the refrigerant is sucked through the suction valve 70, and the sucked refrigerant is compressed, and the high-pressure refrigerant is discharged from the compression chamber 33 to the discharge chamber 66 through the discharge hole 62 and the discharge valve 72. As a result, the refrigerant is supplied from the compressor 4 to the condenser 6 through the high pressure region 2 H of the circulation path 2.

一方、回転弁７８は主軸３４と一体に回転しているので、回転弁７８の内部通路８６の一端開口は圧縮室３３内での冷媒の圧縮過程にて、その圧縮室３３と組みをなす弁孔８８に連通し、この弁孔８８を所定の開弁期間だけ開く。ここでの連通タイミング及び開弁期間は、圧縮室３３内にて圧縮過程にある冷媒の過渡圧が前述した中間圧室６８内の冷媒圧に達するまでの間でそれぞれ設定されている。   On the other hand, since the rotary valve 78 rotates integrally with the main shaft 34, one end opening of the internal passage 86 of the rotary valve 78 is a valve that forms a pair with the compression chamber 33 in the compression process of the refrigerant in the compression chamber 33. The valve hole 88 communicates with the hole 88 and is opened for a predetermined valve opening period. Here, the communication timing and the valve opening period are set until the transient pressure of the refrigerant in the compression process in the compression chamber 33 reaches the refrigerant pressure in the intermediate pressure chamber 68 described above.

従って、冷媒の圧縮過程にて回転弁７８が開弁されると、中間圧室６８内の冷媒が回転弁７８及び弁孔８８を通じて圧縮室３３内に噴射される。ここで、中間圧室６８には、前述した気液分離器１０からの気相の冷媒が導入され、この導入冷媒は圧縮機４から吐出された冷媒の吐出温度よりも十分に低い。それ故、圧縮室３３内に中間圧室６８内の低温の冷媒が噴射されれば、圧縮室３３内にて、噴射された低温の冷媒と圧縮過程にある高温の冷媒とが混合され、圧縮室３３内での圧縮冷媒の温度、即ち、圧縮機４からの吐出冷媒の温度上昇を抑制できる。   Therefore, when the rotary valve 78 is opened during the refrigerant compression process, the refrigerant in the intermediate pressure chamber 68 is injected into the compression chamber 33 through the rotary valve 78 and the valve hole 88. Here, the gas-phase refrigerant from the gas-liquid separator 10 described above is introduced into the intermediate pressure chamber 68, and this introduced refrigerant is sufficiently lower than the discharge temperature of the refrigerant discharged from the compressor 4. Therefore, if the low-temperature refrigerant in the intermediate pressure chamber 68 is injected into the compression chamber 33, the injected low-temperature refrigerant and the high-temperature refrigerant in the compression process are mixed in the compression chamber 33 and compressed. The temperature of the compressed refrigerant in the chamber 33, that is, the temperature increase of the refrigerant discharged from the compressor 4 can be suppressed.

この結果、地球の温暖化を防止するために、冷媒に高圧に圧縮される二酸化炭素や、CF3Iを含む化合物が使用されても、圧縮機４が受ける熱負荷を大幅に低減でき、また、CF3I中のC-I結合が分解されてしまうこともない。
また、圧縮室３３内への低温冷媒の噴射は、圧縮室３３内での冷媒の圧縮効率を高めることから、冷凍回路のエネルギ効率を効果的に向上させる多効サイクルを容易に実現可能となる。 As a result, in order to prevent global warming, the heat load received by the compressor 4 can be greatly reduced even when carbon dioxide compressed to a high pressure or a compound containing CF 3 I is used as the refrigerant. In addition, the CI bond in CF 3 I is not broken down.
Moreover, since the injection of the low-temperature refrigerant into the compression chamber 33 increases the compression efficiency of the refrigerant in the compression chamber 33, a multi-effect cycle that effectively improves the energy efficiency of the refrigeration circuit can be easily realized. .

