EP1061257A1 - Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau - Google Patents

Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau Download PDF

Info

Publication number
EP1061257A1
EP1061257A1 EP99111549A EP99111549A EP1061257A1 EP 1061257 A1 EP1061257 A1 EP 1061257A1 EP 99111549 A EP99111549 A EP 99111549A EP 99111549 A EP99111549 A EP 99111549A EP 1061257 A1 EP1061257 A1 EP 1061257A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
upper lid
main body
pressure adjusting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99111549A
Other languages
English (en)
French (fr)
Other versions
EP1061257B1 (de
Inventor
Sadatake Fujikoki Corporation Ise
Akinori Fujikoki Corporation Fujisawa
Masaki Fujikoki Corporation Tomaru
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujikoki Corp filed Critical Fujikoki Corp
Priority to DE69923437T priority Critical patent/DE69923437T2/de
Priority to EP19990111549 priority patent/EP1061257B1/de
Publication of EP1061257A1 publication Critical patent/EP1061257A1/de
Application granted granted Critical
Publication of EP1061257B1 publication Critical patent/EP1061257B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge pressure

Definitions

  • the present invention relates to a pressure adjusting valve, and in particular to a pressure adjusting valve for a variable capacity compressor to be mounted on air conditioners for vehicles.
  • a vapor compression type cooling system is extensively employed as a cooling system for a vehicle.
  • a coolant is turned into a gas of high temperature and high pressure as the coolant is adiabatically compressed in a compressor, and this resultant gas is then liquefied as the heat thereof is released therefrom in a condenser.
  • the resultant liquid is adiabatically expanded by means of an expansion valve thereby causing the liquid to absorb an external heat in an evaporator, thus causing the liquid to turn into gas while concurrently bringing about a cooling effect of air, the resultant gasified coolant being returned again to the compressor.
  • this cooling system is a kind of refrigerating cycle which takes advantage of the heat of evaporation.
  • FIG. 7 illustrates a refrigerating apparatus of the aforementioned vapor compression type cooling system, which is constituted by a compressor A, a condenser B, an expansion valve C and an evaporator D.
  • the compressor A shown in FIG. 7 is a reciprocating type compressor utilizing a wobble plate, and is consisted of a driving shaft 81, a wobble plate 82, a connecting rod 83, a piston 84 and a cylinder 85.
  • the driving shaft 81 which is rotatably arranged inside the crankcase 80 is designed to be driven by an engine (not shown) through a pulley 86 and a belt 87 which are attached to one end of the driving shaft 81.
  • the wobble plate 82 mounted on the driving shaft 81 is rotated following the rotation of driving shaft 81.
  • the wobble plate 82 is spherically coupled, through an annular groove 88 formed in the wobble plate 82, with the connecting rod 83.
  • each cylinder 85 of the compressor A is provided with a suction chamber “s” and a discharging chamber “d” wherein these plural suction chambers "s” are mutually communicated with each other, and likewise, these plural discharging chambers "d” are mutually communicated with each other.
  • the suction chamber “s” is provided with a valve which is designed to be opened in the suction stroke of the piston 84, while the discharging chamber “d” is provided with a valve which is designed to be opened in the discharge stroke of the piston 84. Further, the discharging chamber “d” is communicated with the condenser B, while the evaporator D is communicated with the suction chamber “s", so that a coolant discharged from the discharging chamber "d” is permitted pass through the condenser B, the expansion valve C and the evaporator D thereby bringing about a predetermined cooling effect, after which the coolant is returned to the suction chamber "s".
  • a pressure adjusting valve 1' is built in a suitable portion of the compressor A.
  • This pressure adjusting valve 1' is designed to detect a pressure of coolant to be sucked in Lhe cylinder 85 thereby altering the capacity of the coolant to be flown into the crankcase 80, thereby controlling the pressure inside the compressor A and hence to maintain the pressure inside the evaporator D.
  • the suction chamber “s" of the cylinder 85 is communicated with a pressure chamber 21' of the pressure adjusting valve 1', the interior of the crankcase 80 is communicated with an intermediate chamber 22' of the pressure adjusting valve 1', and the discharging chamber “d" of the cylinder 85 is communicated with a valve chamber 23' of the pressure adjusting valve 1'.
  • this pressure adjusting valve 1' is constituted by a pressure responding motive portion 10' and a main body portion 20'.
  • the pressure responding motive portion 10' attached to one end of the main body portion 20' comprises an upper lid 12' retaining a diaphragm 11' which is sandwiched between the upper lid 12' and a lower lid 22' integrally attached to the main body portion 20', and a case 13' which is integrally mounted through welding on the upper lid 12'.
  • an adjusting screw 17' screwed into the case 13', a spring shoe 15' contacted with an upper reinforcing plate 14' for the diaphragm 11', and a pressure-setting spring 16' interposed between the adjusting screw 17' and the spring shoe 15' and urging a ball valve 25' in the direction to open the passageway.
  • the main body portion 20' comprises an operating rod 24' contacted with a lower reinforcing plate 32' for the diaphragm 11', and a slide hole 28' formed passing through the main body portion 20'.
  • a pressure chamber 21' is formed at a portion of the main body portion 20' where one end of the operating rod 24' and the lower reinforcing plate 32' are located, and is provided with an inlet port 29' for introducing a suction pressure (a suction pressure: Ps) of the cylinder 85.
