Information
-
Patent Grant
-
6378416
-
Patent Number
6,378,416
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Date Filed
Tuesday, August 29, 200023 years ago
-
Date Issued
Tuesday, April 30, 200222 years ago
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Inventors
-
Original Assignees
-
Examiners
Agents
-
CPC
-
US Classifications
Field of Search
US
- 092 71
- 092 172
- 092 159
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International Classifications
-
Abstract
A piston for a swash plate type compressor including a head portion which includes a cylindrical body portion whose open end is closed by a closure member, and an engaging portion which is formed integrally with the head portion on the side remote from the open end and which engages a swash plate of the compressor, wherein: the body portion includes a hollow cylindrical section whose inner circumferential surface is provided with a plurality of axially extending reinforcing projections, each of which protrudes from the inner circumferential surface in a radially inward direction of the hollow cylindrical section and which extends in a direction parallel to a centerline of the hollow cylindrical section over a substantially entire axial length thereof, the closure member being fixed to the body portion such that the closure member is held in abutting contact with an end face of each of the reinforcing projections on the side of the open end of the body portion.
Description
This application is based on Japanese Patent Application No. 11-247112 filed Sep. 1, 1999, the contents of which are incorporated hereinto by reference.
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a piston for a swash plate type compressor, and more particularly to techniques for reducing the weight of the piston.
2. Discussion of the Related Art
As a piston used in a swash plate type compressor, there are known a single-headed piston and a double-headed piston. The single-headed piston includes a head portion which is slidably fitted in a cylinder bore formed in a cylinder block of the compressor and an engaging portion formed integrally with the head portion for engaging a swash plate. The double-headed piston includes two head portions on the opposite sides of a single engaging portion. Since the piston is reciprocated within the cylinder bore, it is desirable to reduce the weight of the piston. It is generally required to reduce the weight of the single- or double- headed piston used in a swash plate type compressor of fixed capacity type wherein the angle of inclination of the swash plate with respect to a plane perpendicular to the axis of the drive shaft of the compressor is fixed. The single-headed piston is usually used in a swash plate type compressor of variable capacity type wherein the angle of inclination of the swash plate is variable to change the discharge capacity of the compressor. When the single-headed piston is used in the variable capacity type swash plate compressor, it is particularly required to reduce its weight in order to achieve a stable operation of the compressor and reduce the noise of the compressor during its operation.
JP-A-10-159725 discloses a technique of reducing the weight of the piston. Described in detail, this publication discloses a method of producing a single-headed piston with a hollow head portion, by closing an open end of a cylindrical body portion of the piston with a closure member. The piston produced according to this method has a considerably reduced weight. However, the weight of the piston cannot be reduced to a satisfactory extent which permits the piston to be used in the swash plate type compressor of variable capacity type wherein the drive shaft is required to be rotated at a relatively high speed to achieve high operating performance of the compressor.
SUMMARY OF THE INVENTION
The present invention was made in the light of the background art described above. It is a first object of the present invention to provide a piston for a swash plate type compressor having a significantly reduced weight.
It is a second object of the present invention to provide a method of producing a blank used for manufacturing the piston of the invention.
The first object indicated above may be achieved according to any one of the following forms or modes of the present invention, each of which is numbered like the appended claims and depend from the other form or forms, where appropriate, to indicate and clarify possible combinations of technical features of the present invention, for easier understanding of the invention. It is to be understood that the present invention is not limited to the technical features and their combinations described below. It is also to be understood that any technical feature described below in combination with other technical features may be a subject matter of the present invention, independently of those other technical features.
(1) A piston for a swash plate type compressor including a head portion which includes a cylindrical body portion whose open end is closed by a closure member, and an engaging portion which is formed integrally with the head portion on the side remote from the open end and which engages a swash plate of the compressor, wherein: the body portion includes a hollow cylindrical section whose inner circumferential surface is provided with a plurality of axially extending reinforcing projections, each of which protrudes from the inner circumferential surface in a radially inward direction of the hollow cylindrical section and which extends in a direction parallel to a centerline of the hollow cylindrical section over a substantially entire axial length thereof, the closure member being fixed to the body portion such that the closure member is held in abutting contact with an end face of each of the reinforcing projections on the side of the open end of the body portion.
The piston used in the compressor receives a pressure of a compressed gas at its end face which partially defines a pressurizing chamber in the compressor. In the piston constructed according to the present invention, the end face of the piston is provided by one of opposite major surfaces of the closure member (outer end face), on which a considerably high pressure of the gas acts in a direction in which the closure member is pushed into the hollow cylindrical section during manufacture, of the piston. In view of this, it is preferable that the closure member be fixed to the hollow cylindrical section such that the closure member is received and supported by the hollow cylindrical section at the other major surface (inner end face) opposite to the above-indicated outer end face.
If the wall thickness of the hollow cylindrical section is reduced to a value in a range of 1˜2 mm for reducing the weight of the piston, the closure member cannot be received and supported by the hollow cylindrical section with high stability. For fixing the closure member to the hollow cylindrical section with their axes being aligned with each other, at least an axial portion of the closure member needs to be fitted in the hollow cylindrical section. For the following reasons, the reduction of the wall thickness of the hollow cylindrical section, however, makes it difficult that the closure member is fitted in the hollow cylindrical section with its inner end face being securely received and held in abutting contact with the hollow cylindrical section. When the hollow cylindrical section includes a large-diameter axial end portion formed on the side of its open end, which large-diameter axial end portion has an inside diameter larger than that of the other axial portion of the hollow cylindrical section, the closure member is fixed to the hollow cylindrical section such that the closure member is fitted in the large-diameter end portion such that a shoulder formed between the large-diameter end portion and the adjacent axial portion is held in abutting contact with the closure member. According to this arrangement, the closure member is held in position by the shoulder of the hollow cylindrical section while the axes of the hollow cylindrical section and the closure member are aligned with each other. When the wall thickness of the hollow cylindrical section is relatively small, the maximum inside diameter of the axial end portion is limited, so that the radial dimension of the shoulder is inevitably small. Where the large-diameter axial end portion has a low degree of concentricity with the hollow cylindrical section, the radial dimension of the shoulder is considerably small at a local circumferential portion thereof. In this case, the closure member fitted in the hollow cylindrical section cannot be sufficiently supported by the shoulder at the local circumferential portion. Accordingly, the closure member may undesirably be pushed into inner axial portion of the hollow cylindrical section by the pressure of the compressed gas acting thereon.
