EP0959227A2 - Kolben und Verfahren zur Herstellung - Google Patents

Kolben und Verfahren zur Herstellung Download PDF

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Publication number
EP0959227A2
EP0959227A2 EP99109847A EP99109847A EP0959227A2 EP 0959227 A2 EP0959227 A2 EP 0959227A2 EP 99109847 A EP99109847 A EP 99109847A EP 99109847 A EP99109847 A EP 99109847A EP 0959227 A2 EP0959227 A2 EP 0959227A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
lid
piston
skirt
head
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.)
Withdrawn
Application number
EP99109847A
Other languages
English (en)
French (fr)
Other versions
EP0959227A3 (de
Inventor
Takayuki c/o Toyoda Jidoshokki Seisakusho Kato
Takahiro c/o Toyoda Jidoshokki Seisakus. Sugioka
Masato c/o Toyoda Jidoshokki Seisakus. Takamatsu
Tsunehisa Sekiguchi
Masaki Ando
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.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP0959227A2 publication Critical patent/EP0959227A2/de
Publication of EP0959227A3 publication Critical patent/EP0959227A3/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—Pistons

Definitions

  • the present invention relates to pistons for compressors that are used in vehicle air conditioners and to a method for manufacturing the pistons.
  • a typical compressor includes a cylinder block, which constitutes a part of the compressor housing. Cylinder bores are formed in the cylinder block. Each cylinder bore reciprocally houses a piston. Each piston has a metal head accommodated in the associated cylinder bore and a metal skirt coupled to a driving body (for example, a swash plate in a swash plate type compressor) .
  • the head includes a hollow cylinder with a closed end and a lid to close the opening of the cylinder. The lid is integrally formed with the skirt.
  • Such pistons are known as hollow pistons.
  • hollow pistons In comparison to solid pistons, which have solid heads, hollow pistons are light. Using hollow pistons therefore reduces weight.
  • the head and the skirt of a solid piston are integrally formed, for example, by casting.
  • the cylinder and the lid of a hollow piston must be separately formed and welded together.
  • the cylinder and the lid of a hollow piston are welded by electron-beam welding.
  • electron-beam welding a highly accelerated electron-beam is irradiated onto parts to be welded in a vacuum welding chamber.
  • electron-beam welding has the following drawbacks.
  • a method for manufacturing a piston that cooperates with a driving body in a machine is provided.
  • the piston has a skirt and a head.
  • the skirt serves to connect the piston to the driving body
  • the head includes a cylinder having at least one open end and a lid closing the open end.
  • the method includes friction welding the lid to the cylinder.
  • the present invention is also embodied in a piston for cooperating with a driving body in a machine.
  • the piston includes a skirt serving to connect the piston to the driving body and a head.
  • the head includes a cylinder having at least one open end and a lid for closing the open end. The lid is friction welded to the cylinder.
  • Pistons according to a first embodiment will now be described with reference to Figs. 1-3.
  • the pistons are used in variable displacement compressors for vehicle air conditioners.
  • a front housing 11 and a rear housing 13 are secured to a cylinder block 12.
  • a valve plate 14 is located between the cylinder block 12 and the rear housing 13.
  • a crank chamber 15 is defined by the inner walls of the front housing 11 and the front end face of the cylinder block 12.
  • a drive shaft 16 is rotatably supported by the front housing 11 and the cylinder block 12.
  • the drive shaft 16 is coupled to an external drive source (not shown), or a vehicle engine, by a clutch mechanism such as an electromagnetic clutch. When the engine is running, the clutch operably connects the shaft 16 with the engine thereby rotating the shaft 16.
  • a rotor 19 is fixed to the drive shaft 16 in the crank chamber 15.
  • the crank chamber 15 also accommodates a swash plate 20.
  • the swash plate 20 is supported on the drive shaft 16 to slide along the drive shaft 16 and incline with respect to the axis L of the drive shaft 16.
  • a hinge mechanism 21 is located between the rotor 19 and the swash plate 20 to rotate the swash plate 20 integrally with the drive shaft 16.
  • the hinge mechanism 21 guides the movement of the swash plate 20 in the axial direction of the drive shaft 16 and the inclination of the swash plate 20 with respect to the drive shaft 16.
  • the inclination of the swash plate 20 decreases as the swash plate 20 moves toward the cylinder block 12 and increases as the swash plate 20 moves toward the rotor 19.
  • Cylinder bores 12a are formed in the cylinder block 12. Each cylinder bore 12a houses a single-headed hollow piston 22. Each piston 22 is coupled to the swash plate 20 by way of a pair of shoes 23. The shoes 23 convert rotation of the swash plate 20 into reciprocation of each piston 22 in the associated cylinder bore 12a.