  • the other end of the operating rod 24' is extended to the valve chamber 23' in which there are disposed a ball valve 25' contacted with the other end of the operating rod 24', a valve seat 27', and a ball valve-retaining spring 26' interposed between a valve guard 33' contacted with the ball valve 25' and a spring shoe 46' built in the valve chamber 23', the ball valve-retaining spring 26' being set so as to urge the ball valve 25' in the direction to close the passageway.
  • a feeding port 30' for feeding a pressure (a pressure inside the crankcase: Pc) inside the compressor A is formed over the valve seat 27', and an inlet port 31' for introducing a discharge pressure (a discharge pressure: Pd) of the cylinder 85 is formed below the valve seat 27'.
  • the pressure from the evaporator D is introduced into the suction chamber “s" and the pressure chamber 21', and when the suction pressure Ps is decreased, i.e. when the pressure inside the pressure chamber 21' is decreased, the urging force of the pressure-setting spring 16' becomes larger than the combined force of the diaphragm 11' and the ball valve-retaining spring 26', thereby causing the diaphragm 11' to move in the direction to push down the operating rod 24'.
  • the ball valve 25' is opened, and the discharge pressure Pd is introduced via the pressure adjusting valve 1' into the interior of the crankcase 80, thereby increasing the pressure Pc inside the crankcase and concurrently increasing the angle ⁇ between the driving shaft 81 and the wobble plate 82, thus minimizing the magnitude of stroke of the piston 84.
  • the pressure adjusting valve 1' is designed to detect the suction pressure Ps and to control the pressure Pc inside the crankcase thereby to alter the magnitude of stroke of the piston 84, thus maintaining the pressure of the evaporator D.
  • a vehicle is capable of suitably coping with any changes in operating environment, in particular, changes of environment due to atmospheric pressure and temperature.
  • the pressure responding motive portion 10' should be free from any influence by environmental changes as a vehicle travels on a road including a low altitude portion as well as a high altitude portion.
  • a pressure adjusting valve is proposed in Japanese Patent Unexamined Publication (Kokai) H5-39876 wherein the pressure-setting spring 16' is adjusted by means of a screw 17', and after a vacuum cap 18' is welded to the spring case 13', the pressure responding motive portion 10' is exhausted to a predetermined gas pressure or filled with an inert gas using a capillary tube (not shown) thereby preventing the pressure responding motive portion 10' from being influenced by changes in pressure and temperature (FIG. 8).
  • the diaphragm is held between the upper lid and the lower lid, and after the fringe portion of the diaphragm is welded, the spring case and capillary tube are secured to the upper lid by means of welding. Thereafter, the interior of the pressure responding motive portion 10' is adjusted to a predetermined gas pressure, followed by the sealing of the capillary tube.
  • the present invention has been made under the circumstances mentioned above, and therefore an object of the present invention is to provide a pressure adjusting valve, which is capable of improving the air-tightness of the pressure responding motive portion and the performance of the main body portion, and at the same time, capable of minimizing the manufacturing cost thereof by reducing the working process, assembling process and parts to be employed.
  • a pressure adjusting valve for a variable capacity compressor comprising a main body portion provided with a lower lid, a spring case provided with an upper lid, and a diaphragm held between said upper lid and said lower lid; wherein said lower lid is provided at an outer circumference portion thereof with a cylindrical fitting portion and an annular projection, and said upper lid and said lower lid are hermetically connected with each other in such a manner that said upper lid is fitted in said cylindrical fitting portion, said annular projection is bent innerward leaning against said upper lid, and a space between said annular projection and said upper lid is soldered.
  • a pressure adjusting valve for a variable capacity compressor comprising a main body portion provided with a lower lid, a spring case provided with an upper lid, and a diaphragm held between said upper lid and said lower lid; wherein said upper lid and said lower lid are hermetically connected with each other by means of an electron beam welding which is effected at annular outer circumferential portions of these upper and lower lids.
  • the main body portion is provided with a valve chamber having a valve body arranged therein, and a conical coil spring urging said valve body in a direction to close a passageway, wherein said conical coil spring is arranged such that a smaller diametral portion thereof is directly contacted with said valve body thereby pushingly supporting said valve body, and a larger diametral portion thereof is engaged with an annular step portion formed in said valve chamber.
  • the main body portion is provided with a valve chamber, and a valve body guide arranged in said valve chamber, wherein said valve body guide is provided with an outer circumferential side wall contacting with said valve chamber and an inner circumferential side wall with which said valve body is contacted, said inner circumferential side wall being provided with a large number of grooves extending in the direction of flow.
  • the main body portion is provided with an operating rod for actuating the valve body in an interlocking manner in relative to the movement of the diaphragm, and with a slide hole for allowing the operating rod to slidably move therein, wherein the operating rod and the slide hole are designed to be partially contacted with each other, thus forming a partial sliding surface therebetween.
  • the main body portion is provided on the outer circumferential wall thereof with a plurality of annular stepped portions which are diametrally reduced stepwise and are respectively fitted with an annular sealing member, the annular stepped portions being adapted to be engaged with a plurality of annular stepped portions which are diametrally reduced and formed on the inner wall of the engaging hole provided in the variable capacity compressor.
