US3888604A - Compressor for a refrigerating machine - Google Patents

Compressor for a refrigerating machine Download PDF

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US3888604A
US3888604A US400653A US40065373A US3888604A US 3888604 A US3888604 A US 3888604A US 400653 A US400653 A US 400653A US 40065373 A US40065373 A US 40065373A US 3888604 A US3888604 A US 3888604A
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Prior art keywords
low pressure
oil separating
compressor
oil
balance holes
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Expired - Lifetime
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US400653A
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English (en)
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Ryoichiro Oshima
Atsushi Suginuma
Atsuo Kishi
Kenichi Kawashima
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Hitachi Ltd
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Hitachi Ltd
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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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • 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
    • 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
    • F04B27/109—Lubrication

Definitions

  • ABSTRACT A compressor of the swash plate type for a refrigerating machine in which an oil separating chamber is formed in one portion of each of a plurality of cylinder block elements, and two sets of balance holes are formed therein, one set disposed between the oil separating chambers and a crank-case and the other set disposed between the oil separating chambers and a low pressure gas passage. -By this arrangement. blowby gas is ejected at high speed from the crank-case into the oil separating chambers. impinges on walls of the oil separating chambers. and changes its directions of movements to flow into the low pressure gas passage. During this process. lubricant is separated from the blow-by gas and recovered for further use.
  • This invention relates to compressors for refrigerat ing machines. and more particularly it is concerned with a mechanism for precluding the carry-over of oil for a reciprocatory piston compressor of the swash plate type.
  • a lubricant or oil chamber is provided in a lower portion of the crankcase so as to supply oil to various sliding parts of the compressor to effect lubrication by splash lubrication or forced feed lubrication relying on an oil pump.
  • a high negative or sub-atmospheric pressure acts on the crank-ease through the balance hole when the compressor is started. This would cause the lubricant to flow into a low pressure gas passage (the carry-over oil) due to oil foaming and move through the refrigeration cycle with the refrigerant.
  • the lubricant would also flow into the refrigeration cycle through the gaps between the pistons and cylinders, so that shortage of lubricant in the lower portion of the crank-case would ensue.
  • Means has hitherto been provided to separate the lubricant from the refrigerant at the suction side or discharge side of the compressor and recover the same from the refrigeration cycle.
  • the sectional area of the low pressure gas passage suction side
  • the lubricant is required to change the directions of its movement to separate the lubricant from the refrigerant
  • the increased sectional area portion of the low pressure gas passage is made to communicate with the crankcase through a balance hole. so that the lubricant can be returned (by gravity) and the blow-by gas can be reduced (by differential pressure).
  • a lubricant recovery mechanism and a blow-by gas reducing mechanism are provided separately.
  • the dcvice of this type also has disadvantages in that recovery of the lubricant is a time-consuming process and the construction of the device is complex.
  • This invention has its object the provision of a compressor which is capable of precluding a rise in pressure in the crank-case. which permits lubricant to be recovered at early stages, and which is simple in construction.
  • the main characteristic of the invention is that oil separating chambers are formed between the crankcase and the low pressure gas passage and two sets of balance holes are formed therein, one set disposed between the oil separating chambers and the crankcase and the other set disposed between the oil separating chambers and the low pressure gas passage to maintain communication therebetween.
  • FIG. 1 is a sectional view of a conventional compressor of the swash plate type provided with a balance hole;
  • FIG. 2 is an external view ofthe cylinder block of the compressor shown in FIG. 1;
  • FIG. 3 is a vertical sectional view of the compressor of the swash plate type comprising one embodiment of the invention
  • FIG. 4 is an external view of the cylinder block of the compressor shown in FIG. 3. illustrating the stream of a refrigerant
  • FIG. 5 is a detailed view of a portion of the cylinder block shown in FIG. 4 at which a valve plate is attached to the cylinder block;
  • FIG. 6 is the valve plate joining portion shown in FIG. 5 as seen from the side of the valve plate.
  • FIG. 7 and FIG. 8 are vertical sectional views of the compressors of the swash plate type comprising other embodiments of the invention.
  • l and 2 designate a cylin der block split into two pieces or rear and front cylinder block elements by a line perpendicular to the longitudinal axis of the cylinder block.
  • 3 and 4 designate cylinder heads arranged in series at the front and rear ends of the two cylinder block elements I and 2 respectively.