  • a suction chamber 24 and a discharge chamber 25 are defined in the rear housing 13.
  • the valve plate 14 has suction ports 26, suction valve flaps 27, discharge ports 28 and discharge valve flaps 29.
  • Each set of ports 26, 28 and valve flaps 27, 29 corresponds to one of the cylinder bores 12a.
  • refrigerant gas is drawn into the corresponding suction port 26 from the suction chamber 24 thereby opening the suction flap 27 to enter the associated cylinder bore 12a.
  • the gas in the cylinder bores 12a is compressed to a predetermined pressure. The gas is then discharged to the discharge chamber 28 through the associated discharge port 28 while causing the associated valve flap 29 to flex to an open position.
  • a bleeding passage 30 includes a passage 30a formed in the drive shaft 16 along its axis and a passage 30b formed in the cylinder block 12 and the valve plate 14.
  • the bleeding passage 30 connects the crank chamber 15 with the suction chamber 24.
  • a supply passage 31 connects the discharge chamber 25 with the crank chamber 15.
  • a displacement control valve 32 is accommodated in the rear housing 13 to regulate the supply passage 31.
  • the displacement control valve 32 includes a solenoid 32a and a valve body 32b. Excitation and de-excitation of the solenoid 32a causes the valve body 32b to open and close the supply passage 31.
  • the control valve 32 is connected to a computer (not shown). The computer excites and de-excites the solenoid 32a in accordance with the cooling load, which moves the valve body 32b. Accordingly, the control valve 32 regulates flow of refrigerant gas from the discharge chamber 25 to the crank chamber 15, which controls the difference between the pressure of the crank chamber 15 and the pressure of the cylinder bores 12a.
  • the inclination of the swash plate 20 is altered in accordance with changes in the pressure difference. This, in turn, alters the stroke of the pistons 22 and varies the displacement of the compressor.
  • valve body 32b opens the supply passage 31 thereby communicating the discharge chamber 25 with the crank chamber 15.
  • the refrigerant gas in the discharge chamber 25 therefore flows into the crank chamber 15 through the supply passage 31, which raises the pressure in the crank chamber 15.
  • the inclination of the swash plate 20 decreases, and the stroke of the pistons 22 decreases, accordingly. This decreases the displacement of the compressor.
  • valve body 32b closes the supply passage 31. This stops the flow of refrigerant gas from the discharge chamber 25 to the crank chamber 15. Refrigerant gas in the crank chamber 15 flows to the suction chamber 24 through the bleeding chamber 30, which lowers the pressure of the crank chamber 15. As a result, the inclination of the swash plate 20 is increased and the stroke of the pistons 22 increases, accordingly. This increases the displacement of the compressor.
  • the inclination of the swash plate 20 is changed in accordance with the changes in the pressure of the crank chamber 15.
  • the stroke of the pistons 22 changes in accordance with the inclination of the swash plate 20.
  • Hollow pistons are relatively light and therefore have a small inertial force when reciprocated. Therefore, when hollow pistons are used, the swash plate 20 can be moved to a desired inclination position without being significantly affected by the inertial force of the pistons 22.
  • each piston 22 will now be described with reference to Figs. 1 to 3.
  • each piston 22 has a head 40 housed in the associated cylinder bore 12a and a skirt 42 coupled to the swash plate 20 by the shoes 23.
  • the head 40 and the skirt 42 are joined to each other to form the piston 22.
  • the head 40 includes a cylinder 41 and a disk-shaped lid 43.
  • the cylinder 41 includes an end plate 41d for closing the end that faces the valve plate 14.
  • a slot 42a which faces the swash plate 20, is provided in the skirt 42.
  • the slot 42a has a pair of opposing walls.
  • a socket 42b is defined in each wall to receive a shoe 23.
  • a pair of shoes 23 are supported by the sockets 42b.
  • the shoes 23 sandwich a peripheral portion of the swash plate 20 as shown in Fig 1.
  • the lid 43 is formed integrally with the skirt 42.
  • a boss 43a extends from the lid 43.
  • the outer diameter of the boss 43a is substantially the same as the outer diameter of the cylinder 41.
  • the inner diameter of the boss 43a is substantially the same as the inner diameter of the cylinder 41.
  • the cylinder 41 and the skirt 42 are made by casting or forging metal such as aluminum or aluminum alloy.
  • the cylinder 41 and the lid 43 are fixed to each other by friction welding.
  • the cylinder 41 and the skirt 42 are aligned such that the end surface 41b of the cylinder 41 faces the end surface 43b of the boss 43a.
  • Either the cylinder 41 or the skirt 42 is rotated relative to the other about an axis S of the piston 22.
