A pair of combined cylinder blocks which are horizontally disposed are formed with wall portions extending from the boss portions of the cylinder blocks to the bottoms thereof. The wall portions define therebetween a swash plate chamber and an oil pan located beneath the swash plate chamber. The wal
A pair of combined cylinder blocks which are horizontally disposed are formed with wall portions extending from the boss portions of the cylinder blocks to the bottoms thereof. The wall portions define therebetween a swash plate chamber and an oil pan located beneath the swash plate chamber. The wall portions are each formed with a lubricating oil channel communicating the oil pan with a through bore formed in the cylinder block through which the drive shaft of the compressor extends. Due to a pressure differential between the swash plate chamber and the suction chambers of the pump, lubricating oil in the oil pan is led through the lubricating oil channels and gaps between the drive shaft and the through bores and supplied to radial bearings supporting the drive shaft in the through bores, thrust bearings supporting the swash plate and the sliding portions between the swash plate and the pistons to lubricate same. Further, the ends of the lubricating oil channels opening in the through bores are located at such axial predetermined locations as ensure suitable distribution of lubricating oil to the radial bearings and the thrust bearings.
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1. In a swash-plate type compressor having a pair of cylinder blocks combined together in axial alignment and having axes thereof disposed horizontally, each including a plurality of cylinder bores and a boss portion formed therein with a through bore extending axially thereof, said boss portions of
1. In a swash-plate type compressor having a pair of cylinder blocks combined together in axial alignment and having axes thereof disposed horizontally, each including a plurality of cylinder bores and a boss portion formed therein with a through bore extending axially thereof, said boss portions of said cylinder blocks having inner end faces disposed opposite and spaced from each other; a plurality of pistons slidably received within said clyinder bores; a drive shaft rotatably inserted in said axial through bores; a swash plate secured on said drive shaft in slidable engagement with said pistons; a pair of valve plates arranged at opposite ends of said combined cylinder blocks; a pair of cylinder heads secured to the opposite ends of said combined cylinder blocks, said cylinder heads having suction chambers; said valve plates each having a through bore directly communicating an associated one of said axial through bores in said cylinder blocks with an associated one of said suction chambers; said boss portions of said cylinder blocks each having an outer end face disposed substantially in contact with an associated one of said valve plates; a pair of plain radial bearings mounted within said axial through bores and supporting said drive shaft radially thereof; a pair of thrust bearings interposed between said boss portions and said swash plate and supporting said swash plate axially thereof; adjacent lower ones of said cylinder bores defining therebetween a swash plate chamber and an oil reservoir located beneath said swash plate chamber and communicating therewith, said swash plate chamber communicating with all said cylinder bores; the improvement which comprises: a pair of wall portions, each having a substantial thickness and extending from said boss portions to bottom portions of said cylinder blocks, said wall portions defining therebetween said swash plate chamber and said oil reservoir; and a pair of lubricating oil channels formed within said wall portions, said lubricating oil channels each having one end opening in said oil reservoir and the other end opening in a peripheral inner wall of an associated one of said axial through bores at such a predetermined axial location between an associated one of said radial bearings and an associated one of said thrust bearings as permits supply of suitable amounts of lubricating oil from said other end of each of said lubricating oil channels to both said associated radial bearing and said associated thrust bearing, said other ends of said lubricating oil channels each having an opening having a diameter larger than that of the remaining portion thereof; whereby rotation of said swash plate causes lubricant oil in said oil reservoir to be guided through said lubricating oil channels such that part of said lubricant oil is fed in a liquid state to said thrust bearings through gaps between said drive shaft and said axial through bores in said cylinder blocks due to centrifugal force produced by rotation of said thrust bearings, and such that the other part of said lubricant oil is fed in a liquid state to said radial bearings due to a pressure difference between said oil reservoir and said suction chambers, which pressure difference is caused by reciprocating motions of said pistons within respective cylinder bores thereof; said other ends of said lubricating oil channels being located at locations where the distance ratio of a to b is 1 to 2 at maximum, wherein a represents the distance between the diametrical center of said other end of said lubricating oil channel and said outer end face of an associated one of said boss portions of said cylinder blocks, and b represents the distance between the diametrical center of said other end of said lubricating oil channel and said inner end face of said associated boss portion. 