  • 6 and 7 designate valve plates interposed between the cylindcr rear block element I and rear cylinder head 3 and between the front cylinder block element 2 and rear cylinder head 4 respectively, and disposed in predetermined relative positions.
  • 8 designates a drive shaft connected. for example. to a drive of the engine of the vehicle and extending through the central portions of the cylinder block elements I, 2, front cylinder head 4 and valve plates 6, 7.
  • the two cylinder block elements I, 2 are formed with six axial bores 11 of three sets alined with one another and disposed parallel to the center axis of the drive shaft 8., and a reciprocatory piston 12 is received in each set of the bores.
  • Each piston I2 has one side edge cut off as if to straddle an outer edge of the inclined disc 10, and the cut-off portion engages opposite sides of the inclined disc through a steel ball 13 and a slipper 14. so that the pistons 12 can move in reciprocating movement as the inclined disc 10 moves in rotary movement.
  • An axial load applied by the compressing action of the pistons 12 is borne by two thrust bearings 15 interposed between opposite end surfaces of a boss of the inclined disc 10 and the two cylinder block elements 1, 2.
  • a segmental portion disposed above the drive shaft 8 and defined by an upper circularly arcuatc portion of the cylinder block and wall surfaces of two adjacent bores 11 constitutes a portion of a low pressure gas passage 16 through which a refrigerant in a gaseous state is led from the rear cylinder head 3 to the front cylinder head 4.
  • the passage 16 has opposite ends maintained in communication with low pressure chambers 43 in the two cylinder heads 3, 4 through circular or segmental openings formed in the valve plates 6, 7 respectively.
  • Another segmental region 40 (see FIG. 2) constitutes a high pressure gas passage and is maintained in communication with high pressure chambers 41 in the cylinder heads 3, 4 through openings formed in the valve plates 6, 7 respectively.
  • Discharge orifices l7, l8 communicating with the segmental region 40 are connected to an outlet port (not shown) after extending through the interior of the shell 5.
  • Another segmental region 42 disposed in the bottom portion defined by wall surfaces of the bores 11 has inserted therein an oil pump 21 which maintains an oil chamber 19 in the shell 5 in communication with a suction port ofa gear pump 20 for supplying lubricant.
  • the lubricant circulation system ofthe compressor of the type described will be explained.
  • the oil in the shell oil chamber 19 is drawn by suction, pressurized and de' livered by the gear pump 20 to the needle bearings 9, thrust bearings 15, and a mechanical seal 23 through an axial oil bore 22 formed in the central portion of the drive shaft 8 and radial ducts 43a connecting the bore 22 with various sliding parts requiring lubrication.
  • Lubrication of sliding interfaces between the steel balls 13 and seats of the pistons, between the steel balls 13 and slippers 14, and between the slippers 14 and inclined disc 10 is effected by oil ejected through the thrust bearings 15.
  • the oil is returned to the oil chamber 19 after effecting lubrication.
  • blow-by gas such gas is hereinafter referred to as blow-by gas.
  • the blow-by gas would flow from the crank-case 24 into the low pressure gas passage 16 through a small aperture generally referred to as a balance hole through which the crank-case 24 is maintained in communication with the low pressure gas passage 16.
  • a balance hole through which the crank-case 24 is maintained in communication with the low pressure gas passage 16.
  • oil scattered in the crank-case 24 as the inclined disc 10 rotates and adhering to inner walls thereof in film form or oil flying in all directions in the crank-case 24 would flow out of the crank-case 24 and move into the low pressure gas passage 16 together with the blow-by gas.
  • oil moves out of the compressor.
  • the low pressure gas passage 16 includes a relatively narrow passage portion 16 and relatively wider passage portions 26, 26'. so that the refrigerant containing oil returning to the compressor after moving through the refrigeration cycle flows through the low pressure chamber 43 and a suction port 27 of a relatively small cross-sectional area formed in the valve plate 6 into the low pressure gas passage portion 26 of a relatively large cross-sectional area.
  • oil drops are ollected by gravity on the bottom of the relatively wide passage portion 26.
  • the refrigerant impinges on a wall 28 of the cylinder block and the oil is separated therefrom. with the oil being also collected on the bottom of the relatively wide passage portion 26. The oil collected in this way finds its way through the balance hole 25 into the crank-case 24.