  • the cylinder 41 and the skirt 42 are then brought into contact with each other.
  • the relative rotational speed of the cylinder 41 and the skirt 42 and the contact pressure between the cylinder 41 and the skirt 42 change as shown in the graph of Fig. 3.
  • the cylinder 41 is welded to the skirt 42 under atmospheric pressure. Therefore, when the joint between cylinder 41 and the skirt 42 is heated, the metal forming the cylinder 41 and the skirt 42 is not deteriorated by bubbles.
  • Figs. 1 to 3 has the following advantages.
  • Figs. 4 to 5D illustrate a method for assembling a piston according to a second embodiment.
  • the differences from the embodiment of Figs. 1-3 will mainly be discussed below.
  • the outer diameter of the boss 43a is substantially the same as the inner diameter of the cylinder 41.
  • Annular grooves 43c are formed in the outer surface of the boss 43a.
  • the cylinder 41 and the skirt 42 are fixed to each other by plastic flow and adhesive.
  • Adhesive is applied to the circumference of the boss 43a and to the part of the lid 43 that faces the adjacent end surface 41b of the cylinder 41.
  • the adhesive is, for example, resin adhesive such as epoxy, polyamide or vinyl acetate.
  • the skirt 42 is attached to the cylinder 41 such that the lid 43 closes the inner space 41a of the cylinder 41.
  • the outer circumferential surface of the boss 43a contacts the inner wall of the cylinder 41, and the lid 43 contacts the end surface 41b of the cylinder 41.
  • the cylinder 41 and the lid 43 are passed through a die 201, the inner diameter of which is slightly smaller than the outer diameter of the cylinder 41 and the lid 43.
  • the die 201 strongly presses the cylinder 41 against the boss 43a, which causes plastic flow of the metal forming the cylinder 41 into the grooves 43c.
  • the adhesive reinforces the joint between the cylinder 41 and the skirt 42.
  • the cylinder 41 is fixed to the skirt 42 under atmospheric pressure. Therefore, the metal forming the cylinder 41 and the skirt 42 is not deteriorated by bubbles.
  • Fig. 5A the difference between the inner diameter of the die 201 and the outer diameter of the cylinder 41 and the lid 43 is illustrated in an exaggerated manner.
  • the embodiment of Figs. 4 to 5D reduces the manufacturing cost and shortens the manufacturing time. Also, the embodiment of Figs. 4 to 5D has the following advantages.
  • the cylinder 41 and the skirt 42 may be assembled without using adhesive. That is, the cylinder 41 and the skirt 42 may be joined only by plastic flow.
  • Figs. 6A to 6D illustrate a method for assembling a piston according to a third embodiment.
  • the differences from the embodiment of Figs. 4 to 5D will mainly be discussed below.
  • the boss 43a of the embodiment of Figs. 6A to 6D has no annular grooves 43c.
  • solder R fills the space between the cylinder 41 and the boss 43a.
  • the solder R is an alloy having a lower melting point than that of the metal forming the cylinder 41 and the skirt 42.
  • the solder R may be applied either to the cylinder 41 or to the boss 43a prior to the assembly.
  • the solder R may be formed like a ring and be fitted to the cylinder 41 or the boss 43a.
  • cylinder 41 or the lid 43 may be coated with powdered solder R.
  • a die 201 is used in the embodiment of Figs. 6A to 6D.
  • the die 201 strongly presses the cylinder 41 against the boss 43a thereby causing a plastic flow between the cylinder 41 and the boss 43a.
  • This creates a number of lattice defects in the metal forming the cylinder 41 and the skirt 42. In other words, holes are formed in the metal.
  • the atoms of the metal forming the cylinder 41 enter the lattice defects in the skirt 42, and the atoms of the metal forming the skirt 42 enter the lattice defects in the cylinder 41.
  • Passing the piston 22 through the die 201 applies pressure to the joint between the cylinder 41 and the skirt 42, thereby generating heat.
  • the pressure and the heat diffuse the solder R thereby causing the solder R to enter the lattice defects.
  • the piston 22 is heated by an external heat source when being passed through the die 201.
  • the heat of the heat source together with the heat caused by the pressure at the joint, raises the temperature of the solder R above its melting point, which liquefies the solder R.
  • the liquefied solder R is diffused at the joint.
  • the external heat may be omitted, in which case a solidus diffusion of the solder R occurs.
  • an alloy layer G is formed at the joint between the cylinder 41 and the skirt 42.
  • the layer G includes the metal forming the cylinder 41 and the skirt 42 and the solder R.
  • the cylinder 41 and the skirt 42 are fixed to each other by the alloy layer G such that there is no boundary between the cylinder 41 and the skirt 42.