2. The swash-plate type compressor as claimed in claim 1, wherein said lubricating oil channels each have said other end located at a predetermined axial location dependent upon a pressure in an associated one of said suction chambers and a pressure in said swash plate chamber at a location in the vicinity of an associated inner end face of said boss portions of said cylinder blocks, the pressures prevailing during operation of the compressor, as well as dependent upon the ratio in flow resistance between a portion of an associated through bore extending from said other end of said lubricating oil channel to an associated outer end face of said boss portions of said cylinder blocks, and another portion of said associated through bore extending from said other end of said lubricating oil channel to an associated inner end face of said boss portions, said predetermined axial location being as permits feeding of lubricating oil to an associated radial bearing at a rate at least about 1.5 times as large as to an associated thrust bearing. 3. The swash-plate type compressor as claimed in claim 1, wherein the clearance of each of said gaps between said drive shaft and said axial through bores is set at a value of 0.02-0.04 mm. 4. In a swash-plate type compressor having a pair of cylinder blocks combined together in axial alignment and having axes thereof disposed horizontally, each including a plurality of cylinder bores and a boss portion formed therein with a through bore extending axially thereof, said boss portions of said cylinder blocks having inner end faces disposed opposite and spaced from each other; a plurality of pistons slidably received within said clyinder bores; a drive shaft rotatably inserted in said axial through bores; a swash plate secured on said drive shaft in slidable engagement with said pistons; a pair of valve plates arranged at opposite ends of said combined cylinder blocks; a pair of cylinder heads secured to the opposite ends of said combined cylinder blocks, said cylinder heads having suction chambers; said valve plates each having a through bore directly communicating an associated one of said axial through bores in said cylinder blocks with an associated one of said suction chambers; said boss portions of said cylinder blocks each having an outer end face disposed substantially in contact with an associated one of said valve plates; a pair of radial needle bearings mounted within said axial through bores and supporting said drive shaft radially thereof; a pair of thrust bearings interposed between said boss portions and said swash plate and supporting said swash plate axially thereof; adjacent lower ones of said cylinder bores defining therebetwen a swash plate chamber and an oil reservoir located beneath said swash plate chamber and communicating therewith, said swash plate chamber communicating with all said cylinder bores; the improvement which comprises: a pair of wall portions, each having a substantial thickness and extending from said boss portions to bottom portions of said cylinder blocks, said wall portions defining therebetween said swash plate chamber and said oil reservoir; and a pair of lubricating oil channels formed within said wall portions, said lubricating oil channels each having one end opening in said oil reservoir and the other end opening in a peripheral inner wall of an associated one of said axial through bores at such a predetermined axial location between an associated one of said radial bearings and an associated one of said thrust bearings as permits supply of suitable amounts of lubricating oil from said other end of each of said lubricating oil channels to both said associated radial bearing and said associated thrust bearing, said other ends of said lubricating oil channels each having an opening having a diameter larger than that of the remaining portion thereof; whereby rotation of said swash plate causes lubricant oil in said oil reservoir to be guided through said lubricating oil channels such that part of said lubricant oil is fed in a liquid state to said thrust bearings through gaps between said drive shaft and said axial through bores in said cylinder blocks due to centrifugal force produced by rotation of said thrust bearings, and such that the other part of said lubricant oil is fed in a liquid state to said radial bearings due to a pressure difference between said oil reservoir and said suction chambers, which pressure difference is caused by reciprocating motions of said pistons within respective cylinder bores thereof; said other ends of said lubricating oil channels being located at locations where the distance ratio of a to b is approximately 1 to 1, wherein a represents the distance between the diametrical center of said other end of said lubricating oil channel and said outer end face of an associated one of said boss portions of said cylinder blocks, and b represents the distance between the diametrical center of said other end of said lubricating oil channel and said inner end face of said associated boss portion. 5. The swash-plate type compressor as claimed in claim 4, wherein said lubricating oil channels each have said other end located at a predetermined axial location dependent upon a pressure in an associated one of said suction chambers and a pressure in said swash plate chamber at a location in the vicinity of an associated inner end face of said boss portions of said cylinder blocks, the pressures prevailing during operation of the compressor, as well as dependent upon the ratio in flow resistance between a portion of an associated through bore extending from said other end of said lubricating oil channel to an associated outer end face of said boss portions of said cylinder blocks, and another portion of said associated through bore extending from said other end of said lubricating oil channel to an associated inner end face of said boss portions, said predetermined axial location being as permits feeding of lubricating oil to an associated radial bearing at a rate at least about 1.5 times as large as to an associated thrust bearing. 6. The swash-plate type compressor as claimed in claim 4, wherein the clearance of each of said gaps between said drive shaft and said axial through bores is set at a value of 0.02-0.04 mm.
Kawashima Kenichi (Hitachi JPX) Horibe Kiyoshi (Hitachi JPX) Degawa Takashi (Mito JPX), Swash plate type compressor for use in air-conditioning system for vehicles.
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