  • the pressure controlling valve of the present invention is constructed such that the diaphragm is held between the upper lid and the lower lid, that the fitting portion, the annular projection and the diaphragm are simultaneously caulked together, and that a space between the annular projection and the upper lid is hermetically sealed by means of soldering, the air-tightness of the pressure responding motive portion can be improved.
  • the pressure responding motive portion can be always prevented from being influenced by any changes in air atmosphere and temperature, so that works such as the exhaustion or gas filling by making use of a capillary tube, the sealing of the capillary tube, etc. can be dispensed with, thus facilitating the manufacture and adjustment of the pressure adjusting valve as compared with the conventional pressure adjusting valve.
  • any special supporting member such as a valve guard for supporting the ball valve is no more required.
  • the main body portion of the pressure adjusting valve is provided on the outer circumferential wall thereof with a plurality of annular stepped portions which are diametrally reduced stepwise and are respectively fitted with an annular sealing member for engagement, the cost for manufacturing the pressure adjusting valve can be reduced.
  • FIG. 1 illustrates one embodiment of the present invention, wherein this pressure adjusting valve 1 is constituted by a pressure responding motive portion 10 and a main body portion 20.
  • the pressure responding motive portion 10 attached to the upper end of the main body portion 20 comprises an upper lid (made of brass) 12 retaining a diaphragm (made of beryllium copper) 11 which is sandwiched between the upper lid 12 and a lower lid 22 integrally attached to the main body portion (made of brass) 20, and a case 13 which is integrally mounted on the upper lid 12.
  • the main body portion 20 comprises an operating rod 24 contacted with the diaphragm 11, and a slide hole 28 formed passing through the main body portion 20.
  • a pressure chamber 21 is formed at a portion of the main body portion 20 where one end of the operating rod 24 is located, and is provided with an inlet port 29 for introducing a suction pressure.
  • the other end of the operating rod 24 is extended to the valve chamber 23 in which a ball valve 25 contacted with the other end of the operating rod 24, a valve seat 27 provided with a communicating hole for valve chamber 23, and a ball valve-retaining spring 26 being set so as to urge the ball valve 25 in the direction to close the passageway are provided.
  • a feeding port 30 for feeding a pressure inside the crankcase is formed over the valve chamber 23, and an inlet port 31 for introducing a discharge pressure is formed below the valve chamber 23.
  • the pressure adjusting valve 1 is designed to detect the suction pressure Ps and to control the pressure Pc inside the crankcase thereby to alter the magnitude of stroke of the piston 84, thus maintaining the pressure of the evaporator D.
  • this connection is effected through a combination between the upper lid 12 of the pressure responding motive portion 10 and the lower lid 22 of the main body portion 20.
  • the lower lid 22 is provided with a cylindrical fitting portion 33 and an annular projection 34 for caulking.
  • This fitting portion 33 is cylindrical in configuration being formed coaxial with the longitudinal axis of the slide hole 28 of the main body portion.
  • the upper lid 12 having a cylindrical configuration is coaxially fitted in the inner circumferential wall portion of the lower lid 22.
  • the annular projection 34 is cylindrical in configuration and formed coaxial with the longitudinal axis of the slide hole 28 of the main body portion. This annular projection 34 is made thinner in the radial direction than the fitting portion 33.
  • the diaphragm 11 is held between the outer circumferential wall of the upper lid 12 and the inner circumferential wall of the lower lid 22.
  • the fitting portion 33, the annular projection 34 and the diaphragm 11 are integrally bent innerward or in the direction directed from the outer circumferential wall of the lower lid 22 to the inner circumferential wall thereof, thereby coupling the diaphragm 11 and the fitting portion 33 with the upper lid 12 in conformity with the shape of the upper lid 12.
  • This caulking is performed in such a manner that a space S is formed between the annular projection 34 and the upper lid 12. Then, a solder is filled in this space S thereby fill the space S with the solder, thus more completely sealing this caulked portion.
  • This annular projection 34 is extended longer than the outermost brim portion lla of the diaphragm after the aforementioned caulking, and provided on the inner circumferential wall thereof with a stepped portion 34a which is prevented from contacting with the outermost brim portion lla of the diaphragm.
  • this annular projection 34 is that if the outermost brim portion lla is extended longer than the annular projection 34, or if the outermost brim portion lla is contacted with the annular projection 34, a pressure leakage may be generated after the soldering.
  • the aforementioned annular projection 34 may be formed on the upper lid 12, and the upper lid 12 and the diaphragm 11 may be integrally caulked against the lower lid 22, thereby obtaining a hermetically sealed pressure adjusting valve.
  • the ball valve-retaining spring 26 which is set so as to urge the ball valve 25 in the direction to close the passageway is formed of a conical coil spring having a small diametral side 35 and a large diametral side 36.
  • the end face of the small diametral side 35 is flattened by means of polishing, while the terminal end portion at the large diametral side 36 of the spring is directed innerward in the radial direction thereof.
