JPH09175159A - Swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve assembling workability by forming a swash plate out of a journal part near a shaft and a flat plate part fitted outwards in the radial direction of the journal part separately, forming the flat plate part out of material whose Young's modulus is high, and decreasing the thickness of the flat plate part as much as possible. SOLUTION: In this single-head type variable capacity swash plate compressor, a swash plate rotated by a shaft 1 is fitted inside a crank chamber 3, and the rotational movement of the swash plate makes a piston 6 reciprocate inside a cylinder chamber 7, so that fluid is sucked and discharged. This swash plate is constituted by forming a cast iron journal part 2a and a steel flat plate part 2b whose Young's modulus is high separately and connecting both of them with a threaded part N. By forming the flat plate part 2b out of a material whose Young's modulus is high, it is possible to decrease the thickness of the swash plate, increase the engaging allowance of a sliding shoe 5 largely, and set the stroke of the piston 6 so as to be long. It is also possible to facilitate assembling work.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a swash plate type compressor, and more particularly to a swash plate portion of a single-head type variable displacement compressor.

[0002]

2. Description of the Related Art Conventionally, a swash plate type compressor used in a vehicle air conditioner is of a fixed capacity type in which the tilt angle of the swash plate is fixed with respect to the shaft, and the tilt angle of the swash plate with respect to the shaft changes. There is a variable capacity type configured as above, a double-headed type with pistons provided on both axial sides of the swash plate, and a single-headed type with pistons provided on one side.
Recently, a single-head type variable capacity swash plate compressor, which is lightweight and can rotate at high speed, is becoming the mainstream.

In this single-headed variable displacement swash plate compressor, as shown in FIG. 3, a swash plate 2 rotated by a shaft 1 is provided in a crank chamber 3 with a variable inclination angle, and sliding shoes 4 and 5 are used. The swash plate 2 and the piston 6 are directly connected, the swash plate 2 and the shaft 1 are connected by a hinge mechanism K, and the rotation of the shaft 1 is transmitted to the swash plate 2.

Since the swash plate 2 makes a so-called "sliding rotary motion" around the shaft 1, the piston 6 reciprocates linearly in the cylinder chamber 7 due to this. At this time, if the inclination angle of the swash plate 2 is changed,
The stroke amount of the piston 6 is adjusted so that the amount of discharged refrigerant changes.

Each piston 6 comprises a piston head 8 which reciprocates in the cylinder chamber 7, and connecting portions 9 and 10 which engage with the swash plate 2 and which have a substantially U-shaped cross section. Both sides of the connecting portions 9 and 10 are connected to each other. Two spherical concave portions 9s formed in the inner surface at opposing positions,
Sliding shoes 4 and 5 having a substantially hemispherical shape are fitted to 10 s, and both the front and back flat surfaces of the swash plate 2 are sandwiched by these sliding shoes 4 and 5.

As described above, in the single-head type variable capacity swash plate compressor, since the portion for compressing the refrigerant and the like exists only on one side of the swash plate 2, the amount of refrigerant discharged is half that of the double-head type. However, in order to maintain the desired reduction in the discharge amount, it is necessary to rotate the swash plate 2 at a higher speed than the double-head type.

In the figure, "Cv" is a control valve for adjusting the pressure in the crank chamber 3.

[0008]

However, if the single-headed variable displacement swash plate compressor is to be rotated at a higher speed, there is a problem in the structure of the swash plate 2. That is, in the swash plate 2 of this compressor, the journal portion 2a and the flat plate portion 2b are integrally formed, and since this is made of cast iron, the compression reaction force applied to the swash plate when the piston is compressed and the shaft 1 In order to counter the rotational force transmitted, the wall thickness must be increased, resulting in an increase in weight, which is not preferable for rotating at a higher speed.

Further, since the swash plate flat plate portion 2b is thick, the engagement margin S between the spherical concave portions 9s and 10s and the sliding shoes 4 and 5 becomes insufficient, or the spherical concave portion 9 is formed.
Since the shaft side ends of s and 10s interfere with the swash plate 2, the tilt angle of the swash plate 2 cannot be increased, and as a result, the stroke of the piston 6 is shortened, and the discharge amount of the refrigerant or the like is reduced accordingly. There is also a problem.