In the piston constructed according to the present invention wherein the hollow cylindrical section is provided with a plurality of axially extending reinforcing projections formed on its inner circumferential surface, the weight of the piston can be sufficiently reduced by reducing the wall thickness of the hollow cylindrical section at its circumferential parts in which the reinforcing projections are not formed, while permitting the closure member to be fixedly supported by the reinforcing projections. Accordingly, the present arrangement is effective to not only reduce the weight of the piston by reducing the wall thickness of the hollow cylindrical section, but also prevent the closure member from being pushed into the hollow cylindrical section upon exposure to the pressure of the compressed gas.
By suitably determining the cross sectional shape, location, and number of the reinforcing projections, the rigidity and mechanical strength of the hollow cylindrical section can be significantly increased, as compared with those of the hollow cylindrical section which has a constant wall thickness. This is based on a fact that the rigidity and mechanical strength of a relatively thin-walled structure can be increased when the structure is provided with reinforcing ribs. In this respect, the present arrangement is effective to improve the mechanical strength of the head portion of the piston while reducing its weight.
The head portion of the piston whose hollow cylindrical section is provided with the axially extending reinforcing projections as described above can be easily produced by die-casting. When the head portion of the piston whose hollow cylindrical section having a constant small wall thickness is produced by die-casting, the cast thin-walled structure has a relatively large circumferential surface area. It is, however, difficult to die-cast such a thin-walled structure since a molten metal does not easily flow through a mold cavity which has a relatively small radial dimension corresponding to the small wall thickness of the hollow cylindrical section and which has a relatively large diameter, whereby the mold cavity may not be uniformly and entirely filled with the molten metal. Accordingly, there is a limit to reduce the weight of the head portion of the piston by reducing the wall thickness of the hollow cylindrical section, due to the above-mentioned difficulty in the process of die-casting. In contrast, when the head portion of the piston whose hollow cylindrical section has the reinforcing projections is formed by die-casting, the molten metal comparatively easily flow through circumferential portions of the mold cavity, which portions have a relatively large radial dimension corresponding to the radial dimension of the reinforcing projections, so that the mold cavity can be uniformly and entirely filled with the molten metal, resulting in easy die-casting of the head portion of the piston. Accordingly, the lightweight piston can be produced efficiently by providing the reinforcing projections (thick-walled circumferential portions) on the inner circumferential surface of the hollow cylindrical section, rather than by reducing the wall thickness of the hollow cylindrical section to a constant small value.
(2) A piston according to the above mode (1), wherein the plurality of reinforcing projections are equally spaced apart from each other in the circumferential direction of the hollow cylindrical section
(3) A piston according to the above mode (1) or (2), wherein each of the reinforcing projections protrudes from the inner circumferential surface in the radially inward direction of the hollow cylindrical portion by an amount which is not greater than 300% of a wall thickness of the hollow cylindrical section, and each of the reinforcing projections has a circumferential dimension as measured in the circumferential direction of the hollow cylindrical section, which is larger than the amount of protrusion from the inner circumferential surface, each of the reinforcing projections providing a thick-walled circumferential portion having a wall thickness larger than a nominal wall thickness of the hollow cylindrical section.
(4) A piston according to the above form (1) or (2), wherein each of the reinforcing projections is in the form of a rib which protrudes from the inner circumferential surface in the radially inward direction of the hollow cylindrical section by an amount which is larger than a circumferential dimension of the rib as measured in the circumferential direction of the hollow cylindrical section.
The hollow cylindrical section may have both of the projections according to the mode (3) and the ribs according to the above mode (4).
(5) A piston according to any one of the modes (1)-(4), wherein the closure member has a plurality of fitting protrusions formed on its inner end face, for engagement with the body portion so as to prevent relative rotation of the closure member and the body portion.
In the piston according to the above mode (5) of the present invention, the relative rotation of the closure member and the body portion is prevented by the engagement of the fitting protrusions of the closure member with the body portion, facilitating the machining operation which is effected during manufacture of the piston from a blank. For instance, a closing member which gives the closure member may have a holding portion formed on its outer end face remote from the fitting protrusions, so that the blank is held by a suitable chuck at the holding portion of the closing member. When the blank held by the chuck is rotated to perform the machining operation thereon, the closing member and the body portion are effectively prevented from being rotated relative to each other by the engagement of the fitting protrusions of the closing member with the body portion. The holding portion may be cut away from the closing member after the holding portion has achieved its function.
(6) A piston for a swash plate type compressor, including a hollow cylindrical head portion and an engaging portion which is formed integrally with the head portion and which engages a swash plate of the compressor, wherein the piston includes a plurality of axially extending reinforcing projections which are formed on an inner circumferential surface of the hollow cylindrical head portion, so as to extend in a direction parallel to a centerline of the hollow cylindrical head portion over a substantially entire axial length thereof.
The piston according to the above mode (6) is substantially the same as the piston according to the above mode (1), except that the piston according to the mode (6) does not include the feature that the end faces of the reinforcing projections are held in abutting contact with the inner end face of the closure member. This mode (6) aims to improve the rigidity and mechanical strength of the hollow cylindrical section itself. It is noted that the piston according to this mode (6) may employ the technical feature according to any one of the above modes (1) through (5).
The second object indicated above may be achieved according to the following mode (7) of the invention.
(7) A method of producing a blank used for manufacturing a piston for a swash plate type compressor, as defined in any one of the modes (1)-(6), comprising the steps of: preparing a casting mold consisting of two mold halves which define a parting plane at which the two mold halves are spaced apart from each other and butted together and which have respective molding surfaces; inserting, into the casting mold, a pair of slide cores which are slidably movable in a direction perpendicular to the parting plane, each of the slide cores having an outer circumferential surface whose configuration follows that of an inner circumferential surface of the hollow cylindrical section of the piston, the outer circumferential surface of each of the slide cores cooperating with the molding surfaces of the mold halves to define a mold cavity therebetween; injecting a molten metal into the mold cavity to form the blank for the piston; retracting the slide cores out of the casting mold; and moving the mold halves apart from each other at the parting plane to remove the blank formed in the mold cavity.
This mode (7) of the present invention permits easy production of the blank for manufacturing the piston defined in any one of the above modes (1) through (6).