  • the ball valve 25 is directly supported by the small diametral side 35 of the ball valve-retaining spring 26.
  • the ball valve 25 may be integrally connected with the ball valve-retaining spring 26 by spot-welding the contacting portion between the ball valve 25 and the small diametral side 35 of the ball valve-retaining spring 26.
  • the valve chamber 23 is provided with a tapered portion 37 formed in the vicinity of the discharge pressure-introducing port 31 and tapering in the direction directed from the outside of the discharge pressure-introducing port 31 to the inner wall of the valve chamber 23, and a stepped portion 38 formed between the terminal portion of the tapered portion 37 and the inner wall of the valve chamber 23.
  • the ball valve-retaining spring 26 can be set in place as follows. Namely, after the ball valve 25 is introduced into the valve chamber 23, the ball valve-retaining spring 26 is introduced into the valve chamber 23 while forcing the large diametral side 36 thereof to shrink in radial direction along the tapered portion 37. The ball valve-retaining spring 26 introduced in this manner into the valve chamber 23 is then fixedly mounted on the stepped portion 38 by taking advantage of the restoring force of the spring. By the way, the terminal end portion of the large diametral side 36 of the spring, which is directed innerward in the radial direction, is prevented from being contacted with the tapered portion 37 and makes it easy to mount the ball valve-retaining spring 26 in the valve chamber 23.
  • the ball valve 25 is punched using a jig (not shown) which can be introduced through the discharge pressure-introducing port 31, thereby causing the shape of the ball valve 25 to conform with the shape of the valve seat 27, thus minimizing the generation of valve leakage.
  • the outer circumferential wall of a portion of the operating rod 24 which is located to face the slide hole portion of the main body portion is provided with a large number of annual grooves 44, thus providing the operating rod 24 with portions which are contacted with the slide hole 28 and also with portions which are not contacted with the slide hole 28.
  • a labyrinth effect can be generated in a fluid flowing through a clearance between the operating rod 24 and the slide hole 28 thereby to minimize a clearance leakage between the suction pressure inlet port 29 and the feeding port 30.
  • a strainer 39 is attached to the inner wall of suction pressure inlet port 29 by means of press-fitting or screwing, and additionally, strainers 40 and 41 are also attached to the outer walls of feeding port 30 and of the discharge pressure-introducing port 31 by means of press-fitting.
  • the pressure-setting spring 16 mounted in the pressure responding motive portion 10 is constituted by a cylindrical coil spring, both end faces of which are flattened by means of polishing. These end faces are supported, via a convex spring shoes 15 being faced to each other and disposed coaxial with the spring, by a convex adjusting screw 17 disposed at the top of the spring 16 and facing downward and by the upper reinforcing plate 14 disposed at the bottom of the spring 16.
  • the axial alignment of the pressure-setting spring 16 can be automatically effected, thereby making it possible to render the force of the spring 16 to be perpendicularly acted on the ball valve 25 through the operating rod 24, and to stabilize the movement of the operating rod 24 against changes in pressure of the pressure chamber 21.
  • FIGS. 2a and 2b illustrate an embodiment where a valve guide 42 for guiding the movement of the ball valve 25 is provided in the valve chamber 23 of the pressure adjusting valve 1.
  • the valve guide 42 is cylindrical in configuration and the outer circumferential wall 42a thereof is contacted with the inner wall of the valve chamber 23, while the inner circumferential wall 42b thereof is contacted with the circumferential line of the ball valve 25, thereby to prevent the generation of rocking movement and the accompanying vibration and noise, thus stabilizing the movement of the ball valve 25.
  • FIG. 2b is a cross-sectional view taken along the line X-X of FIG. 2a, and illustrates that the valve guide 42 is provided with grooves 43 functioning as a fluid passageway.
  • These grooves 43 are formed in the inner circumferential wall of the valve guide 42 and are parallel with the flow line and formed equidistantly as viewed in the circumferential direction. The provision of these grooves 43 is effective in rectifying the liquid flow, in homogenizing the force acting on the ball valve 25, and in further improving the stability in movement of the ball valve 25.
  • this valve guide 42 may be formed integral with or separate from the valve chamber 23.
  • FIG. 3 illustrates the sliding surface between the operating rod 24 and the slide hole 28.
  • This operating rod 24 is permitted to move up and down within the slide hole 28 of the main body portion in conformity with changes in pressure of the pressure chamber 21, thereby opening or closing the ball valve 25. If the contacting area between the operating rod 24 and the slide hole 28 is large in this case, the frictional resistance at the occasion of sliding would be increased. Therefore, either a stepped rod 44 (FIG. 3a) where every portions of the operating rod 24 except both end portions 24a and 24b are made smaller in diameter, or a stepped hole 45 (FIG.
  • FIG. 4 illustrates another embodiment of the present invention, wherein this pressure adjusting valve la is constituted by a pressure responding motive portion 10 and a main body portion 20.
  • the pressure responding motive portion 10 attached to the upper end of the main body portion 20 comprises an upper lid 12 or shell (made of copper) retaining a diaphragm (made of beryllium copper) 11 which is sandwiched between the upper lid 12 and a lower lid 22 or shell (made of copper) integrally attached to the main body portion 20, and a case 13 which is integrally mounted on the upper lid 12 or shell.