  • the inner diameter of the die 201, or the pressure applied to the cylinder 41 and the skirt 42 when the piston 22 is passed through the die 201, is determined such that the strain of the joint between the cylinder 41 and the skirt 42 is three to fifteen percent. For example, if the applied pressure is too small, that is, if the strain of the joint is smaller than three percent, the number of lattice defects will not be sufficient. In other words, there will not be enough holes and the metal atoms in the cylinder 41 and the skirt 42 will not sufficiently interweave. Also, inadequate pressure prevents the solder R from being satisfactorily diffused, which weakens the strength of the joint between the cylinder 41 and the skirt 42.
  • the cylinder 41 Since inadequate pressure slows the diffusion of the solder R, the cylinder 41 must be passed through the die 201 relatively slowly. On the other hand, if the applied pressure is relatively great, that is, if the strain of the joint exceeds fifteen percent, the piston 22 is greatly deformed and the piston 22 will require machining.
  • the joint between the cylinder 41 and the skirt 42 is heated again.
  • the temperature is preferably higher than the melting point of the layer G.
  • the heat promotes the diffusion of the alloy layer G thereby enforcing the joint between the cylinder 41 and the skirt 42.
  • a laser heater or an electron-beam heater may be used to apply the heat to the joint between the cylinder 41 and the lid 43 by.
  • the whole piston 22 may be placed in a furnace.
  • the cylinder 41 and the skirt 42 are manufactured by forging or casting.
  • the cylinder 41 and the skirt 42 are then hardened and tempered. Thereafter, the cylinder 41 is passed through the die 201. Re-heating the piston 22 in a furnace allows the tempering process to be omitted.
  • the cylinder 41 and the skirt 42 are preferably made of the same or different aluminum alloys selected from the alloys specified in Japanese Industrial Standard (JIS) A2017, A2014, A4032, A6063, A6061, A7075, ADC12 and A390.
  • JIS Japanese Industrial Standard
  • the materials that are suitable for the solder R are as follows:
  • the percentage by weight of the first principal component is greater than or equal to the percentage by weight of the second principal component, and the percentage by weight of the second principal component is greater than or equal to the percentage by weight of the third principal component (if a third principle component is present.
  • the percentage by weight of the additives are extremely small relative to those of the principal components.
  • the joint of the cylinder 41 and the skirt 42 is pressed by the die 201. This generates plastic flow at the joint thereby promoting the diffusion of the solder R. Compared to simple soldering in which the joint is not pressed, the embodiment of Figs. 6A to 6D enforces the joint between the cylinder 41 and the skirt 42.
  • a fourth embodiment illustrated in Figs. 7A to 7C the die 201 of the embodiment shown in Figs. 4 to 6D is replaced with rollers 202.
  • the piston 22 is rotated about its axis.
  • the rollers 202 are strongly pressed against the joint between the cylinder 41 and the boss 43a. This generates a plastic flow at the joint.
  • the piston 22 shown in Fig. 7A has grooves formed on the circumference of the boss 43a like the piston 22 of Fig. 4. However, the grooves may be omitted.
  • adhesive may be used in the embodiment of Fig. 7A.
  • solder may be used in the embodiment of Fig. 7A.
  • each roller 202 shown in Fig. 7A is constant along its axis.
  • the surface of the roller 202 is cylindrical.
  • the entire circumferential surface of the roller 202 is pressed against the piston 22.
  • the piston 22 is heated to a relatively high temperature and the rollers 202 are pressed against the piston 22 by relatively small pressure.
  • the assembly takes a relatively long period.
  • the pressing force of the roller 202 per unit area is relatively small, which generates relatively small plastic flow at the joint.
  • the large pressing area of the roller 202 of Fig. 7A and the long assembly time increase the temperature at the joint. Therefore, if used, solder is smoothly diffused.
  • the axial length of the rollers 202 is determined such that the plastic flow at the joint is sufficient to ensure the strength of the joint and that no plastic flow occurs in the other part of the piston.
  • Fig. 7B shows another type of roller 202.
  • the circumferential surface of the roller 202 of Fig. 7B is circularly curved so that the axial center of the roller 202 is recessed.
  • the radius of curvature R2 at the axial ends of the roller 202 may be extremely small.
  • the piston 22 is heated to a relatively low temperature and the rollers 202 are pressed against the piston 22 by a relatively great pressure. Further, the process takes a relatively short time.
  • plastic flow at the joint is highly promoted and the joint is not heated to a high temperature.
  • the shape of the roller 202, specifically a radius of curvature R1 of the recess in the axial center is optimized to effectively generate plastic flow at the joint thereby minimizing the energy required to couple the cylinder 41 with the skirt 42.