  • the crank-case 24 is maintained in direct communication with the low pressure gas passage 16 as aforementioned, the oil flowing into the low pressure gas passage together with the blow-by gas is large in quantity in compressors of this type.
  • the carry-over of oil would take place owing to oil foaming caused by gasification of the refrigerant in a liquid state dissolved in the oil in the oil chamber 19.
  • This is largely responsible for the abnormal noise produced when the compressor is started or the breakdwon of the valve due to abnormal pressure.
  • the system of returning oil to the oil chamber relying on the balance hole is low in efficiency in recovering oil from the refrigeration cycle. This causes lack of lubrication and resultant seizure of the sliding parts.
  • such compressor is also low in the degree of efficiency with which refrigeration is effected because of a high content of oil in the refrigerant.
  • 29' designate oil separating chambers each of which is a segmental section disposed between the adjacent two bores 11 formed in the cylinder block elements 1, 2 and above the drive shaft 8.
  • Each oil separating chamber 29 (29) is defined by an outer wall 24a (24b) of the crank-case 24, a wall 16a (16b) of the low pressure gas passage 16 and the valve plate 6 (7).
  • 25, 25' designate a first set of balance holes formed between the oil separating chambers 29, 29 and the crank-case 24, and 30, 30' designate a second set of balance holes (grooves or small apertures) formed between the oil separating chambers 29, 29' and the low pressure gas passage 16.
  • 31 designates an oil return opening formed between the rear oil separating chamber 29 and the needle bearing portion
  • 32 designates an oil return opening formed between the front oil separating chamber 29' and the mechanical seal box.
  • the blow-by gas leaking through gaps between the cylinder bores 11 and pistons 12 during the compression stroke of the latter is relatively high in pressure.
  • the blow-by gas moves from the crank-case 24 through the first set of balance holes 25, 25' into the oil separating chambers 29, 29' together with a portion of the lubricant in the crankcase 24.
  • Portions of oil drops are collected by gravity on the bottoms of oil separating chambers.
  • the oil which is not separated from the blow-by gas impinges on the valve plates 6, 7, whereby the oil is separated from the refrigerant and also collected on the bottoms of the oil separating chambers 29, 29'.
  • the second set of balance holes 30, 30' is disposed as far away as possible from the first set of balance holes 25, 25' in order to increase the efficiency of separating oil from refrigerant by gravity.
  • the second set of balance holes 30, 30' is disposed near the portions of the compressor at which the valve plates 6, 7 are mounted thereon in order that oil may be separated from refrigerant with a high degree of efficiency by impinging on the valve plates 6, 7.
  • the balance holes 30, 30' of the second set and the balance holes 25, 25' of the first set should be constructed such that the former has a larger sectional area than the latter so as to increase the rate of flow of the oil containing gas through the balance holes 25, 25' over that of the oil containing gas through the balance holes 30, 30', in order that the degree of efficiency with which oil is separated from gas by the impinging of oil drops on the valve plates may be increased.
  • sectional area of the first set of balance holes 25, 25' should be reduced as much as possible to increase the rate at which the gas-oil mixture is ejected thcrethrough while maintaining the size of the sectional area of the second set of balance holes 30, 30 at a suitable level, in order to effectively separate oil from blow-by gas and preclude the carry-over of oil due to the action of blow-by gas.
  • FIG. 3 An example of the invention will be described with reference to FIG. 3.
  • a compressor of the type shown in the figure with a capacity of about I70 cubic centimeters was operated at 3,000 rpm after setting the diameters of the balance holes and the data of relevant parts at suitable levels.
  • the rate of flow of the blow-by gas through the balance holes 25, 25 was about 24 meters per second. It was ascertained experimentally that since the blow-by gas was caused to impinge on the valve plates 6, 7 at such high speed and change its directions of movement suddenly, almost all the oil was separated from the blow-by gas and moved downwardly along the valve plates. After having the oil separated in this way, the blow-by gas moved from the oil separating chambers 29, 29' through the second sets of balance holes 30, 30 into the low pressure gas passage 16.
  • the first set of balance holes 25, 25 is formed near the upper wall of the crank-case 24.
  • the major portion of lubricant scattered by centrifugal forces in the crank-case 24 as the inclined disc rotates adheres to the inner peripheral wall surface of the crank-case. Because of this, it would be possible to increase the efficiency of delivering the oil containing refrigerant to the oil separating chambers 29, 29' if the balance holes 25, 25 were disposed as aforementioned.