BRIEF DESCRIPTION OF THE DRAWINGS
The above and optional objects, features, advantages and technical and industrial significance of the present invention will be better understood and appreciated by reading the following detailed description of presently preferred embodiments of the invention, when considered in connection with the accompanying drawings, in which:
FIG. 1
is a front elevational view in cross section of a swash plate type compressor equipped with a piston constructed according to one embodiment of the present invention;
FIG. 2
is a front elevational view in cross section of the piston shown in
FIG. 1
;
FIG. 3
is a right-hand side end elevational view of a body portion of a head portion of the piston of
FIG. 2
;
FIG. 4
is a cross sectional view taken along line
4
—
4
of
FIG. 3
;
FIG. 5
is a side elevational view of the closure member of the piston of
FIG. 2
;
FIG. 6
is a cross sectional view taken along line
6
—
6
of
FIG. 5
;
FIG. 7
is a front elevational view partly in cross section showing a blank used for manufacturing the piston of
FIG. 2
, after closing members are fixed to a body member of the blank;
FIG. 8
is a front elevational view partly in cross section showing the body member of the blank of
FIG. 7
;
FIG. 9
is a right-hand side end elevational view of the body member of
FIG. 8
;
FIG. 10
is a fragmentary enlarged front elevational view in cross section showing engagement of the closing member with the body member;
FIG. 11
is a front elevational view in cross section of a piston constructed according to another embodiment of the present invention;
FIG. 12
is an end elevational view of a cylindrical body portion of a piston according to still another embodiment of the invention;
FIG. 13
is an end elevational view of a cylindrical body portion of a piston according to yet another embodiment of the invention; and
FIG. 14
is an end elevational view of a cylindrical body portion of a piston according to a further embodiment of the invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring first to
FIG. 1
, there is shown a compressor of swash plate type incorporating a plurality of single-headed pistons (hereinafter referred to simply as “pistons”) each constructed according to one embodiment of the present invention.
In
FIG. 1
, reference numeral
10
denotes a cylinder block having a plurality of cylinder bores
12
formed so as to extend in its axial direction such that the cylinder bores
12
are arranged along a circle whose center lies on a centerline of the cylinder block
10
. The piston generally indicated at
14
is reciprocably received in each of the cylinder bores
12
. To one of the axially opposite end faces of the cylinder block
10
, (the left end face as seen in
FIG. 1
, which will be referred to as “front end face”), there is attached a front housing
16
. To the other end face (the right end face as seen in
FIG. 1
, which will be referred to as “rear end face”), there is attached a rear housing
18
through a valve plate
20
. The front housing
16
, rear housing
18
and cylinder block
10
cooperate to constitute a housing assembly of the swash plate type compressor. The rear housing
18
and the valve plate
20
cooperate to define a suction chamber
22
and a discharge chamber
24
, which are connected to a refrigerating circuit (not shown) through an inlet
26
and an outlet
28
, respectively. The valve plate
20
has suction ports
32
, suction valves
34
, discharge ports
36
and discharge valves
38
.
A rotary drive shaft
50
is disposed in the cylinder block
10
and the front housing
16
such that the axis of rotation of the drive shaft
50
is aligned with the centerline of the cylinder block
10
. The drive shaft
50
is supported at its opposite end portions by the front housing
16
and the cylinder block
10
, respectively, via respective bearings. The cylinder block
10
has a central bearing hole
56
formed in a central portion thereof, and the bearing is disposed in this central bearing hole, for supporting the drive shaft
50
at its rear end portion. The front end portion of the drive shaft
50
extends through a central portion of the front housing
16
, such that the front end of the drive shaft
50
is located outside the front housing
16
, so that the drive shaft
50
is connected to a drive power source (not shown). The rotary drive shaft
50
carries a swash plate
60
such that the swash plate
60
is axially movable and tiltable relative to the drive shaft
50
. The swash plate
60
is mounted on the drive shaft
50
such that the drive shaft
50
passes through a central mounting hole
61
formed in the central portion of the swash plate
60
. The diameter of the central mounting hole
61
of the swash plate
60
gradually increases in the axially opposite directions from its axially intermediate portion towards the axially opposite ends. To the drive shaft
50
, there is fixed a rotary member
62
which is held in engagement with the front housing
16
through a thrust bearing
64
. The swash plate
60
is rotated with the drive shaft
50
by a hinge mechanism
66
during rotation of the drive shaft
50
. The hinge mechanism
66
guides the swash plate
60
for its axial and tilting motions. The hinge mechanism
66
includes a pair of support arms
67
fixed to the rotary member
62
, guide pins
69
which are formed on the swash plate
60
and which slidably engage guide holes
68
formed in the support arms
67
, the central mounting hole
61
of the swash plate
60
, and the outer circumferential surface of the drive shaft
50
.
The piston
14
indicated above includes a neck portion
70
engaging the swash plate
60
, and a head portion
72
formed integrally with the neck portion
70
and fitted in the corresponding cylinder bore
12
. The neck portion
70
has a groove
74
formed therein, and the swash plate
60
is held in engagement with the groove
74
through a pair of hemi-spherical shoes
76
. The piston is reciprocated by rotation of the swash plate
60
. The hemi-spherical shoes
76
are held in the groove
74
such that the shoes
76
slidably engage the neck portion
70
at their hemi-spherical surfaces and such that the shoes
76
slidably engage the radially outer portions of the opposite surfaces of the swash plate
60
at their flat surfaces. The configuration of the piston
14
will be described in detail.
A rotary motion of the swash plate
60
is converted into a reciprocating linear motion of the piston
14
through the shoes
76
. A refrigerant gas in the suction chamber
22
is sucked into the pressurizing chamber
79
through the suction port
32
and the suction valve
34
, when the piston
14
is moved from its upper dead point to its lower dead point, that is, when the piston
14
is in the suction stroke. The refrigerant gas in the pressurizing chamber
79
is pressurized by the piston
14
when the piston
14
is moved from its lower dead point to its upper dead point, that is, when the piston
14
is in the compression stroke. The pressurized refrigerant gas is delivered into the discharge chamber
24
through the discharge port
36
and the discharge valve
38
. A reaction force acts on the piston
14
in the axial direction as a result of compression of the refrigerant gas in the pressurizing chamber
79
. This compression reaction force is received by the front housing
16
through the piston
14
, swash plate
60
, rotary member
62
and thrust bearing
64
.
The cylinder block
10
has an intake passage
80
formed therethrough for communication between the discharge chamber
24
and a crank chamber
86
which is defined between the front housing
16
and the cylinder block
10
. The intake passage
80
is connected to a solenoid-operated control valve
90
provided to control the pressure in the crank chamber
86
. The solenoid-operated control valve
90
includes a solenoid coil
92
, and a shut-off valve
94
which is selectively closed and opened by energization and de-energization of the solenoid coil
92
. Namely, the shut-off valve
94
is placed in its closed state when the solenoid coil
92
is energized, and is placed in its open state when the coil
92
is de-energized.
The rotary drive shaft
50
has a bleeding passage
100
formed therethrough. The bleeding passage
100
is open at one of its opposite ends to the central bearing hole
56
, and is open to the crank chamber
86
at the other end. The central bearing hole
56
communicates at its bottom with the suction chamber
22
through a communication port
104
.