That is, both side surfaces of the flat plate portion 2b of the swash plate 2 are
It is a sliding surface of the sliding shoes 4, 5, and circular flat surface portions 4a, 5a of the sliding sliding shoes 4, 5 are in sliding contact therewith, while a spherical concave portion 9s, is formed in the connecting portion 9 of the piston. 10s are formed, and the spherical convex portions 4b, 5b of the sliding shoes 4, 5 are formed here.
Are in sliding contact.

In such a structure, the inclined swash plate 2
When the shaft 6 is rotated by the shaft 1, the piston 6 moves to the top dead center position (upper piston position in FIG. 4) when slidingly contacting the outer edge portion of the swash plate 2 closest to the cylinder chamber side. The bottom dead center position (the piston position on the lower side in FIG. 4) when slidingly contacting the outer edge portion far from the cylinder chamber side.
Go to

Here, in order to maintain the state in which the sliding shoes 4 and 5 are in good engagement with each other without slipping off from the connecting portions 9 and 10 of the piston 6 even when the swash plate 2 makes a rubbed rotary movement. As shown in FIG. 4, the spherical convex portions 4b, 5b of the sliding shoes 4, 5 must be formed so as to form a part of the spherical surface of the same sphere.

However, in this case, due to the restrictions on the design layout of the peripheral portions of the sliding shoes 4, 5, the running allowance S (see FIG. 5) of the sliding shoes 4, 5 when the swash plate is tilted becomes small. As is clear from FIGS. 4 and 5, when the swash plate 2 is tilted to the maximum, the spherical concave portion 10s of the connecting portion 10 when the piston 6 is at the top dead center position.
The sliding margin S between the sliding shoe 5 and the sliding shoe 5 and the sliding margin S between the spherical concave portion 9s of the connecting portion 9 and the sliding shoe 4 at the bottom dead center position are extremely small.

Therefore, the sliding shoes 4 and 5 are pushed out in the direction of the arrow in the figure by the rotating operation of the swash plate 2 and the like, near the ends of the spherical concave portions 9s and 10s having the smaller engagement margin S on the shaft 1 side. There is a risk that the riding shoe may get caught and the sliding shoe may get caught or fall off. This phenomenon occurs when the frictional resistance increases due to insufficient lubrication, such as during a sudden start.

For this reason, when the vicinity of the ends of the spherical recesses 9s, 10s on the shaft 1 side is pushed out toward the direction that wraps the sliding shoe, and the engagement margin S between the spherical recesses 9s, 10s and the sliding shoes 4, 5 is increased, the swash plate is increased. When 2 is tilted, the ends of the spherical recesses 9s, 10s on the shaft 1 side having the larger engagement margin S interfere with the swash plate 2, so the engagement margin S cannot be unnecessarily increased.

On the other hand, it is possible to increase the running margin S by setting the plate thickness of the flat plate portion 2b of the swash plate 2 thin, but the strength and rigidity of the swash plate 2 are impaired, and durability and reliability are improved. There is a risk of lowering it.

Therefore, in the current variable capacity swash plate type compressor, the thickness of the flat plate portion 2b of the swash plate 2 cannot be reduced, and the sliding allowance S of the sliding shoes 4, 5 accompanying this cannot be reduced.
Also, the inclination angle of the swash plate 2 cannot be increased due to the problem of interference of the spherical concave portions 9s and 10s with the swash plate 2, and as a result, the stroke of the piston 6 is shortened, and the discharge amount of the refrigerant or the like is reduced accordingly. .

Further, the structure of the portion of the swash plate 2 described above is as follows.
There is also a problem when assembling the compressor. That is, the connecting portions 9, 1 of the swash plate 2 and the piston 6
Journal part 2 of swash plate 2 even when connecting with 0
Since a and the flat plate portion 2b are integrated, the sliding shoes 4 and 5 are incorporated into the connecting portions 9 and 10, and the swash plate is maintained while the sliding shoes 4 and 5 are present in the connecting portions 9 and 10. 2 to both sliding shoes 4,5
There is a problem that a laborious work of mounting the shaft 1 after it is inserted into the space requires a troublesome work of assembling.

The present invention has been made in view of the above-mentioned problems of the prior art, and it is possible to increase the running allowance of the sliding shoe, increase the discharge amount of the refrigerant and the like, and workability in assembling the swash plate and the like. The object of the present invention is to provide a variable capacity swash plate type compressor that is good and can rotate at high speed.