  • the balance holes 25, 25 are disposed at right angles to the valve plates 6, 7 respectively.
  • the balance holes 25, 25' may be slightly downwardly oriented in order to increase the efficiency of separating oil from blow-by gas.
  • a recess 44 is formed in a portion of the low pressure gas passage 16 to facilitate movement ofa stream of refrigerant in a gaseous state from the rear low pressure chamber 43 into the low pressure gas passage 16. This is made necessary because of the fact that the second set of balance holes 30, 30' should be disposed at the same or a higher level than the first set of balance holes 25, 25'.
  • the oil collected on the bottom of rear oil separating chamber 29 moves by gravity through the oil return opening 31 to the needle bearing 9 portion from which it is returned to the crank-case 24.
  • the oil collected on the bottom of front oil separating chamber 29' is moved by gravity through the oil return opening 32 to the mechanical seal box from which the oil is passed to the needle bearing 9 portion to lubricate the same before returning to the crank-case 24.
  • the oil containing refrigerant completing the refrigeration cycle is introduced through a suction port 35 into the cylinder head and caused to impinge on a bottom wall of the port, and the oil separated from the refrigerant is collected in an oil sump 33.
  • the oil collected in the oil sump 33 is forcedly recovered by the gear pump 20 and moved to the oil chamber 19 during the suction stroke of the pump through a communication duct 34.
  • the invention obviates all the afore-mentioned disadvantages.
  • almost all the oil accompanying the blow-by gas is separated therefrom and returned to the oil chamber before being introduced into the refrigeration cycle.
  • the efficiency of a refrigerating machine is lowered when there is a high content of oil in the refrigerant in a gaseous state.
  • the invention minimizes the quantity of oil flowing into the refrigeration cycle. thereby increasing the efficiency of the refrigerating machine.
  • the low pressure gas passage 16 may be constructed such that. as shown in FIG. 7. the gas flows into the passage 16 at the center of the shell and flow Ieftwardly and rightwardly in two streams instead of in one direction as shown in FIG. 3.
  • the oil which has not been separated from the refrigerant and introduced into the refrigeration cycle must be recovered by means other than that shown and described with reference to the aforementioned embodiment.
  • Such means would take advantage of the fact that the low pressure gas passage 16 is bifurcated at right angles to its approach passage. No matter what means may be taken, such means should be simple in construction because the quantity of oil introduced into the refrigeration cycle is very small.
  • the invention offers many advantages. Since the invention is effective to separate and recover lubricant from blow-by gas, it is possible to increase the degree of efficiency with which refrigera tion is carried out. Particularly, it is possible to preclude breaking of the valves and production of abnormal noise which might otherwise occur due to overcomprcssion caused by the carry-over of oil taking place, at the time the compressor is started. It is also possible to preclude seizure and cracking of the slippers 14 and to ensure that lacking of lubricant never occurs during normal operation of the compressor. Thus seizure of the sliding parts of the inclined disc can be positively precluded.
  • An additional advantage offered by the invention is that the mechanical seal 23 and needle bearings 9 can be lubricated by the lubricant separated from the blowby gas according to the invention without requiring forced lubrication as shown in FIG. 3, so that the gear pump has only to lubricate the thrust bearings and the sliding parts of the inclined disc.
  • the bore 22 has only to extend from the rear end of the compressor to the front thrust bearing portion only as shown in the figure, making the compressor more economical than conventional compressors.
  • the invention is not limited to the precise form of means for separating lubricant from blow-by gas described as an embodiment. and that any other means may be used instead.
  • rotary blades driven by the stream of blow-by gas may be utilized to attain the end.
  • the lubricant separated from the blow-by gas may be either drawn by suction into the oil chamber or directly returned to the oil chamber.
  • FIG. 8 shows a modification of the embodiment in which, instead of projecting the shell downwardly to provide an oil sump in its lower portion, the segmental region 42 (See FIG. 2.) is used as an oil chamber (not shown).
  • the oil separated in the oil separating chambers 29, 29' from the blow-by gas moves downwardly by its own weight to the oil chamber after moving through the oil return openings 31, 32 and lubricating the needle bearings 9 and mechanical seal 23.
  • This modification is more advantageous from the points of view of production and mounting because the shell is wholly circular in its outer appearance.