  • Fig. 7C shows another type of roller 202.
  • the circumferential surface of the roller 202 of Fig. 7C is tapered by a predetermined angle ⁇ .
  • the piston 22 is heated to a relatively low temperature and the rollers 202 are pressed against the piston 22 by a relatively great pressure. Further, the process is performed in a relatively short time. Plastic flow at the joint is highly promoted and the joint is not heated to a high temperature. The angle ⁇ is optimized to effectively generate plastic flow at the joint thereby minimizing the energy required to couple the cylinder 41 with the skirt 42.
  • the skirt 42 and the head 41 of each piston 22 are integrally formed, and the end plate 41d is separately formed from the cylinder 41.
  • the cylinder 41 and the end plate 41d are coupled to each other by friction welding or plastic flow as shown in Figs. 1 to 7C.
  • Fig. 8 illustrates a method for manufacturing a piston 22 according to a fifth embodiment.
  • the end plate 41d is disk shaped.
  • the end surface 41e of the cylinder 41 and the end surface 41f of the end plate 41d are brought into contact. Then, the cylinder 41 and the end plate 41d are coupled to each other either by friction welding or by plastic flow.
  • Fig. 9 illustrates a piston 22 according to a sixth embodiment.
  • the end plate 41 includes a boss 41g.
  • the outer diameter of the boss 41g is substantially the same as the inner diameter of the cylinder 41.
  • the boss 41g is fitted into the cylinder 41 such that the end surfaces 41e and 41f contact each other. Then, the cylinder 41 and the end plate 41d are coupled to each other either by friction welding or by plastic flow.
  • Fig. 10 illustrates a piston 22 according to a seventh embodiment.
  • a cylindrical portion 41h is integrally formed with the end plate 41.
  • the outer diameter of the cylindrical portion 41h is the same as that of the cylinder 41.
  • the end surface 41m of the cylindrical portion 41h and the end surface 41e of the cylinder 41 are brought into contact. Then, the cylinder 41 and the end plate 41d are coupled to each other either by friction welding or by plastic flow.
  • Fig. 11 illustrates a piston 22 according to an eighth embodiment.
  • the piston 22 of Fig. 11 is a modification of the piston of Fig. 10. That is, the cylindrical portion 41h of the end plate 41d includes a boss 41i. The outer diameter of the boss 41i is smaller than the rest of the cylindrical portion 41h.
  • the cylinder 41 has connector portion 41j formed at the open end. The inner diameter of the connector portion 41j is substantially the same as the outer diameter of the boss 41i.
  • the boss 41i is fitted in the connector portion 41j such that the end surfaces 41e of the cylinder 41 contact the end surfaces 41m of the cylindrical portion 41e. Then, the cylinder 41 and the end plate 41d are coupled to each other either by friction welding or by plastic flow.
  • Fig. 12 illustrates a piston 22 according to a ninth embodiment.
  • the piston 22 of Fig. 12 is a modification of the piston of Fig. 10. That is, the inner diameter of the cylindrical portion 41h is larger than the inner diameter of the cylinder 41.
  • the cylinder 41h includes a boss 41n at the open end. The outer diameter of the boss 41n is substantially the same as the inner diameter of the cylindrical portion 41h.
  • the boss 41n is fitted in the cylindrical portion 41h such that the end surfaces 41e of the cylinder 41 contact the end surfaces 41m of the cylindrical portion 41h. Then, the cylinder 41 and the end plate 41d are coupled to each other either by friction welding or by plastic flow.
  • either the cylinder 41, the skirt 42 or both may be made of metal other than aluminum and aluminum alloy, such as iron, iron alloy, copper or copper alloy.
  • either the cylinder 41, the end plate or both may be made of metal other than aluminum and aluminum alloy, such as iron, iron alloy, copper or copper alloy.
  • the present invention may be embodied in pistons other than the pistons 22 of Figs. 1 to 12, which are used in swash plate compressors.
  • the present invention may be embodied in pistons of wave cam plate type compressors, pistons of double-headed piston type variable displacement compressor, pistons in air compressors and pistons in reciprocation internal combustion engines.
  • Each piston (22) includes a head (40) and a skirt (42).
  • the head (40) has a cylinder (41) with an open end, and the skirt (42) has a lid (43) for closing the open end of the cylinder (41).
  • the lid (43) is friction welded to the cylinder (41). This method firmly joins the lid (43) to the cylinder (41) and reduces the cost and the time for manufacturing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
EP99109847A 1998-05-20 1999-05-19 Kolben und Verfahren zur Herstellung Withdrawn EP0959227A3 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP13853998 1998-05-20
JP13853998 1998-05-20
JP34841998 1998-12-08
JP10348419A JP2000038987A (ja) 1998-05-20 1998-12-08 圧縮機のピストンの製造方法