[0020]

The present invention for achieving the above object is constructed as follows for each claim. According to a first aspect of the present invention, a crank chamber, a shaft provided so as to pass through the crank chamber, a swash plate provided in the crank chamber and tiltable with respect to an axis of the shaft, A hinge mechanism that transmits the rotation of the shaft to the swash plate, and a plurality of units that are connected by a connecting portion via a sliding shoe so that the swash plate can slide inside, and each of which is provided so as to be linearly reciprocally movable in the cylinder chamber. And a swash plate compressor configured to convert the swash plate's sloping rotary motion into a reciprocating linear motion of the piston, the swash plate having a journal portion near the shaft and the journal. The flat plate portion provided on the outer side in the radial direction of the flat portion is formed as a separate body, and the flat plate portion is made of a material having a high Young's modulus and the flat plate portion is formed as much as possible. Characterized in that the thin-walled. The flat plate portion according to the invention of claim 2 is made of steel. A flat plate portion according to a third aspect of the invention is configured to be attached to the journal portion.

[0021]

According to the present invention having the above-described structure, each claim operates as follows. In the invention according to claim 1, when the flat plate portion of the swash plate is made of a material having a Young's modulus higher than that of the cast iron journal portion, when the same strength as the conventional one is obtained, the flat plate portion becomes It can be made considerably thinner than that of the other one, the weight of the swash plate that makes the razor movement can be reduced, and it can be rotated at a higher speed.Even with a single-head variable capacity swash plate compressor, the discharge amount of refrigerant etc. Can be in any desired amount. Moreover, the stroke of the piston can be made larger than that of the conventional one by thinning the flat plate portion of the swash plate, which also increases the discharge amount of the refrigerant and the like.

Further, since the journal portion and the flat plate portion are constructed separately, if the flat plate portion is connected to the connecting portion of the piston and then connected to the journal portion, the troublesome installation of the sliding shoe is relatively easy. As a result, the workability of assembly is also improved.

If the flat plate portion is made of steel as in the second aspect of the present invention, the cost of the swash plate can be relatively low when the strength of the swash plate is increased.

If the flat plate portion is mounted on the journal portion as in the third aspect of the invention, the workability of assembling is further improved.

[0025]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic sectional view of a single-head type variable capacity swash plate compressor according to an embodiment of the present invention,
FIG. 2 is an enlarged view of a main part of FIG. 1, and members common to those shown in FIGS. 3 to 5 are given the same reference numerals.

In the variable displacement swash plate compressor shown in FIG. 1, a cylinder block 21 is housed in a tubular case 20, and a rear housing 20r is provided on the right end side of the tubular case 20.
Is provided, and a front housing 20f is provided on the left end side, and both housings 20r and 20f are connected by a bolt V.

At the center of the front housing 20f,
A through hole 23 for inserting the shaft 1 is bored, a radial bearing 24 for rotatably supporting the shaft 1 is press-fitted into the through hole 23, and an oil seal 25 is also arranged in the vicinity of the radial bearing 24. ing.

A crank chamber 3 is defined between the inner wall of the front housing 20f and the cylinder block 21, and the shaft 1 in the crank chamber 3 is located near the front housing.
A hinge mechanism K that transmits the rotation of the shaft 1 to the swash plate 2 is provided.

As will be described later in detail, the swash plate 2 has a journal portion 2a and a flat plate portion 2b as separate bodies, and these two are connected by a screw portion N.

In the hinge mechanism K, the base end is fitted to the shaft 1 and the rotary arm 26 is provided with a long hole 26b in the distal end portion 26a and the distal end of the rotary arm 26 from the rear surface of the journal portion 2a of the swash plate 11. A driven arm 29 which is projected toward the portion 26a and has a hole corresponding to the elongated hole 26b.
And a pin 30 inserted through the long hole 26b.

A spherical bush 28 repelled by springs B1 and B2 is provided on the shaft 1 so as to be slidable in the axial direction on the shaft 1. The spherical surface of the spherical bush 28 is the center of the journal portion 2a of the swash plate 2. The journal portion 2a and the spherical bush 28 are opposed to the inner peripheral surface of the center hole O formed in the center hole O. The pair of pins 31 project from the journal portion 2a along the central axis of the spherical bush 28. Are connected by. Therefore, the swash plate 2 has the shaft 1
It is possible to rotate about the pin 31 while being rotated by.

A thrust bearing 31t is provided between the inner wall surface of the front housing 20f and the rotary arm 26.

The other end of the shaft 1 is connected to the cylinder block 2
1, is rotatably supported by a radial bearing 31r, and a thrust bearing 32 is provided on the end surface of the shaft 1.