  • the invention can be incorporated not only in a compressor of the swash plate type as described above but also in all other types of compressors for refrigerating machines of the type wherein blow-by gas flows into the crank case.
  • a compressor for a refrigerating machine in which rotary movements of a drive shaft are converted into reciprocatory movements of pistons in a crankcase and a refrigerant in a gaseous state is drawn by suction and compressed by a combination of pistons, cylinders, and inlet and discharge valve means.
  • the compressor com prising passage means for maintaining the interior of the crank-case in communication with a low pressure gas passage on the suction side, and oil separating means disposed in said passage means for separating and recovering oil for lubricating the compressor from blow-by gas flowing from the crank-case to said low pressure gas passage including at least two balance holes, each of said balance holes having a small cross sectional area, and an oil separating chamber having a passage disposed between said balance holes, said passage being of a larger cross sectional area than each of said two balance holes.
  • a compressor according to claim 1 wherein oil separating chambers are disposed between the crank case and the low pressure gas passage, said at least two balance holes being disposed between said oil separating chambers and the crank-case substantially at an upper end of each of the oil separating chambers and communicating with said crank-case, and wherein at least two further balance holes are disposed between the oil separating chamber and the low pressure gas passage substantially at the upper end of each oil separating chamber and communicating with the low pressure gas passage.
  • a compressor according to claim 3 wherein said at least two balance holes and said two further balance holes are disposed substantially at the same level.
  • a compressor according to claim 3 wherein said two further balance holes are disposed at a level above said at least two balance holes.
  • a compressor of the swash plate type for a refrigerating machine in which an inclined disc secured to a drive shaft and pistons each slidably received in a cylinder are operatively connected to one another in a crank-case formed in a cylinder block so as to convert rotary movements of the drive shaft into reciprocatory movements of the pistons, inlet and discharge valve means for controlling gas pressure within the compressor, and a low pressure gas passage is formed to communicate with the cylinders at their suction side, such compressor comprising oil separating chambers interposed between said crank-case and said low pressure gas passage, a first set of balance holes formed between the oil separating Chambers and the crank-case and each disposed near the upper end of each oil separating chamber to maintain the oil separating chambers in communication with the crank-case, and a second set of balance holes formed between the oil separating chambers and the low pressure gas passage and each disposed near the upper end of each oil separating chamber to maintain the oil separating chambers in communication with the low pressure gas passage, said oil separating chambers each being formed
  • a compressor of the swash plate type for a refrigerating machine in which said oil separating chambers provided between the crank-case and the low pressure gas passage are closed and equal to each other in dimensions.
  • said balance holes of the first set maintaining an upper portion of the crank-case in communication with upper portions of the oil separating chambers are small in size
  • said balance holes of the second set formed between the oil separating chambers and the low pressure gas passage to maintain them in communication with one another are disposed in upper portions of the oil separating chambers in positions in which they are spaced apart from the balance holes of the first set so as to greatly vary the directions of streams of the refrigerant in a gaseous state 10.
  • a compressor of the swash plate type according to claim 9 further comprising a cylinder block consisting of a pair of cylinder block elements of equal size and shape and built in a shell, a pair of cylinder heads each cylinder head being secured to one of opposite ends of said cylinder block through a valve plate interposed therebctween, and low pressure chambers each defined in one of said cylinder heads, said low pressure gas passage being formed in a portion of said cylinder block in which no cylinders are formed and which is formed with a recess so that the low pressure gas passage is defined by a bottom and walls of the recess and the shell, said oil separating chambers being formed in spaces formed below opposite end portions of said recess with partitions being disposed between said spaces and said low pressure gas passage so that each said oil separating chamber is defined between one of the valve plates and one outer wall of the crank-case, said valve plates each being formed therein with a suction port so as to maintain each of said low pressure chambers in communication with the low pressure gas passage, and said second set of
  • a compressor of the swash plate type for a refrigerating machine wherein one of said oil return openings formed in the lower portions of said oil separating chambers is maintained in communication with a needle bearing portion arranged between the drive shaft and the cylinder block and the other oil return opening is maintained in communication with a mechanical seal portion arranged near one end of the drive shaft.