The present swash plate type compressor is a variable capacity type. By controlling the pressure in the crank chamber
86
by utilizing a difference between the pressure in the discharge chamber
24
as a high-pressure source and the pressure in the suction chamber
22
as a low pressure source, a difference between the pressure in the crank chamber
86
which acts on the front side of the piston
14
and the pressure in the pressurizing chamber
79
is regulated to change the angle of inclination of the swash plate
60
with respect to a plane perpendicular to the axis of rotation of the drive shaft
50
, for thereby changing the reciprocating stroke (suction and compression strokes) of the piston
14
, whereby the discharge capacity of the compressor can be adjusted.
As described above, the pressure in the crank chamber
86
is controlled by controlling the solenoid-operated control valve
90
to selectively connect and disconnect the crank chamber
86
to and from the discharge chamber
24
. Described more specifically, when the solenoid coil
92
of the solenoid-operated control valve
90
is energized, the intake passage
80
is closed, so that the pressurized refrigerant gas in the discharge chamber
24
is not delivered into the crank chamber
86
. In this condition, the refrigerant gas in the crank chamber
86
flows into the suction chamber
22
through the bleeding passage
100
and the communication port
104
, so that the pressure in the crank chamber
86
is lowered, to thereby increase the angle of inclination of the swash plate
60
. The reciprocating stroke of the piston
14
which is reciprocated by rotation of the swash plate
60
increases with an increase of the angle of inclination of the swash plate
60
, so as to increase an amount of change of the volume of the pressurizing chamber
79
, whereby the discharge capacity of the compressor is increased. When the solenoid coil
92
is de-energized, the intake passage
80
is opened, permitting the pressurized refrigerant gas to be delivered from the discharge chamber
24
into the crank chamber
86
, resulting in an increase in the pressure in the crank chamber
86
, and the angle of inclination of the swash plate
60
is reduced, so that the discharge capacity of the compressor is accordingly reduced.
The maximum angle of inclination of the swash plate
60
is limited by abutting contact of a stop
106
formed on the swash plate
60
, with the rotary member
62
, while the minimum angle of inclination of the swash plate
60
is limited by abutting contact of the swash plate
60
with a stop
107
in the form of a ring fixedly fitted on the drive shaft
50
. The solenoid coil
92
of the solenoid-operated control valve
90
is controlled by a control device not shown depending upon a load acting on the air conditioning system including the present compressor. The control device is principally constituted by a computer. In the present embodiment, the intake passage
80
, the crank chamber
86
, the solenoid-operated control valve
90
, the bleeding passage
100
, the communication port
104
, and the control device for the control valve
90
cooperate to constitute a major portion of a crank chamber pressure control device for controlling the pressure in the crank chamber
86
, or a swash plate angle adjusting device for controlling the angle of inclination of the swash plate
60
.
The cylinder block
10
and each piston
14
are formed of an aluminum alloy. The piston
14
is coated at its outer circumferential surface with a fluoro resin film which prevents a direct contact of the aluminum alloy of the piston
14
with the aluminum alloy of the cylinder block
10
so as to prevent seizure therebetween, and makes it possible to minimize the amount of clearance between the piston
14
and the cylinder bore
12
. The cylinder block
10
and the piston
14
may also be formed of a hyper-eutectic aluminum silicon alloy. Other materials may be used for the cylinder block
10
, the piston
14
, and the coating film.
There will next be described the configuration of the piston
14
.
The end portion of the neck portion
70
of the piston
14
, which is remote from the head portion
72
, has a U-shape in cross section, as shown in FIG.
2
. Described in detail, the neck portion
70
has a base section
108
which defines the bottom of the U-shape and a pair of substantially parallel arm sections
110
,
111
which extend from the base section
108
in a direction perpendicular to the axis of the piston
14
. The two opposed lateral walls of the U-shape of the end portion of the neck portion
70
have respective recesses
112
which are opposed to each other. Each of these recesses
112
is defined by a part-spherical inner surface of the lateral wall. The pair of shoes
76
indicated above are held in contact with the opposite surfaces of the swash plate
60
at its radially outer portion and are received in the respective part-spherical recesses
112
. Thus, the neck portion
70
slidably engages the swash plate
60
through the shoes
76
. In the present embodiment, the neck portion
70
constitutes an engaging portion which engages the drive member in the form of the swash plate
60
.
The head portion
72
of the piston
14
is formed integrally with the neck portion
70
on the side of its arm section
111
, and includes a cylindrical body portion
114
and a closure member
116
fixed to the body portion
114
. The cylindrical body portion
114
is open at one of its opposite ends which is remote from the neck portion
70
, and is closed at the other end. The closure member
116
closes the open end of the body portion
114
. As shown in
FIGS. 3 and 4
, the body portion
114
includes a hollow cylindrical section
120
whose inner circumferential surface
122
is provided with a plurality of axially extending reinforcing projections
126
. The plurality of reinforcing projections
126
, four reinforcing projections in the present embodiment, are arranged equiangularly from each other in the circumferential direction of the hollow cylindrical section
120
and protrude from the inner circumferential surface
122
of the hollow cylindrical section
120
in the radially inward direction thereof. Each of the reinforcing projections
126
extends in the axial direction of the hollow cylindrical section
120
from an axial position near the open end of the body portion
114
to a bottom surface
132
of the hollow cylindrical section
120
on the side of the neck portion
70
. Each reinforcing projection
126
has an arcuate cross sectional shape, as shown in
FIG. 3
, and has a circumferential dimension which is larger than a radial dimension thereof. Each reinforcing projection
126
protrudes from the inner circumferential surface
122
in the radially inward direction of the hollow cylindrical section
120
by an amount which is not less than 100% of the wall thickness of the hollow cylindrical section
120
. More specifically, the wall thickness of the hollow cylindrical section
120
is about 0.8 mm while the radial dimension of the axial reinforcing projection
126
(the amount of protrusion of the projection
126
from the inner circumferential surface
122
) is about 0.9 mm. For reducing the weight of the piston
14
, the amount of protrusion of the reinforcing projection
126
is preferably within a range of 0.3˜2.0 mm or 0.3˜1.0 mm. In
FIGS. 3 and 4
, the thickness of the hollow cylindrical section
120
and the radial dimension of the reinforcing projections
126
are exaggerated for easier understanding.