A plurality of pistons 6 are provided on the swash plate 2, and the swash plate 2 and individual pistons 6 are connected by sliding shoes 4 and 5, respectively.

The sliding shoes 4 and 5 are flat surfaces 4a and 5a which are finished to be smooth so as to slide on the flat portion 2b of the swash plate 2, and spherical concave portions 9s and 10s of the connecting portions 9 and 10, respectively. It has spherical convex surfaces 4b and 5b which are fitted in concave and convex, and is adapted to convert the rubbing rotary motion of only the swash plate 2 into the reciprocating linear motion of the piston.

A suction port 35 for sucking the refrigerant and a discharge port 36 for discharging the refrigerant are formed on one end surface of the silicidator chamber 7, and the refrigerant flows to the suction port 35 and the discharge port 36. A valve plate 39 including valve forming plates 37 and 38 having a plurality of intake valves and discharge valves for controlling the above is provided.

The return refrigerant from the evaporator flows into the suction port 35 through the suction chamber 40, and the elastic return force of the suction valve formed on the valve forming plate 37 on the left side of the valve plate 37 in the figure is applied. On the contrary, the gas flows into the cylinder chamber 7 in the suction process. Further, the refrigerant compressed by the piston is discharged to the discharge port 36 against the elastic closing force of the discharge valve formed on the valve forming plate 38 on the right side of the valve plate 37 in the figure, and this refrigerant is The discharge port 36 leads the discharge chamber 41.

Further, a control valve Cv for adjusting the pressure state in the crank chamber 3 and adjusting the inclination angle of the swash plate 2
Is installed in the rear housing 20r. The control valve Cv adjusts the pressure in the crank chamber 3 in accordance with the suction pressure of the returning refrigerant to change the angle of the swash plate 2 to adjust the amount of refrigerant discharged from the compressor, so that the suction pressure of the compressor is It is controlled to be constant.

That is, since the swash plate 2 is provided with a plurality of pistons 6 at equal angular intervals, a reaction force due to refrigerant compression is applied to the swash plate 2 from the piston 6 in the compression stroke, and each piston 6 A moment M1 acts around the hinge mechanism K by the reaction force acting on. This moment M1 is
Since the moment generated by the piston 6 positioned farther from the pin 30 of the swash plate 2 is larger, it acts clockwise in FIG.

Further, the moment M2 acts counterclockwise due to the elastic force of the spring B1. Further, there is a moment M3 caused by the pressure difference between the crank chamber 3 and the suction chamber 40, but this moment M3 can be ignored because the pressure in the suction chamber 40 and the pressure in the crank chamber 3 are almost equal.

Here, the resilience of the spring B1 is M1> M2
The tilt angle of the swash plate 2 is increased by the moment acting clockwise about the hinge mechanism K. The swash plate 1 is inclined until the pin 30 of the hinge mechanism K contacts the upper end of the elongated hole 26b.

As a result, the stroke of the piston 6 is increased, the amount of discharged refrigerant is increased, the amount of refrigerant circulating in the cooling cycle is increased, and an appropriate amount of refrigerant is discharged according to the heat load, and the suction pressure of the compressor is increased. Will gradually fall, and will eventually be maintained at a constant suction pressure.

In particular, in the present embodiment, the swash plate 2 has a journal 2a made of cast iron and a flat plate 2 made of steel having a high Young's modulus.
b is formed separately, and both are connected by a screw portion N. However, the connection between the two is not limited to the screw connection, and the connection may be made by other means such as press fitting.

Generally, the swash plate 2 is subjected to a compression reaction force generated when the piston 6 advances and compresses the refrigerant, and a piston inertial force generated when the piston 6 retracts, but the former compression reaction force. Is about 300 to 400 kg, while the value of the piston inertial force is about 30 kg.
It is about 1 kg, which is about 1/10 of the compression reaction force.

Therefore, the strength of the flat plate portion 2b of the swash plate 2 is a material having a high Young's modulus that can withstand a large compressive reaction force of 400 kg, which is the same as the conventional one, that is, mechanical strength such as tensile strength and bending rigidity. A material with high strength, specifically,
It is made of steel such as carbon steel or alloy steel, and the material forming the journal portion 2a to which relatively little force is applied is made of cast iron.