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US400653A 1972-09-29 1973-09-25 Compressor for a refrigerating machine Expired - Lifetime US3888604A (en)

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JP9704072A JPS5627708B2 (enrdf_load_stackoverflow) 1972-09-29 1972-09-29

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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4127363A (en) * 1976-12-16 1978-11-28 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash-plate type compressor
US4229145A (en) * 1977-01-27 1980-10-21 Diesel Kiki Co., Ltd. Swash plate compressor
US4321019A (en) * 1978-06-02 1982-03-23 Hitachi, Ltd. Swash plate type compressor
US4326838A (en) * 1978-06-07 1982-04-27 Hitachi, Ltd. Swash plate type compressor for use in air-conditioning system for vehicles
US4347046A (en) * 1978-12-04 1982-08-31 General Motors Corporation Swash plate compressor
US4415315A (en) * 1980-11-06 1983-11-15 Diesel Kiki Co., Ltd. Swash-plate type compressor having an improved lubricant oil feeding arrangement
US4701110A (en) * 1985-05-20 1987-10-20 Diesel Kiki Co., Ltd. Swash-plate type rotary compressor with drive shaft, lubrication
US4790727A (en) * 1987-09-25 1988-12-13 Ford Motor Company Swashplate compressor for air conditioning systems
US4820133A (en) * 1987-12-03 1989-04-11 Ford Motor Company Axial piston compressor with discharge valving system in cast housing head
DE4002221A1 (de) * 1989-01-27 1990-08-09 Toyoda Automatic Loom Works Taumelscheibenkompressor mit drucklagerschmierung
DE4006338A1 (de) * 1989-03-02 1990-09-13 Toyoda Automatic Loom Works Taumelscheibenkompressor mit internem kaeltemittel/schmiermittel-trennsystem
DE4090278T1 (de) * 1989-03-02 1991-02-21 Toyoda Automatic Loom Works Taumelscheiben-kaeltemittelkompressor mit einem separator fuer kaeltemittelgas und schmieroel
US5178521A (en) * 1991-04-23 1993-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central discharge passage
US5181834A (en) * 1991-07-26 1993-01-26 Kabushiki Kaisha Toyoda Jidoshokii Seisakusho Swash plate type compressor
US5183394A (en) * 1991-05-10 1993-02-02 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central inlet passage
US5207563A (en) * 1991-05-20 1993-05-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central discharge passage
DE19616650A1 (de) * 1995-04-28 1996-11-14 Toyoda Automatic Loom Works Kältemittel-Kolbenkompressor mit verbesserter Schmierung in der Startphase
US5779004A (en) * 1995-04-18 1998-07-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubricating mechanism for piston type compressor
US6206648B1 (en) * 1997-12-24 2001-03-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor
US20030141149A1 (en) * 2001-12-21 2003-07-31 Noriyuki Shintoku Method and apparatus for lubricating piston type compressor
US20040197202A1 (en) * 2003-03-18 2004-10-07 Akio Saiki Double-headed piston type compressor
US20050053480A1 (en) * 1999-12-17 2005-03-10 Kazuo Murakami Compressor and method of lubricating the compressor
US20080019844A1 (en) * 2006-07-24 2008-01-24 Halla Climate Control Corp. Compressor
US20130101443A1 (en) * 2010-06-21 2013-04-25 Tsutomu Ishikawa Variable Capacity Compressor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52169107U (enrdf_load_stackoverflow) * 1976-06-16 1977-12-22
JPS5765887A (en) * 1980-10-09 1982-04-21 Diesel Kiki Co Ltd Rotary swash-plate type compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3352485A (en) * 1965-10-22 1967-11-14 Toyoda Automatic Loom Works Swash plate compressor for use in air conditioning system for vehicles
US3712759A (en) * 1971-01-04 1973-01-23 Mitchell J Co Lubricating system for multiple piston compressor units and driven parts thereof
US3730648A (en) * 1970-04-13 1973-05-01 S Komiya Swash plate type compressor for automobile air-conditioning
US3796522A (en) * 1970-06-29 1974-03-12 Hitachi Ltd Compressor
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US3730648A (en) * 1970-04-13 1973-05-01 S Komiya Swash plate type compressor for automobile air-conditioning
US3796522A (en) * 1970-06-29 1974-03-12 Hitachi Ltd Compressor
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Cited By (33)