Publications (2)

Publication Number Publication Date
EP0959227A2 true EP0959227A2 (de) 1999-11-24
EP0959227A3 EP0959227A3 (de) 2000-08-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99109847A Withdrawn EP0959227A3 (de) 1998-05-20 1999-05-19 Kolben und Verfahren zur Herstellung

Country Status (5)

Country Link
EP (1) EP0959227A3 (de)
JP (1) JP2000038987A (de)
KR (1) KR100300511B1 (de)
CN (1) CN1108470C (de)
BR (1) BR9901990A (de)

Cited By (11)

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EP1148235A1 (de) * 2000-04-18 2001-10-24 Halla Climate Control Corp. Verfahren zur Herstellung eines Hohlkolbens eines Kompressors
EP1106828A3 (de) * 1999-12-01 2002-06-19 Kabushiki Kaisha Toyota Jidoshokki Herstellung eines Kompressorhohlkolbens
EP1126168A3 (de) * 2000-02-18 2002-07-03 Kabushiki Kaisha Toyota Jidoshokki Verfahren zur Herstellung eines Kolbens eines Taumelscheibenverdichters
US6532655B1 (en) 1999-03-20 2003-03-18 Halla Climate Control Corp. Method of manufacturing hollow piston for compressors
FR2839909A1 (fr) * 2002-03-28 2003-11-28 Sanden Corp Procede de fabrication d'un piston ayant une tete de piston creuse
EP1384886A1 (de) * 2002-07-26 2004-01-28 Zexel Valeo Compressor Europe Gmbh Verdichterkolben
EP1234979A3 (de) * 2001-02-23 2004-06-23 Kabushiki Kaisha Toyota Jidoshokki Herstellungsverfahren eines Kompressorkolbens
DE10306792A1 (de) * 2003-01-23 2004-08-19 Zexel Valeo Compressor Europe Gmbh Kolben, insbesondere für einen Axialkolben-Verdichter, und Verfahren zur Herstellung desselben
EP1512487A1 (de) * 2003-09-08 2005-03-09 Halla Climate Control Corporation Verfahren zur Herstellung von Kolben für Taumelscheibenkompressoren mit variablem Hubraum
US6953140B2 (en) 2003-09-08 2005-10-11 Halla Climate Control Corporation Friction stir welding apparatus of piston for swash plate type compressor with variable capacity
US7036708B2 (en) 2003-09-09 2006-05-02 Halla Climate Control Corporation Manufacturing method of piston for swash plate type compressor with variable capacity

Families Citing this family (12)