一方、前述したクランク室２４は吸入室６４及び吐出室６６の双方に、弁板５８及びシリンダブロック２６を貫通する接続通路（図示しない）を介して接続され、そして、クランク室２４と吸入室６４とを接続する接続通路には絞りが介挿され、クランク室２４と吐出室６６とを接続する接続通路には電磁制御弁が介挿されている。この電磁制御弁は吐出室６６からクランク室２４に流入する高圧冷媒の流入量を制御し、クランク室２４内の圧力を調整する。   On the other hand, the crank chamber 24 described above is connected to both the suction chamber 64 and the discharge chamber 66 via a connection passage (not shown) that penetrates the valve plate 58 and the cylinder block 26, and the crank chamber 24 and the suction chamber 64. Is connected to the connecting passage connecting the crank chamber 24 and the discharge chamber 66, and an electromagnetic control valve is inserted into the connecting passage connecting the crank chamber 24 and the discharge chamber 66. This electromagnetic control valve controls the amount of high-pressure refrigerant flowing from the discharge chamber 66 into the crank chamber 24 and adjusts the pressure in the crank chamber 24.

公知のようにクランク室２４の斜板４６の傾斜角は、各ピストン３２からの圧縮反力と斜板４６の背面に加わるクランク室２４内の圧力、即ち、背圧とが釣り合う角度に保持されるので、クランク室２４内の圧力（背圧）が調整されることで、斜板４６の傾斜角、即ち、各ピストン３２のストロークが調整され、この結果、圧縮機４の冷媒吐出量が可変されることになる。   As is well known, the inclination angle of the swash plate 46 in the crank chamber 24 is maintained at an angle that balances the compression reaction force from each piston 32 and the pressure in the crank chamber 24 applied to the back surface of the swash plate 46, that is, the back pressure. Therefore, by adjusting the pressure (back pressure) in the crank chamber 24, the inclination angle of the swash plate 46, that is, the stroke of each piston 32 is adjusted, and as a result, the refrigerant discharge amount of the compressor 4 is variable. Will be.

ここで、ピストン３２のストロークが可変されても、各圧縮室３３に対する回転弁７８の開弁タイミング及び開弁期間は変化しないので、圧縮機４の冷媒吐出圧と中間圧室６８の冷媒圧との関係は略一定に保たれ、冷媒の圧縮過程での圧縮室３３内への低温冷媒の噴射は安定して実施可能である。
本発明は上述した一実施例に制約されるものではなく、種々の変形が可能である。 Here, even if the stroke of the piston 32 is varied, the valve opening timing and the valve opening period of the rotary valve 78 with respect to each compression chamber 33 do not change, so that the refrigerant discharge pressure of the compressor 4 and the refrigerant pressure of the intermediate pressure chamber 68 This relationship is maintained substantially constant, and the low temperature refrigerant can be stably injected into the compression chamber 33 during the refrigerant compression process.
The present invention is not limited to the above-described embodiment, and various modifications can be made.

例えば、図３は、主軸３４とは独立して回転される回転弁７８を示す。この場合、回転弁７８は電動モータ９０の出力軸９２に同軸にして連結されており、電動モータ９０はシリンダヘッド２２の外面に取り付けられている。通常、電動モータ９０は主軸３４の回転と同期して回転弁７８を回転させるが、必要に応じて回転弁７８の開弁タイミング（連通タイミング）及び開弁期間を調整することができる。   For example, FIG. 3 shows a rotary valve 78 that is rotated independently of the main shaft 34. In this case, the rotary valve 78 is coaxially connected to the output shaft 92 of the electric motor 90, and the electric motor 90 is attached to the outer surface of the cylinder head 22. Normally, the electric motor 90 rotates the rotary valve 78 in synchronization with the rotation of the main shaft 34, but the valve opening timing (communication timing) and valve opening period of the rotary valve 78 can be adjusted as necessary.

また、図４は、回転弁７８に代えて電磁開閉弁９４が使用された変形例を示す。電磁開閉弁９４は各圧縮室３３に割り当てられ、前述した回転弁７８と同様な機能を発揮する。
更に、本発明の往復動型圧縮機は、固定容量式であってもよいし、その駆動源もまたエンジンに代えて電動機を使用可能である。また、往復動の形式もまた、図示の揺動板式に限らず、片斜板式や他のアキシャルピストン方式であってよい。 FIG. 4 shows a modification in which an electromagnetic on-off valve 94 is used in place of the rotary valve 78. The electromagnetic on-off valve 94 is assigned to each compression chamber 33 and exhibits the same function as the rotary valve 78 described above.
Furthermore, the reciprocating compressor of the present invention may be of a fixed capacity type, and its drive source can also use an electric motor instead of the engine. Further, the type of reciprocating motion is not limited to the illustrated swing plate type, but may be a swash plate type or other axial piston type.