By providing the axially extending reinforcing projections
126
on the inner circumferential surface
122
of the hollow cylindrical section
120
described above, the hollow cylindrical section
120
has thin-walled portions having the nominal wall thickness, i.e., 0.8 mm, in which the reinforcing projections
126
are not formed, and thick-walled portions whose thickness is a sum of the nominal wall thickness (0.8 mm) of the hollow cylindrical section
120
and the amount of protrusion (0.9 mm) of the reinforcing projections
126
from the inner circumferential surface
122
, i.e., 1.7 mm.
According to this arrangement, the cylindrical body portion
114
of the piston
14
has a sufficient mechanical strength owing to the reinforcing projections
126
(thick-walled portions), while permitting the piston
14
to have a reduced weight owing to the thin-walled portion of the hollow cylindrical section
120
. Further, the closure member
116
is securely fixed in the open end portion of the hollow cylindrical section
120
, with its inner end face
142
held in abutting contact with the reinforcing projections
126
, as described below in greater detail.
As shown in
FIG. 3
, the hollow cylindrical section
120
has a plurality of engaging grooves
130
, each of which is defined by opposed lateral or side surfaces of the adjacent two reinforcing projections
126
and the inner circumferential surface
122
. The engaging grooves
130
, which correspond to the above-indicated thin-walled portions, are arranged equiangularly from each other in the circumferential direction of the hollow cylindrical section
120
, such that each groove
130
is interposed between the adjacent reinforcing projections
126
. According to this arrangement, the hollow cylindrical section
120
has a constant wall thickness at its open end, and the alternately arranged thick-walled portions and thin-walled portions which extend from the axial position near the open end to the bottom surface
132
of the hollow cylindrical section
120
and which cooperate to take the form of a spline in transverse cross section.
The closure member
116
is a generally disc-shaped member which consists of a circular plate portion
140
, and a plurality of fitting protrusions
144
(four fitting protrusions in this embodiment) which protrude from the outer peripheral portions of one of the opposite end faces of the plate portion
140
, i.e., the inner end face
142
, of the plate portion
140
, and which are arranged equiangularly from each other in the circumferential direction of the plate portion
140
. Each fitting protrusion
144
has a circumferential dimension which is larger than its radial dimension, and has an arcuate cross sectional shape, as shown in FIG.
5
. In the present embodiment, the outer part-circumferential surface of each fitting protrusion
144
is continuously contiguous to or flush with the outer circumferential surface of the circular plate portion
140
. As indicated in the two-dot chain line in
FIG. 3
, the closure member
116
is shaped to be held in engagement with the inner circumferential surface
122
of the hollow cylindrical section
120
of the body portion
114
. Namely, each fitting protrusion
144
of the closure member
116
is dimensioned and located in the circumferential direction of the circular plate portion
140
so as to be held in engagement with the corresponding engaging groove
130
of the hollow cylindrical section
120
.
The closure member
116
is fitted in the inner circumferential surface
122
of the hollow cylindrical section
120
such that the inner end face
142
of the closure member
116
is held in abutting contact with end faces
150
of the respective reinforcing projections
126
on the side of the open end of the body portion
114
. Described in detail, the outer circumferential surface of the circular plate portion
140
of the closure member
116
engages the axial end portion of the inner circumferential surface
122
, while each fitting protrusion
144
engages the corresponding engaging groove
130
of the hollow cylindrical section
120
of the body portion
114
. In this state, the body portion
114
and the closure member
116
are welded together. The compression reaction force which acts on the end face of the piston
14
(which partially defines the pressurizing chamber
79
), as a result of compression of the refrigerant gas in the pressurizing chamber
79
during the compression stroke of the piston
14
, is received by the end faces
150
of the reinforcing projections
126
and the inner end face
142
of the closure member
116
which are held in abutting contact with each other, as well as the contacting circumferential surfaces of the body portion
114
and the closure member
116
, which surfaces are bonded together by welding. When the closure member
116
engages the inner circumferential surface
122
of the hollow cylindrical section
120
of the body portion
114
as described above, the relative rotation of the closure member
116
and the body portion
114
is prevented by the engagement of the lateral or side surfaces of the adjacent axial reinforcing projection
126
and the fitting protrusion
144
.
Two pieces of the piston
14
constructed as described above are produced from a single blank
160
shown in FIG.
7
. The blank
160
used for producing the two pistons
14
has a body member
162
and two closing members
164
. The body member
162
consists of a twin neck section
166
and two cylindrical hollow head sections
168
formed integrally with the twin neck section
166
such that the two hollow head sections
168
extend from the opposite ends of the twin neck section
166
in the opposite directions. The twin-neck section
166
consists of mutually integrally formed two portions which correspond to the neck portions
165
of the two single-headed pistons
14
. Each of the two hollow head sections
168
is closed at one of its opposite ends which is on the side of the twin neck section
166
, and has a hollow cylindrical section
170
which is open at the other end and which corresponds to the hollow cylindrical body portion
114
of the head portion
72
of the piston
14
.
On the inner circumferential surface
172
of the hollow cylindrical section
170
of each head section
168
, four axially extending reinforcing projections
174
are formed so as to protrude from the inner circumferential surface
172
in a radially inward direction of the hollow cylindrical section
170
. The inner circumferential surface
172
cooperates with the lateral surfaces of the two adjacent reinforcing projections
174
to define an engaging groove
176
. Namely, four engaging grooves
176
are formed in the inner circumferential surface
172
as shown in FIG.
9
. The reinforcing projections
174
and the engaging grooves
176
respectively function as the reinforcing projections
126
and the engaging grooves
130
of the piston
14
. The hollow cylindrical section
170
and each reinforcing projection
174
of the blank
160
have the same dimensional relationship as the hollow cylindrical section
120
and each reinforcing projection
126
, and a detailed description of which is dispensed with. The body member
162
is formed by die-casting of a metallic material in the form of an aluminum alloy. This formation of the body member
162
by die-casting is a step of preparing the body member
162
. Each of the two neck portions
165
of the twin neck portion
166
includes a base section
182
functioning as the base portion
182
of the piston
14
and a pair of opposed parallel arm sections
184
,
186
functioning as the arm sections
110
,
111
of the piston
14
. Reference numeral
180
denotes two bridge portions, each of which connects the inner surfaces of the arm sections
184
,
186
, in order to reinforce the neck portion
165
for thereby increasing the rigidity of the body member
162
. Each bridge portion
180
functions as a reinforcing portion by which the body member
162
is protected from being deformed due to heat.
There will be described a process of manufacturing the body member
162
by die-casting by referring to
FIGS. 8 and 9
.