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Publication number Priority date Publication date Assignee Title
US4127363A (en) * 1976-12-16 1978-11-28 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash-plate type compressor
US4229145A (en) * 1977-01-27 1980-10-21 Diesel Kiki Co., Ltd. Swash plate compressor
US4321019A (en) * 1978-06-02 1982-03-23 Hitachi, Ltd. Swash plate type compressor
US4326838A (en) * 1978-06-07 1982-04-27 Hitachi, Ltd. Swash plate type compressor for use in air-conditioning system for vehicles
US4347046A (en) * 1978-12-04 1982-08-31 General Motors Corporation Swash plate compressor
US4415315A (en) * 1980-11-06 1983-11-15 Diesel Kiki Co., Ltd. Swash-plate type compressor having an improved lubricant oil feeding arrangement
US4701110A (en) * 1985-05-20 1987-10-20 Diesel Kiki Co., Ltd. Swash-plate type rotary compressor with drive shaft, lubrication
US4790727A (en) * 1987-09-25 1988-12-13 Ford Motor Company Swashplate compressor for air conditioning systems
US4820133A (en) * 1987-12-03 1989-04-11 Ford Motor Company Axial piston compressor with discharge valving system in cast housing head
DE4002221A1 (de) * 1989-01-27 1990-08-09 Toyoda Automatic Loom Works Taumelscheibenkompressor mit drucklagerschmierung
DE4006338A1 (de) * 1989-03-02 1990-09-13 Toyoda Automatic Loom Works Taumelscheibenkompressor mit internem kaeltemittel/schmiermittel-trennsystem
DE4090278T1 (de) * 1989-03-02 1991-02-21 Toyoda Automatic Loom Works Taumelscheiben-kaeltemittelkompressor mit einem separator fuer kaeltemittelgas und schmieroel
US5088897A (en) * 1989-03-02 1992-02-18 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with internal refrigerant and lubricant separating system
US5178521A (en) * 1991-04-23 1993-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central discharge passage
US5183394A (en) * 1991-05-10 1993-02-02 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central inlet passage
US5207563A (en) * 1991-05-20 1993-05-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with a central discharge passage
US5181834A (en) * 1991-07-26 1993-01-26 Kabushiki Kaisha Toyoda Jidoshokii Seisakusho Swash plate type compressor
US5779004A (en) * 1995-04-18 1998-07-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubricating mechanism for piston type compressor
DE19616650A1 (de) * 1995-04-28 1996-11-14 Toyoda Automatic Loom Works Kältemittel-Kolbenkompressor mit verbesserter Schmierung in der Startphase
US5772407A (en) * 1995-04-28 1998-06-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating piston type compressor improved to distribute lubricating oil sufficiently during the starting phase of its operation
DE19616650C2 (de) * 1995-04-28 1998-07-30 Toyoda Automatic Loom Works Kältemittel-Kolbenkompressor mit verbesserter Schmierung in der Startphase
US6206648B1 (en) * 1997-12-24 2001-03-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor
US7117782B2 (en) * 1999-12-17 2006-10-10 Kabushiki Kaisha Toyota Jidoshokki Compressor and method of lubricating the compressor
US20050053480A1 (en) * 1999-12-17 2005-03-10 Kazuo Murakami Compressor and method of lubricating the compressor
US6862975B2 (en) * 2001-12-21 2005-03-08 Kabushiki Kaisha Toyota Jidoshokki Apparatus for lubricating piston type compressor
US20030141149A1 (en) * 2001-12-21 2003-07-31 Noriyuki Shintoku Method and apparatus for lubricating piston type compressor
US20040197202A1 (en) * 2003-03-18 2004-10-07 Akio Saiki Double-headed piston type compressor
US7547198B2 (en) * 2003-03-18 2009-06-16 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type compressor
US20080019844A1 (en) * 2006-07-24 2008-01-24 Halla Climate Control Corp. Compressor
JP2008025583A (ja) * 2006-07-24 2008-02-07 Halla Climate Control Corp 圧縮機
EP1884662A3 (en) * 2006-07-24 2008-08-27 Halla Climate Control Corporation Compressor
US7950904B2 (en) 2006-07-24 2011-05-31 Halla Climate Control Corp. Compressor
US20130101443A1 (en) * 2010-06-21 2013-04-25 Tsutomu Ishikawa Variable Capacity Compressor

Also Published As

Publication number Publication date
JPS5627708B2 (enrdf_load_stackoverflow) 1981-06-26
JPS4961702A (enrdf_load_stackoverflow) 1974-06-14

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