  • a spring 16 is interposed between the upper end portion 15 of the spring case 13 and an upper reinforcing plate 14 of the diaphragm 11, the spring 16 urging a ball valve 25 in the direction to open the passageway.
  • the main body portion 20 comprises a lower lid 22 or shell, a main valve body 50 (made of brass), an operating rod 24 contacted with the diaphragm 11, and a slide hole 28 formed passing through the main body portion 20.
  • a pressure chamber 21 is formed at a portion of the main body portion 20 where one end of the operating rod 24 is located, and is provided with an inlet port 29 for introducing a suction pressure.
  • the other end of the operating rod 24 is extended to the valve chamber 23 in which there are disposed a ball valve 25 contacted with the other end of the operating rod 24, a valve seat 27 provided with a communicating hole for valve chamber 23, and a pressure-setting/ball valve-retaining spring 26 being interposed between the valve guard contacting with the ball valve 25 and the adjusting spring stopper 46 screwed into the valve chamber 23, and set so as to urge the ball valve 25 in the direction to close the passageway.
  • a feeding port 30 for feeding a pressure inside the crankcase is formed over the valve chamber 23, and an inlet port 31 for introducing a discharge pressure is formed below the valve chamber 23.
  • the pressure adjusting valve la is designed to detect the suction pressure Ps and to control the pressure Pc inside the crankcase thereby to alter the magnitude of stroke of the piston 84, thus maintaining the pressure of the evaporator D.
  • this connection is effected through a combination between the upper lid 12 or shell of the pressure responding motive portion 10 and the lower lid 22 or shell of the main body portion 20.
  • the upper lid 12 and lower lid 22 are both cylindrical in configuration being formed coaxial with the longitudinal axis of the slide hole 28 of the main body portion. These upper and lower lids 12 and 22 are formed by means of press molding.
  • the spring case 13 formed integral with the upper lid 12 or shell is assembled with a spring urging the ball valve 25 in the direction to open the passageway and with an upper reinforcing plate 14. Then, the main valve body 50 provided with the ball valve 25 and the operating rod 24 is fitted in the lower lid 22 or shell, after which the diaphragm 11 is held between the shells, i.e. the upper lid 12 and the lower lid 22.
  • the brim portions W of the diaphragm 11, the upper lid 12 and the lower lid 22 are simultaneously welded by means of electron beam welding (EBW). Since the electron beam welding is performed in vacuum in general, the interior of the spring case 13 becomes vacuum at the moment of finishing the welding. Therefore, the pressure responding motive portion 10 can be always prevented from being influenced by any changes in air atmosphere and temperature. By the way, since the electron beam welding is minimal in welding heat and in strain of the welded portion, the electron beam welding is advantageous in these respects.
  • EBW electron beam welding
  • these shells constituting the upper and lower lids 12 and 22 of the pressure adjusting valve la according to this embodiment are connected together by making use of the electron beam welding, a material (copper) which is different from the material (brass) of the main valve body 50 is employed for these shells.
  • the fixing of the shell (the lower lid 22) to the main valve body 50 can be performed by a process wherein the main valve body 50 provided with an annual groove is fitted in the shell at first, and then the outer circumferential wall of the shell is contractingly caulked toward the circumferential groove of the main valve body 50 by making use of a three-piece jig for instance thereby to coupling the shell with the main valve body 50.
  • the contracting caulking is performed after fitting the main valve body 50 provided with circumferential grooves 49a and 49b in the shell as shown in FIG. 4, the air-tightness of intermediate portions among the suction pressure inlet port 29, the feeding port 30 and the discharge pressure-introducing port 31 can be realized.
  • the spring 26 can be functioned as a ball valve-retaining spring and at the same time, as a pressure adjusting spring.
  • the groove 51' for an O-ring is respectively formed on an outer circumferential wall portion of the main body portion between the suction pressure-introducing inlet port 29' and the crankcase inner pressure feeding port 30', as well as between the crankcase inner pressure feeding port 30' and the discharge pressure inlet port 31', and after attaching the O-ring 52 to the grooves 51' in advance, the resultant pressure adjusting valve 1' is assembled with the compressor A.
  • FIG. 5 shows an air-tight structure according to this embodiment, wherein the groove 51' for an O-ring is totally dispensed with in a pressure adjusting valve, and instead, the pressure adjusting valve la provided with stepped portions 48 which are gradually lowered in level in the direction from the suction pressure-introducing inlet port 29 to the discharge pressure inlet port 31 is assembled with the compressor A.
  • the compressor A is provided on the inner circumferential wall thereof with the stepped portions 55a to 55d to be fitted with the configuration of the stepped portions 48 formed on the outer circumferential wall of the main body portion of the pressure adjusting valve la, and each pressure at the suction pressure-introducing inlet port 29, at the crankcase inner pressure feeding port 30 and at the discharge pressure inlet port 31 is separated from the others by attaching the O-ring 52 to each engaging portion, thereby realizing an air-tightness between the pressure adjusting valve la and the compressor A.
  • FIG. 6 illustrates still another embodiment of the present invention, wherein this pressure adjusting valve 1b is constituted by a pressure responding motive portion 10 and a main body portion 20.