A casting mold used for producing the body member
162
consists of two mold halves, one of which is stationary and the other of which is movable relative to the stationary mold half. The contact surfaces
190
,
192
of the two mold halves define a parting plane
193
, at which the two mold halves are butted together and are spaced apart from each other by a suitable moving device not shown. As indicated by a two-dot chain line in
FIG. 9
, the parting plane
193
includes the centerline of the blank
160
passing the centers of the generally cylindrical head sections
168
and is parallel to the direction of extension of the arm sections
184
,
186
from the base sections
182
of the neck portions
165
. The two mold halves have respective molding surfaces
194
,
196
which cooperate with outer circumferential surfaces
204
of slide cores
200
,
202
, to define a mold cavity
198
whose profile follows that of the body member
162
. The slide cores
200
,
202
are disposed in the casting mold consisting of the two mold halves, such that the slide cores
200
,
202
are advanced into and retracted out of the casting mold by a suitable drive device not shown. The slide cores
200
,
202
indicated in the two-dot chain line in
FIGS. 8 and 9
are slidably movable relative to each other in a direction parallel to the centerline of the cylindrical head sections
168
and in a direction perpendicular to the parting direction of the mold halves described above. Each of the slide cores
200
,
202
includes a front end portion to be inserted into the casting mold and a cylindrical portion remote from the front end portion. In the outer circumferential surface
204
of the front end portion of each slide core
200
,
202
, there are formed axially extending four recesses
206
which extend in the axial direction of the slide core and which are dimensioned and disposed so as to give the four reinforcing projections
174
described above. The cylindrical portion of each slide core
200
,
202
has an outside diameter which corresponds to the inside diameter of the hollow cylindrical section
170
at an axial portion thereof in which the reinforcing projections
174
are not formed. Each slide core
200
,
202
is movable between an advanced position in which the outer circumferential surface
204
of each slide core
200
,
202
cooperates with the molding surfaces
194
,
196
of the two mold halves to define the molding cavity
198
, and a retracted position in which the front end portion of each slide core
200
,
202
is located outside the casting mold.
By using the casting mold and the slide cores
200
,
202
constructed as described above, the body member
162
is die-cast in the following manner. Initially, the movable mold half is assembled with the stationary mold half at the parting plane
193
so that the two mold halves are prevented from moving relative to each other. After each slide core
200
,
202
is placed in the advanced position described above, a molten metal, i.e., a molten aluminum alloy is injected, via a channel not shown, into the mold cavity
198
which is defined between the molding surfaces
194
,
196
of the two mold halves and the outer circumferential surfaces
204
of the slide cores
200
,
202
. The injected molten metal flows mainly through portions of the mold cavity
198
, which portions correspond to the thick-walled circumferential portions of the hollow cylindrical section
170
in which the reinforcing projections
174
are formed and which have a radial dimension larger than the other circumferential portions, namely, the thin-walled circumferential portions of the hollow cylindrical section
170
in which the engaging grooves
176
are formed. Thus, the molten metal more easily flows to uniformly fill the mold cavity
198
in the present mold, than in a mold wherein the mold cavity has a constant radial dimension for forming a hollow cylindrical section without the reinforcing projections
174
. Accordingly, the present arrangement results in easy manufacture of the body member
162
.
Subsequently, the movable mold half is separated from the stationary mold half a predetermined time after the molten metal was injected into the mold cavity
198
, and the slide cores
200
,
202
are retracted out of the formed head sections
168
. Then, the formed body member
162
is removed from the stationary mold half.
The two closing members
164
are identical in construction with each other as shown in FIG.
7
. Like the closure member
116
, each of these closing members
164
includes a circular plate portion
210
and four fitting protrusions
212
which provide as the fitting protrusions
212
of the piston
14
. The circular plate portion
210
and the fitting protrusions
212
of the closing member
164
have the same dimensional relationship as the circular plate portion
140
and the fitting protrusions
144
of the closure member
116
, and a detailed explanation of which is dispensed with. The circular plate portion
210
of each closing member
164
has a holding portion
220
formed at a central portion of an outer end face
216
which is opposite to the inner end face
214
on which the fitting protrusions
212
are formed. The holding portion
220
has a circular shape in cross section, and has a center hole
222
. In the present embodiment, the closing member
164
is formed by die-casting of a metallic material in the form of an aluminum alloy. This formation of the closing members
164
by die-casting is a step of preparing the closing members
164
.
To fix the closing members
164
to the body member
162
, each closing member
164
is inserted into the open end of the head section
168
while the four fitting protrusions
212
of the closing member
164
are held in alignment with the respective engaging grooves
176
of the head section
168
. As shown in the enlarged view of
FIG. 10
, the outer circumferential surface of the circular plate portion
210
of the closing member
164
engages the inner circumferential surface
172
of the head section
168
while the fitting protrusions
212
of the closing member
164
engage the respective engaging grooves
176
of the head section
168
, whereby the closing member
164
is fixed to the body member
162
with their axes being aligned with each other. The closing member
164
is inserted into the open end of the head section
168
until the inner end face
214
of the circular plate portion
210
is brought into abutting contact with the end faces
226
of the respective reinforcing projections
174
formed on the inner circumferential surface
172
of the hollow cylindrical section
170
of the body section
168
. With each closing member
164
fitted in the body member
162
as described above, the inner circumferential surface
172
of the head section
168
and the outer circumferential surface of the circular plate portion
210
of the closing member
164
are held close to or in abutting contact with each other, so that these inner and outer circumferential surfaces are bonded to each other by means of an electron beam welding. In the welding operation, an assembly of the body member
162
and the two closing members
164
fitted in the body member
162
is held and sandwiched by and between a pair of jigs not shown such that each closing member
164
is pressed onto the body member
162
by each jig with the holding portion
220
of the closing member
164
being fitted in a hole formed in the jig. In this state, a torque is applied to each closing member
164
through the jig by a suitable drive device, so that the assembly of the body member
162
and the closing members
164
is rotated. Then, the electron beam is incident upon the body member
162
and the closing members
164
, so that these members are welded together at the contacting inner and outer circumferential surfaces described above. The closing members
164
are prevented from being removed away from the body member
162
by the engagement of the lateral surfaces of the reinforcing projections
174
of the head section
168
with the lateral surfaces of the fitting protrusions
212
of the closing members
164
, and by the jigs which press the closing members
164
onto the body member
162
, permitting an efficient welding of these members.
In the present embodiment, since the body member
162
and each closing member
164
are both formed by die-casting and have a high dimensional accuracy, the closing members
164
are fitted in the body member
162
without prior mechanical working operations such as machining and grinding operations, resulting in a reduced cost of manufacture of the blank
160
for the single-headed pistons
14
.