Thus, as shown by the broken line in FIG. 2, by thinning the swash plate 2, for example, the engagement margin S of the conventional sliding shoe 5 can be increased to Sa,
It is possible to reliably prevent the sliding shoes 4 and 5 from falling off. Further, the wall thickness T of the swash plate 2 is Ta.
As a result, the stroke of the piston 6 can be set longer and the discharge amount of the refrigerant or the like can be increased accordingly.

Next, the operation will be described. First, in order to assemble the swash plate portion of the variable displacement compressor, the spherical concave surfaces 9s, 1 of the connecting portions 9, 10 formed at the rear end portion of the piston 6 are assembled.
In 0s, hemispherical convex surface 4 of sliding shoes 4 and 5
Sliding shoes 4, with b and 5b fitted together
Swash plate 2 which is smaller and lighter than the conventional one between 5
Since it suffices that the sliding shoes 4 and 5 be mounted so that only the flat portion 2b thereof is positioned, the sliding shoes 4 and 5 can be easily mounted so as not to fall. If this state is maintained and the flat portion 2b and the journal portion 2a are connected by the screw portion N, the assembly can be performed very easily.

Next, the operation of the compressor will be described. When an electromagnetic clutch (not shown) is turned on and the shaft 1 is rotated by an engine (neither is shown) via a belt and a pulley, the rotating arm 26 is rotated accordingly, and the swash plate is rotated via the hinge mechanism K. 2 also rotates. When the swash plate 2 is tilted with respect to the shaft 1, the swash plate 2 pivots in a grazing motion, and the piston 6 reciprocates accordingly, so that the suction port 35 sucks into the cylinder chamber 7. The discharged refrigerant is compressed and discharged from the discharge port 36 into the discharge chamber 41.

Since the sliding shoes 4 and 5 only slide on the flat portion 2a of the swash plate 2 even if the swash plate 2 rotates, no rotational force is transmitted to the piston 6 and the sliding shoes 4 and 5 are inclined. The rotational force of the plate 2 is converted into the reciprocating motion of the piston 6.

Here, the heat load in the cooling cycle is
When the temperature is higher than the preset temperature, the suction pressure of the refrigerant becomes high.

In this case, a relatively high suction pressure is introduced into the crank chamber 14 by the action of the control valve Cv, so that the internal pressure thereof becomes substantially equal to the suction pressure.
Therefore, even in the piston 6 in the suction process, the pressure difference between the front and the rear is almost eliminated, and the piston 6 moves to the cylinder chamber 7
The inside of the piston 6 can be smoothly retracted, and the stroke of the piston 6 increases. If compression is performed in this state,
The amount of discharged refrigerant increases, the flow rate of the refrigerant that circulates in the cooling cycle increases, the appropriate refrigerant flow rate is again discharged according to the heat load, the suction pressure of the compressor gradually decreases, and finally the constant suction pressure. Will be kept.

On the other hand, when the heat load in the cooling cycle becomes small or the compressor rotates at a high speed to cause an excess of the refrigerant, the pressure of the returning refrigerant does not have a sufficient superheat amount, and the refrigerant returns at a low pressure to the suction chamber 40. The pressure of becomes low. In this case, by the action of the control valve Cv, the high pressure refrigerant compressed by the piston 6 and guided to the discharge port 36 is introduced into the crank chamber 3,
The internal pressure of the crank chamber 3 is increased. As a result, the moments of the forces applied to the plurality of pistons 6 centering around the pin 30 are different, and the above-mentioned moments become M1 <M2 + M3 at a certain point, and the swash plate 2 moves the hinge mechanism K. The tilt angle is reduced by the moment acting counterclockwise about the center. Therefore, the stroke of the piston 6 becomes smaller and the amount of discharged refrigerant decreases.

By the way, the suction, compression and discharge of the refrigerant are carried out by the swash plate 2 inclined with respect to the shaft 1 as described above.
This is done by bringing the piston 6 whose sliding direction is regulated by the cylinder chamber 7 into sliding contact with the sliding shoes 4 and 5 so as to convert the rubbing rotary motion of the swash plate 2 into the reciprocating motion of the piston 6. However, in this case, the frictional resistance increases due to insufficient lubrication or sudden activation, and a force acts in the direction in which the sliding shoes 4, 5 are pushed out due to the rotational movement of the swash plate 2 or the like. Also, the spherical concave portions 9s, 10 of the connecting portions 9, 10 of the piston 6
Since the engagement margin Sa between s and the sliding shoes 4, 5 is sufficiently secured, even if the piston 6 is at the top dead center position or the bottom dead center position, the sliding shoes 4, 5
Does not run near the ends of the spherical concave portions 9s, 10s on the shaft 1 side, let alone the sliding shoes 4, 5 bite and lock, or the sliding shoes 4, 5 fall out. Can be reliably avoided.