冷凍回路の構成を示した概略図である。It is the schematic which showed the structure of the freezing circuit. 図１の圧縮機の詳細を示した断面図である。It is sectional drawing which showed the detail of the compressor of FIG. 変形例の回転弁を示した図である。It is the figure which showed the rotary valve of the modification. 回転弁の代わりに使用される電磁開閉弁を示した図である。It is the figure which showed the electromagnetic on-off valve used instead of a rotary valve.

符号の説明Explanation of symbols

２ 循環経路
１０ 気液分離器
１６ ハウジング
２４ クランク室
３０ シリンダボア
３２ ピストン
３４ 主軸
３３ 圧縮室
４６ 斜板
６８ 中間圧室
７０ 吸入弁
７２ 吐出弁
７４ 導入ポート
７６ 導入経路
７８ 回転弁（開閉弁）
８６ 内部通路（接続通路）
８８ 弁孔（接続通路）
９０ 電動モータ
９４ 電磁開閉弁 2 Circulation path 10 Gas-liquid separator 16 Housing 24 Crank chamber 30 Cylinder bore 32 Piston 34 Main shaft 33 Compression chamber 46 Swash plate 68 Intermediate pressure chamber 70 Suction valve 72 Discharge valve 74 Introduction port 76 Introduction path 78 Rotary valve (open / close valve)
86 Internal passage (connection passage)
88 Valve hole (connection passage)
90 Electric motor 94 Electromagnetic on-off valve

Claims (6)