* Cited by examiner, † Cited by third party
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JP2000345963A (ja) * 1999-05-31 2000-12-12 Toyota Autom Loom Works Ltd 片頭式ピストン製造用素材の製造方法
KR100388826B1 (ko) * 2000-10-11 2003-06-25 한라공조주식회사 압축기용 중공 피스톤 및 그 제조방법
KR100701164B1 (ko) * 2001-02-28 2007-03-28 한라공조주식회사 사판식 압축기용 피스톤
KR100516858B1 (ko) * 2002-10-22 2005-09-26 한국델파이주식회사 자동차용 사판식 압축기의 피스톤
JP2005042578A (ja) * 2003-07-25 2005-02-17 Zexel Valeo Climate Control Corp ピストンの尾部構成部品、ピストン及びピストンの製造方法
CN100396915C (zh) * 2003-09-24 2008-06-25 汉拏空调株式会社 可变容量的斜盘式压缩机用活塞的制造方法
KR100780379B1 (ko) 2006-06-14 2007-11-29 학교법인 두원학원 압축기용 피스톤
DE102011100521B4 (de) * 2010-08-10 2015-01-15 Mahle International Gmbh Verfahren zur Herstellung eines Kolbens für einen Verbrennungsmotor, sowie einen danach hergestellten Kolben
JP5696594B2 (ja) * 2011-06-09 2015-04-08 カルソニックカンセイ株式会社 圧縮機用ピストン
CN102310259A (zh) * 2011-08-25 2012-01-11 桐乡市易锋机械厂 活塞电子束焊接方法
CN107876919A (zh) * 2017-11-09 2018-04-06 北京海纳川汽车部件股份有限公司 活塞的制造方法以及活塞
CN113478066B (zh) * 2021-08-20 2022-06-14 黄山学院 一种用于闸阀阀板表面搅拌摩擦加工的随动夹具及随动控制方法

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US6532655B1 (en) 1999-03-20 2003-03-18 Halla Climate Control Corp. Method of manufacturing hollow piston for compressors
EP1106828A3 (de) * 1999-12-01 2002-06-19 Kabushiki Kaisha Toyota Jidoshokki Herstellung eines Kompressorhohlkolbens
US6604284B1 (en) 1999-12-01 2003-08-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Manufacturing method of piston with a hollow space for compressor
KR100403217B1 (ko) * 1999-12-01 2003-10-23 가부시키가이샤 도요다 지도숏키 압축기용 피스톤 제조방법 및 피스톤 제조장치
EP1126168A3 (de) * 2000-02-18 2002-07-03 Kabushiki Kaisha Toyota Jidoshokki Verfahren zur Herstellung eines Kolbens eines Taumelscheibenverdichters
EP1148235A1 (de) * 2000-04-18 2001-10-24 Halla Climate Control Corp. Verfahren zur Herstellung eines Hohlkolbens eines Kompressors
EP1234979A3 (de) * 2001-02-23 2004-06-23 Kabushiki Kaisha Toyota Jidoshokki Herstellungsverfahren eines Kompressorkolbens
FR2839909A1 (fr) * 2002-03-28 2003-11-28 Sanden Corp Procede de fabrication d'un piston ayant une tete de piston creuse
EP1384886A1 (de) * 2002-07-26 2004-01-28 Zexel Valeo Compressor Europe Gmbh Verdichterkolben
DE10306792A1 (de) * 2003-01-23 2004-08-19 Zexel Valeo Compressor Europe Gmbh Kolben, insbesondere für einen Axialkolben-Verdichter, und Verfahren zur Herstellung desselben
DE10306792B4 (de) * 2003-01-23 2007-03-22 Valeo Compressor Europe Gmbh Kolben, insbesondere für einen Axialkolben-Verdichter, und Verfahren zur Herstellung desselben
EP1512487A1 (de) * 2003-09-08 2005-03-09 Halla Climate Control Corporation Verfahren zur Herstellung von Kolben für Taumelscheibenkompressoren mit variablem Hubraum
US6953140B2 (en) 2003-09-08 2005-10-11 Halla Climate Control Corporation Friction stir welding apparatus of piston for swash plate type compressor with variable capacity
US7036708B2 (en) 2003-09-09 2006-05-02 Halla Climate Control Corporation Manufacturing method of piston for swash plate type compressor with variable capacity

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JP2000038987A (ja) 2000-02-08
CN1245264A (zh) 2000-02-23
KR100300511B1 (ko) 2001-09-22
KR20000011266A (ko) 2000-02-25
EP0959227A3 (de) 2000-08-30
CN1108470C (zh) 2003-05-14
BR9901990A (pt) 2000-03-14

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