After the two closing members
164
are fixedly fitted in the respective open end portions of the body member
162
as described above, a machining operation is performed on the outer circumferential surfaces of the hollow head sections
168
of the body member
162
and the exposed outer circumferential surfaces (
FIG. 11
) of the closing members (
300
). This machining operation is effected on a lathe or turning machine such that the blank
160
is held by chucks at the holding portions
220
of the closing members
164
, with the blank
160
being centered with two centers engaging the center holes
222
, and such that the blank
160
is rotated by a suitable drive device. Since the closing members
164
are fixed to the body member
162
by welding, and the lateral surfaces of the reinforcing projections
174
of the head section
168
engage the lateral surfaces of the fitting protrusions
212
of each closing member
164
, the closing members
164
and the body member
162
are prevented from rotating relative to each other, so that the blank
160
can be turned as a whole for efficient machining on its outer circumferential surface.
Then, the outer circumferential surfaces of the hollow head sections
168
of the body member
162
and the closing members are coated with a suitable material, such as a film of polytetrafluoroethylene. The blank
160
is then subjected to a machining operation to cut off the holding portions
220
from the closing members
164
, and a centerless grinding operation on the coated outer circumferential surfaces of the hollow head sections
168
and the closing members, so that the two portions which provide the head portions
72
of the two pistons
14
are formed. In the next step, a cutting operation is performed near the two bridge portions
180
of the twin-neck section
166
, to form the recesses
112
in which the shoes
76
of the pistons
14
are received. Thus, the two portions which provide the neck portions
70
of the two pistons
14
are formed at the twin neck section
166
. Finally, the twin neck section
166
is subjected at its axially central portion to a cutting operation to cut the blank
160
into two pieces which provide the respective two single-headed pistons
14
.
The present embodiment described above is effective to reduce the weight of the piston
14
by reducing the wall thickness of the hollow cylindrical section
120
of the body portion
114
of the piston
14
while the closure member
116
is received and supported with high stability by the axially extending reinforcing projections formed on the inner circumferential surface
122
of the hollow cylindrical section
120
. According to this arrangement, the compression reaction force acting, during the compression stroke of the piston, on the end face of the piston
14
which partially defines the pressurizing chamber
79
, can be received by the abutting contact of the end faces
150
of the respective reinforcing projections
126
with the inner end face
142
of the closure member
116
, whereby the closure member
116
is prevented from being pushed into the cylindrical body section
120
of the body portion
114
, resulting in an improved mechanical strength of the head portion
72
of the piston
14
on the side of its end face partially defining the pressurizing chamber
79
. Further, since the reinforcing projections
126
are formed on the inner circumferential surface
122
of the hollow cylindrical section
120
of the body portion
114
, so as to extend over substantially the entire axial length of the hollow cylindrical section
120
, the hollow cylindrical section
120
exhibits a sufficiently high degree of rigidity and mechanical strength with respect to buckling.
The closure member may be otherwise constructed. For instance, the closure member
300
shown in
FIG. 11
has a circular plate portion
302
which includes a large-diameter portion
304
, a small-diameter portion
306
, and a shoulder
310
formed therebetween. The large-diameter portion
304
has an outside diameter equal to that of the hollow cylindrical section
120
of the body portion
114
. The small-diameter portion
306
is fitted at its outer circumferential surface in the inner circumferential surface
122
of the hollow cylindrical section
120
. The closure member
300
is fitted in the inner circumferential surface
122
of the hollow cylindrical section
120
of the body portion
114
such that the shoulder
310
of the closure member
300
is held in abutting contact with the annular end face
314
of the hollow cylindrical section
120
on the side of its open end, and such that the inner end face
142
of the closure member
300
is held in abutting contact with the end faces
150
of the respective reinforcing projections
126
of the body portion
114
. In this state, the closure member
300
is welded to the body portion
114
. In this arrangement, the compression reaction force of the refrigerant gas acting, during the compression stroke of the piston
14
, on the end face of the piston
14
partially defining the pressurizing chamber
79
, is received by the abutting contact of the annular end face
314
of the hollow cylindrical section
120
with the shoulder
310
of the closure member, as well as the abutting contact of the end faces
150
of the respective reinforcing projections
126
with the inner end face
142
of the closure member
300
, to thereby increase the mechanical strength of the head portion
72
of the piston
14
. In
FIG. 11
, the same reference numbers as used in
FIGS. 1-10
are used to identify the corresponding components, and a detailed description of which is dispensed with. The piston
14
of
FIG. 11
is produced in a manner similar to that for producing the piston
14
of
FIGS. 1-10
, and a detailed description of which is dispensed with.
The reinforcing projections
126
shown in
FIGS. 1-10
may be otherwise constructed by suitably changing the cross sectional shape, location, and numbers thereof, as shown in the following embodiments of
FIGS. 12-14
, wherein the same reference numerals as used in
FIGS. 1-10
are used to identify the corresponding components, and a detailed description of which is dispensed with. The piston is produced by using the body portions
114
having different reinforcing projections shown in
FIGS. 12-14
, in a manner similar to that in
FIGS. 1-10
, and a detailed description of which is dispensed with.
The body portion
114
shown in
FIG. 12
has a plurality of axially extending reinforcing projections in the form of ribs
400
, eight reinforcing ribs
400
in this embodiment, which are arranged equiangularly from each other in the circumferential direction of the body portion
114
and each of which protrudes from the inner circumferential surface
122
of the hollow cylindrical section
120
in its radially inward direction. Each reinforcing rib
400
is formed on the inner circumferential surface
122
such that the reinforcing rib
400
extends from an axial position of the hollow cylindrical section
120
near its open end to the bottom surface
132
over substantially the entire axial length of the hollow cylindrical section
120
. Each reinforcing rib
400
is rectangular in cross section, and has a radial dimension (an amount of protrusion from the inner circumferential surface
120
) larger than its circumferential dimension as measured in the circumferential direction of the hollow cylindrical section
120
. In the present embodiment, the circumferential dimension of each rib
400
is equal to the wall thickness of the hollow cylindrical section
120
while the radial dimension (the amount of protrusion) is about two times the wall thickness of the hollow cylindrical section
120
. The radial dimension of the rib
400
is preferably within a range between not less than 100% or 200% of the wall thickness of the hollow cylindrical section
200
and not greater than 400% or 300% of the wall thickness of the hollow cylindrical section
120
. It is preferable that at least three reinforcing ribs
400
be formed on the inner circumferential surface
122
of the hollow cylindrical section
120
.