  • the pressure responding motive portion 10 attached to the upper end of the main body portion 20 comprises an upper lid 12 (made of copper) retaining a diaphragm (made of beryllium copper) 11 which is sandwiched between the upper lid 12 and a lower lid 22 integrally attached to the main body portion 20, and a case 13 which is integrally mounted on the upper lid 12 or shell.
  • a spring 16 is interposed between the upper end portion 15 of the spring case 13 and an upper reinforcing plate 14 of the diaphragm 11, the spring 16 urging a ball valve 25 in the direction to open the passageway.
  • the main body portion 20 comprises an operating rod 24 contacted with the diaphragm 11, and a slide hole 28 formed passing through the main body portion 20.
  • a pressure chamber 21 is formed at a portion of the main body portion 20 where one end of the operating rod 24 is located, and is provided with an inlet port 29 for introducing a suction pressure.
  • the other end of the operating rod 24 is extended to the valve chamber 23 in which there are disposed a ball valve 25 contacted with the other end of the operating rod 24, a valve seat 53 provided with a communicating hole for valve chamber 23, and a pressure-setting/ball valve-retaining spring 26 being interposed between the valve guard contacting with the ball valve 25 and the adjusting spring stopper 46 screwed into the valve chamber 23, and set so as to urge the ball valve 25 in the direction to close the passageway.
  • a feeding port 30 for feeding a pressure inside the crankcase is formed over the valve chamber 23, and an inlet port 31 for introducing a discharge pressure is formed below the valve chamber 23.
  • the pressure adjusting valve 1b is designed to detect the suction pressure Ps and to control the pressure Pc inside the crankcase thereby to alter the magnitude of stroke of the piston 84, thus maintaining the pressure of the evaporator D.
  • connection between the pressure responding motive portion 10 and the main body portion 20 in the pressure controlling valve 1b will be explained. Namely, this connection is effected through a combination between the upper lid 12 of the pressure responding motive portion 10 and the lower lid 22 of the main body portion 20.
  • the upper lid 12 and lower lid 22 are both cylindrical in configuration being formed coaxial with the longitudinal axis of the slide hole 28 of the main body portion 20. These upper and lower lids 12 and 22 are formed by means of press molding or cutting.
  • the spring case 13 formed integral with the upper lid 12 is assembled with a spring urging the ball valve 25 in the direction to open the passageway and with an upper reinforcing plate 14.
  • the operating rod 24 is fitted in the main body portion 20 integrally formed with the lower lid 22, after which the diaphragm 11 is held between the upper lid 12 and the lower lid 22. Thereafter, the brim portions W of the diaphragm 11, the upper lid 12 and the lower lid 22 are simultaneously welded by means of electron beam welding (EBW).
  • EBW electron beam welding
  • valve seat 53 and a collar 54 each formed of a material different from that of the main body portion 20 are disposed in the valve chamber 23 and the slide hole 28.
  • the valve seat 53 formed of a hard material such as brass, SUS, etc.
  • the collar 54 such as brass, resin, etc.
  • the pressure responding motive portion 10 can be always prevented from being influenced by any changes in air atmosphere and temperature, so that works such as the exhaustion or gas filling by making use of a capillary tube, the sealing of the capillary tube, etc. can be dispensed with, thus facilitating the manufacture and adjustment of the pressure adjusting valve as compared with the conventional pressure adjusting valve.
  • the end face of the small diametral side 35 of the ball valve-retaining spring 26 is flattened by means of polishing and then used to directly support the ball valve 25, the seating of the ball valve 25 can be stabilized, thus making it possible to omit the employment of special member such as a valve guard for supporting the ball valve 25.
  • the contacting portion between the ball valve-retaining spring 26 and the ball valve 25 is spot-welded to integrally connect the ball valve-retaining spring 26 and the ball valve 25, the separation of the ball valve 25 from the ball valve-retaining spring 26 can be prevented even if the ball valve 25 is suddenly opened or closed.
  • a tapered portion 37 tapering in the direction directed from the outside of the discharge pressure-introducing port 31 to the inner wall of the valve chamber 23 the mounting of the ball valve-retaining spring 26 can be facilitated, and the ball valve-retaining spring 26 can be prevented from falling out due to the stepped portion to be formed between the small diametral end portion of the tapered portion 37 and the inner wall of the valve chamber 23.
  • a supporting member such as a spring shoe, or a caulking work for fixing the spring shoe can be dispensed with.
  • the compressor A is provided on the inner circumferential wall thereof with stepped portions fitting the shape of the stepped portion 48 formed on the outer circumferential wall of the pressure adjusting valve la, and the O-ring 52 is placed at the engaging portions of these stepped portions, it is possible to reduce the cost for manufacturing the pressure adjusting valve.
  • the pressure adjusting valve according to the present invention is designed such that the upper lid or the lower lid is closely sealed with the diaphragm by means of caulking and additional soldering, or by means of electron beam welding, the reliability in air-tightness of the pressure responding motive portion can be improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP19990111549 1999-06-15 1999-06-15 Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau Expired - Lifetime EP1061257B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE69923437T DE69923437T2 (de) 1999-06-15 1999-06-15 Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau
EP19990111549 EP1061257B1 (de) 1999-06-15 1999-06-15 Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19990111549 EP1061257B1 (de) 1999-06-15 1999-06-15 Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau

Publications (2)

Publication Number Publication Date
EP1061257A1 true EP1061257A1 (de) 2000-12-20
EP1061257B1 EP1061257B1 (de) 2005-01-26

Family

ID=8238356

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19990111549 Expired - Lifetime EP1061257B1 (de) 1999-06-15 1999-06-15 Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau

Country Status (2)

Country Link
EP (1) EP1061257B1 (de)
DE (1) DE69923437T2 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2836521A1 (fr) * 2002-02-28 2003-08-29 Taiheiyo Kogyo Kk Distributeur de commande d'un compresseur a deplacement variable, et son procede de fabrication
EP1420162A2 (de) * 2002-11-14 2004-05-19 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen verstellbaren Taumelscheibenkompressor
EP1520987A1 (de) * 2003-09-30 2005-04-06 Fujikoki Corporation Ventil
CN100441876C (zh) * 2004-06-21 2008-12-10 乐金电子(天津)电器有限公司 旋转式压缩机的容量可变装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5039876A (de) 1973-08-11 1975-04-12
US4585174A (en) * 1983-04-02 1986-04-29 Robert Bosch Gmbh Electro-magnetically operable valve
US4723891A (en) * 1986-04-09 1988-02-09 Toyoda Jidoshokki Seisakusho Kabushiki Kaisha Variable displacement wobble plate type compressor with improved crankcase pressure control system
US4924905A (en) * 1975-06-30 1990-05-15 Michael Mastromatteo Control devices
EP0537776A1 (de) * 1991-10-17 1993-04-21 Eaton Corporation Temperaturabhängiges Expansionsventil
US5245753A (en) * 1991-05-15 1993-09-21 Mitsuba Electric Manufacturing Co., Ltd. Method of manufacturing pressure control valve
EP0748936A1 (de) * 1995-06-05 1996-12-18 Calsonic Corporation Schiefscheibenverdichter mit veränderlicher Verdrängung
US5620310A (en) * 1993-01-11 1997-04-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for a variable displacement refrigerant compressor
US5680703A (en) * 1995-12-25 1997-10-28 Mitsuba Corporation Method of manufacturing pressure regulator
US5799499A (en) * 1995-09-27 1998-09-01 Fujikoki Corporation Combined unit of expansion valve and reservoir tank