弁板とシリンダヘッドとの間に形成され、それぞれ環状をなす吐出室及び吸入室と、複数のシリンダボア内にそれぞれ往復動自在に嵌合され、対応するシリンダボア内に圧縮室を形成し且つ主軸の回転を受けて往復動可能なピストンとを含み、前記ピストンの往復運動により、対応するシリンダボア内にて前記圧縮室への冷媒の吸入から圧縮を経て吐出に至る一連のプロセスが実行される冷凍回路の往復動型圧縮機において、
前記シリンダヘッド内に前記吐出室及び前記吸入室よりも前記シリンダヘッドの中央に位置して形成され、前記冷凍回路から前記冷媒の吐出圧よりも低く且つ前記圧縮室内にて圧縮過程にある冷媒の過渡圧よりも高い中間圧の冷媒の供給を受ける中間圧室と、
前記中間圧室と前記各圧縮室とを接続する接続通路と、
前記接続通路に設けられ、前記冷媒の圧縮過程にて、前記各圧縮室内の前記冷媒の圧力が前記過渡圧と前記中間圧との間に達しているとき、前記中間圧室に対し前記各圧縮室を前記接続通路を通じて順次連通させるべく回転する回転弁と
を具備し、
前記回転弁は、前記主軸と前記中間圧室との間に配置され、前記主軸に一体的に連結された一端を有することを特徴とする冷凍回路の往復動型圧縮機。 Formed between the valve plate and the cylinder head, a discharge chamber and the suction chamber forming a circular respectively fitted freely respectively reciprocate in a plurality of cylinder bores, the corresponding formed and spindle compression chamber into the cylinder bore A refrigerating circuit that includes a piston that can reciprocate under rotation, and a reciprocating motion of the piston executes a series of processes from suction of refrigerant into the compression chamber through compression to discharge within the corresponding cylinder bore In the reciprocating compressor of
Wherein in the cylinder head discharge chamber and than the suction chamber is formed located in the center of the cylinder head, in the hands compression process and the compression chamber lower than the discharge pressure of the refrigeration circuit or found before Symbol refrigerant an intermediate pressure chamber for receiving a supply of refrigerant higher intermediate pressure than transient pressure of the refrigerant,
A connecting passage for connecting the respective compression chambers and the intermediate pressure chamber,
When the pressure of the refrigerant in each compression chamber reaches between the transient pressure and the intermediate pressure in the compression process of the refrigerant provided in the connection passage, the compression is performed on the intermediate pressure chamber. A rotary valve that rotates to sequentially communicate the chamber through the connection passage ,
The reciprocating compressor of a refrigeration circuit, wherein the rotary valve has one end that is disposed between the main shaft and the intermediate pressure chamber and is integrally connected to the main shaft . シリンダボア内に往復動自在に嵌合されて前記シリンダボア内に圧縮室を形成し且つ主軸の回転を受けて往復動可能なピストンを含み、前記ピストンの往復運動により、前記圧縮室への冷媒の吸入から圧縮を経て吐出に至る一連のプロセスが実行される冷凍回路の往復動型圧縮機において、
前記冷凍回路から前記冷媒の吐出圧よりも低く且つ前記圧縮室内に圧縮過程にある冷媒の過渡圧よりも高い中間圧の冷媒の供給を受ける中間圧室と、
前記中間圧室と前記圧縮室とを接続する接続通路と、
前記接続通路に設けられ、前記冷媒の圧縮過程にて、前記圧縮室内の前記冷媒の圧力が前記過渡圧と前記中間圧との間にあるとき、前記接続通路を開く回転弁であって、前記主軸とは独立したモータにより回転される回転弁と具備したことを特徴とする冷凍回路の往復動型圧縮機。 A piston that is reciprocally fitted in a cylinder bore to form a compression chamber in the cylinder bore and that can reciprocate in response to the rotation of the main shaft, and sucks refrigerant into the compression chamber by the reciprocating motion of the piston. In a reciprocating compressor of a refrigeration circuit in which a series of processes from compression to discharge is performed,
An intermediate pressure chamber that receives supply of refrigerant having an intermediate pressure lower than the refrigerant discharge pressure from the refrigeration circuit and higher than the transient pressure of the refrigerant in the compression process in the compression chamber;
A connection passage connecting the intermediate pressure chamber and the compression chamber;
A rotary valve that is provided in the connection passage and opens the connection passage when the pressure of the refrigerant in the compression chamber is between the transient pressure and the intermediate pressure in the compression process of the refrigerant, independent reciprocating compressor of refrigeration circuit you characterized by comprising a rotary valve which is rotated by the motor to the main shaft. シリンダボア内に往復動自在に嵌合されて前記シリンダボア内に圧縮室を形成し且つ主軸の回転を受けて往復動可能なピストンを含み、前記ピストンの往復運動により、前記圧縮室への冷媒の吸入から圧縮を経て吐出に至る一連のプロセスが実行される冷凍回路の往復動型圧縮機において、
前記冷凍回路から前記冷媒の吐出圧よりも低く且つ前記圧縮室内に圧縮過程にある冷媒の過渡圧よりも高い中間圧の冷媒の供給を受ける中間圧室と、
前記中間圧室と前記圧縮室とを接続する接続通路と、
前記接続通路に設けられ、前記冷媒の圧縮過程にて、前記圧縮室内の前記冷媒の圧力が前記過渡圧と前記中間圧との間にあるとき、前記接続通路を開く電磁弁と
を具備したことを特徴とする冷凍回路の往復動型圧縮機。 A piston that is reciprocally fitted in a cylinder bore to form a compression chamber in the cylinder bore and that can reciprocate in response to the rotation of the main shaft, and sucks refrigerant into the compression chamber by the reciprocating motion of the piston. In a reciprocating compressor of a refrigeration circuit in which a series of processes from compression to discharge is performed,
An intermediate pressure chamber that receives supply of refrigerant having an intermediate pressure lower than the refrigerant discharge pressure from the refrigeration circuit and higher than the transient pressure of the refrigerant in the compression process in the compression chamber;
A connection passage connecting the intermediate pressure chamber and the compression chamber;
An electromagnetic valve that is provided in the connection passage and opens the connection passage when the pressure of the refrigerant in the compression chamber is between the transient pressure and the intermediate pressure in the compression process of the refrigerant ;
Reciprocating compressor of refrigeration circuit characterized by comprising a. 斜板を備えた容量可変機構を更に含むことを特徴とする請求項１〜３の何れかに記載の冷凍回路の往復動型圧縮機。 The reciprocating compressor for a refrigeration circuit according to any one of claims 1 to 3 , further comprising a variable capacity mechanism including a swash plate. 冷媒は二酸化炭素であることを特徴とする請求項１〜４の何れかに記載の冷凍回路の往復動型圧縮機。 The reciprocating compressor of the refrigeration circuit according to any one of claims 1 to 4 , wherein the refrigerant is carbon dioxide. 冷媒はC-I結合を有する化合物を含むことを特徴とする請求項１〜４の何れかに記載の冷凍回路の往復動型圧縮機。 The reciprocating compressor for a refrigeration circuit according to any one of claims 1 to 4 , wherein the refrigerant includes a compound having a CI bond.
JP2006325544A 2006-12-01 2006-12-01 Reciprocating compressor for refrigeration circuit Expired - Fee Related JP5118340B2 (en)

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PCT/JP2007/073169 WO2008066156A1 (en) 2006-12-01 2007-11-30 Reciprocating compressor of refrigerating machine
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