The body portion
114
shown in
FIG. 13
has four axially extending reinforcing projections in the form of walls
500
which are arranged equiangularly from each other in the circumferential direction of the hollow cylindrical section
120
of the body portion
114
. Each reinforcing wall
500
extends from an axial position of the hollow cylindrical section
120
near its open end to the bottom surface
132
over substantially the entire axial length of the hollow cylindrical section
120
. Like the reinforcing rib
400
in
FIG. 12
, the reinforcing wall
500
has a radial dimension (an amount of protrusion from the inner circumferential surface
120
) which is larger than its circumferential dimension as measured in the circumferential direction of the hollow cylindrical section
120
. Each of the reinforcing walls
500
protrudes from the inner circumferential surface
122
of the hollow cylindrical section
120
in its radially inward direction, so that the four reinforcing walls
500
are connected together at the center of the hollow cylindrical section
120
, as shown in FIG.
13
.
The reinforcing projections need not be located equiangularly from each other in the circumferential direction of the hollow cylindrical section
120
of the body portion
114
. For instance, a plurality of axially extending reinforcing projections
600
, e.g., five reinforcing projections
600
in the embodiment shown in
FIG. 14
, are not equally spaced apart from each other in the circumferential direction of the hollow cylindrical section
120
of the body portion
114
. The reinforcing projections
600
of
FIG. 14
have a triangular cross sectional shape whose circumferential dimension decreases with an increase of the radial distance from the inner circumferential surface
122
.
The reinforcing projections may consist of a combination of projections and/or ribs such as the projections
144
,
600
and the ribs
400
,
500
.
The configuration of the closure member is not particularly limited. For instance, the closure member is a circular plate which engages the inner circumferential surface
122
of the hollow cylindrical section
120
such that one of its opposite end faces is held in abutting contact with the end faces of the respective reinforcing projections. Alternatively, the closure member may have fitting protrusions (
144
) protruding from one of its opposite end faces, as in the illustrated embodiments. The configuration of the fitting projections of the closure member is not particularly limited.
The parting plane which is defined by the two mold halves of the casting mold used for die-casting the blank for the two single-headed pistons may be otherwise established. For instance, the parting plane may be parallel to a plane which includes a centerline of the blank
160
passing the centers of the cylindrical body portions
168
and which is perpendicular to the direction of extension of the arm sections
184
,
186
from the base sections
182
. In this case, the parting plane passes a part of the neck portions
165
which has the largest dimension as measured in the direction perpendicular to the direction of extension the arm sections
184
,
186
.
The closing members may be welded to the body member of the blank for the piston by means of a laser beam. Alternatively, the closing members and the body member may be bonded together by any suitable means other than the beam welding. For instance, the closing members are fixed to the body member by bonding using an adhesive agent or an alloy having a lower melting point than those members, such as a soldering or brazing material. Further, the closing members may be fixed to the body member by caulking or by means of screws. Alternatively, the closing members may be fixed to the body member by utilizing frictional contact or plastic material flow between the two members. The above-described methods may be employed in combination.
The blank for the piston may be formed by forging. In this case, two closing members are formed integrally with a twin neck member, and each closing member closes the open end of the corresponding one of two hollow cylindrical members each of which gives the head portion of the piston.
The construction of the swash plate type compressor for which the piston
14
is incorporated is not limited to that of FIG.
1
. For instance, the solenoid-operated control valve
90
is not essential, and the compressor may use a shut-off valve which is mechanically opened and closed depending upon a difference between the pressures in the crank chamber
86
and the suction chamber
22
. In place of or in addition to the solenoid-operated control valve
90
, a solenoid-operated control valve similar to the control valve
90
may be provided in the bleeding passage
100
. Alternatively, a shut-off valve may be provided, which is mechanically opened or closed depending upon a difference between the pressures in the crank chamber
86
and the discharge chamber
24
. Further, the swash plate type compressor may be of a fixed capacity type, wherein the angle of inclination of the swash plate is fixed. The swash plate type compressor may employ double-headed pistons.
While some presently preferred embodiments of this invention have been described above, for illustrative purpose only, it is to be understood that the present invention may be embodied with various changes and improvements such as those described in the SUMMARY OF THE INVENTION, which may occur to those skilled in the art.
Claims
- 1. A piston for a swash plate type compressor including a head portion which includes a cylindrical body portion whose open end is closed by a closure member, and an engaging portion which is formed integrally with said head portion on the side remote from said open end and which engages a swash plate of the compressor, wherein the improvement comprises:said body portion including a hollow cylindrical section whose inner circumferential surface is provided with a plurality of axially extending reinforcing projections, each of which protrudes from said inner circumferential surface in a radially inward direction of said hollow cylindrical section and which extends in a direction parallel to a centerline of said hollow cylindrical section over a substantially entire axial length thereof, said closure member being fixed to said body portion such that said closure member is held in abutting contact with an end face of each of said reinforcing projections on the side of said open end of said body portion.
- 2. A piston according to claim 1, wherein said plurality of reinforcing projections are equally spaced apart from each other in the circumferential direction of said hollow cylindrical section.
- 3. A piston according to claim 2, wherein each of said reinforcing projections protrudes from said inner circumferential surface in said radially inward direction of said hollow cylindrical portion by an amount which is not greater than 300% of a wall thickness of said hollow cylindrical section, and said each of said reinforcing projections has a circumferential dimension as measured in the circumferential direction of said hollow cylindrical section, which is larger than said amount of protrusion from said inner circumferential surface, said each of said reinforcing projections providing a thick-walled circumferential portion having a wall thickness larger than a nominal wall thickness of said hollow cylindrical section.
- 4. A piston according to claim 1, wherein said each of said reinforcing projections is in the form of a rib which protrudes from said inner circumferential surface in said radially inward direction of said hollow cylindrical section by an amount which is larger than a circumferential dimension of said rib as measured in the circumferential direction of said hollow cylindrical section.
- 5. A piston according to claim 1, wherein said closure member has a plurality of fitting protrusions formed on its inner end face, for engagement with said body portion so as to prevent relative rotation of said closure member and said body portion.
- 6. A piston for a swash plate type compressor including a hollow cylindrical head portion and an engaging portion which is formed integrally with said head portion and which engages a swash plate of the compressor, wherein the improvement comprises:a plurality of axially extending reinforcing projections being formed on an inner circumferential surface of said hollow cylindrical head portion, so as to extend in a direction parallel to a centerline of said hollow cylindrical head portion over a substantially entire axial length thereof.
Priority Claims (1)
Number |
Date |
Country |
Kind |
11-247112 |
Sep 1999 |
JP |
|
US Referenced Citations (4)
Foreign Referenced Citations (3)
Number |
Date |
Country |
505264 |
Jul 1920 |
FR |
A-9-250451 |
Sep 1997 |
JP |
A-10-159725 |
Jun 1998 |
JP |