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5039876A (de) 1973-08-11 1975-04-12
US4924905A (en) * 1975-06-30 1990-05-15 Michael Mastromatteo Control devices
US4585174A (en) * 1983-04-02 1986-04-29 Robert Bosch Gmbh Electro-magnetically operable valve
US4723891A (en) * 1986-04-09 1988-02-09 Toyoda Jidoshokki Seisakusho Kabushiki Kaisha Variable displacement wobble plate type compressor with improved crankcase pressure control system
US5245753A (en) * 1991-05-15 1993-09-21 Mitsuba Electric Manufacturing Co., Ltd. Method of manufacturing pressure control valve
EP0537776A1 (de) * 1991-10-17 1993-04-21 Eaton Corporation Temperaturabhängiges Expansionsventil
US5620310A (en) * 1993-01-11 1997-04-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for a variable displacement refrigerant compressor
EP0748936A1 (de) * 1995-06-05 1996-12-18 Calsonic Corporation Schiefscheibenverdichter mit veränderlicher Verdrängung
US5799499A (en) * 1995-09-27 1998-09-01 Fujikoki Corporation Combined unit of expansion valve and reservoir tank
US5680703A (en) * 1995-12-25 1997-10-28 Mitsuba Corporation Method of manufacturing pressure regulator

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2836521A1 (fr) * 2002-02-28 2003-08-29 Taiheiyo Kogyo Kk Distributeur de commande d'un compresseur a deplacement variable, et son procede de fabrication
EP1420162A2 (de) * 2002-11-14 2004-05-19 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen verstellbaren Taumelscheibenkompressor
EP1420162A3 (de) * 2002-11-14 2004-09-15 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen verstellbaren Taumelscheibenkompressor
EP1520987A1 (de) * 2003-09-30 2005-04-06 Fujikoki Corporation Ventil
CN100441876C (zh) * 2004-06-21 2008-12-10 乐金电子(天津)电器有限公司 旋转式压缩机的容量可变装置

Also Published As

Publication number Publication date
EP1061257B1 (de) 2005-01-26
DE69923437D1 (de) 2005-03-03
DE69923437T2 (de) 2006-03-30

Similar Documents

Publication Publication Date Title
US6105928A (en) Pressure adjusting valve for variable capacity compressors
US6626645B2 (en) Control valve for variable capacity compressors
US4723891A (en) Variable displacement wobble plate type compressor with improved crankcase pressure control system
US6146106A (en) Electromagnetic valve
KR100323264B1 (ko) 필터가 장착된 유체 기계
US9903352B2 (en) Swash plate type variable displacement compressor
US5975859A (en) Control valve in variable displacement compressor and its assembling method
US8241012B2 (en) Structure for mounting a filter in a compressor
US6217292B1 (en) Variable displacement type refrigerant compressor
AU646336B2 (en) Slant plate type compressor with variable displacement mechanism
US6280152B1 (en) Variable-type swash plate compressor having a cock member for fixed capacity operation and manufacturing method therefor
US6688853B1 (en) Control valve for regulating flow between two chambers relative to another chamber
KR100858604B1 (ko) 가변용량형 압축기용 제어밸브
EP1061257B1 (de) Regelventil für Taumelscheibenkompressor mit veränderlicher Förderleistung und Verfahren für den Zusammenbau
US5255569A (en) Slant plate type compressor with variable displacement mechanism
US10815980B2 (en) Variable displacement swash plate type compressor
JP4173980B2 (ja) 可変容量型圧縮機用の制御弁
JP4082802B2 (ja) 可変容量型圧縮機用制御弁
JP3461343B2 (ja) 可変容量型圧縮機用の制御弁
KR20010079737A (ko) 용량가변형 압축기용 제어밸브
JP3547858B2 (ja) 圧力調整弁
JP4247225B2 (ja) 可変容量型圧縮機用の制御弁
JP3847617B2 (ja) 可変容量型圧縮機用の制御弁
JP6469994B2 (ja) 圧縮機
US11015587B2 (en) Piston compressor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT NL

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20010118

AKX Designation fees paid

Free format text: DE ES FR GB IT NL

17Q First examination report despatched

Effective date: 20030729

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT NL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050126

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 69923437

Country of ref document: DE

Date of ref document: 20050303

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050507

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20050609

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20050615

Year of fee payment: 7

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ET Fr: translation filed
26N No opposition filed

Effective date: 20051027

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20060103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060615

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20060630

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070103

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20060615

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20070630

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070615

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060630