Further, since the engagement state between the sliding shoes 4, 5 and the connecting portions 9, 10 is also improved,
Operation with less vibration and noise is possible.

Moreover, if the swash plate 2 is formed of a material having a high Young's modulus so as to have a thin plate thickness Ta, the strength and rigidity required for the function of the swash plate 2 are not impaired.
The swash plate 2 can be rotated at a higher speed, and the stroke of the piston 6 can be increased, which increases the amount of discharged refrigerant. Even with a single-head variable displacement compressor, the desired amount of discharged refrigerant can be easily changed. Can be secured.

The present invention is not limited to the above-described embodiments, but can be variously modified within the scope of the claims. For example, in the above-described embodiment, the wall thickness is equally reduced from both sides of the swash plate 2, but the present invention is not limited to this, and the wall thickness may be reduced from one side by a predetermined amount. Maybe,
Various kinds of control valves can be used as the control valve of the present invention. For example, as a control means for adjusting the pressure in the crank chamber 3, a control valve having a structure in which a gas of a predetermined pressure is enclosed in a bellows, or a suction pressure is used. The bellows expands and contracts in response to this, and this operation opens and closes the valve to introduce high-pressure discharge pressure into the crank chamber 3 and at the same time cut off communication with the suction chamber 40, or cut off high-pressure discharge pressure to increase the crank chamber. It is also possible to use a system in which the pressure of the crank chamber 3 is reduced by communicating 3 with the suction chamber 40, or a system in which the pressure introduced into the crank chamber 3 is electronically controlled according to the heat load of the refrigeration cycle. can do. Further, a system in which the suction chamber 40 and the crank chamber 3 are always communicated with each other by an orifice and a high discharge pressure is introduced into the crank chamber 3 can be controlled.

[0057]

As described above, according to the present invention, the following effects can be obtained for each claim. According to the invention described in claim 1, since the flat plate portion of the swash plate is made of a material having a high Young's modulus and is made thin, the weight of the swash plate can be reduced, and the swash plate can be rotated at a higher speed. Even with the variable capacity swash plate compressor, the discharge amount of the refrigerant or the like can be set to a desired amount. Moreover, due to this thinning, the stroke of the piston can be increased, which also increases the discharge amount of the refrigerant and the like.

Further, since the journal portion and the flat plate portion are separately formed, if the flat plate portion is connected to the connecting portion of the piston and then connected to the journal portion, it is relatively easy to attach the sliding shoe. As a result, the workability of assembly is also improved.

According to the second aspect of the invention, since the flat plate portion is made of steel, it can be made relatively inexpensive when increasing the strength of the swash plate.

According to the third aspect of the present invention, the flat plate portion is attached to the journal portion, so that the assembling workability is further improved.

[Brief description of the drawings]

FIG. 1 is a schematic sectional view of a variable capacity swash plate compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged explanatory view of a main part of FIG.

FIG. 3 is a schematic cross-sectional view of a conventional variable displacement swash plate compressor.

FIG. 4 is an enlarged view of a main part of the compressor.

FIG. 5 is an enlarged explanatory view of a main part of FIG.

[Explanation of symbols]

1 ... Shaft, 2 ... Swash plate, 2a ... Journal part, 2b ... Flat plate part, 3 ... Crank chamber,
4, 5 ... sliding shoe, 6 ... piston,
7 ... Cylinder chamber, 9, 10 ... Connection part,
K ... Hinge mechanism.

Claims (3)

[Claims] 1. A crank chamber (3), a shaft (1) provided so as to be inserted through the crank chamber (3), and an axis line of the shaft (1) arranged in the crank chamber (3). A swash plate (2) tiltably provided, a hinge mechanism (K) for transmitting the rotation of the shaft (1) to the swash plate (2), and the swash plate (2)
Sliding shoes (4,
5) is connected by connecting portions (9, 10), and each has a plurality of pistons (6) provided in the cylinder chamber (7) so as to be linearly reciprocable, and the swash plate (2) In a swash plate type compressor configured to convert a sledding rotational motion into a reciprocating linear motion of a piston (6), the swash plate (2) is a journal part near the shaft (1).
(2a) and the flat plate portion (2b) provided on the outer side in the radial direction of the journal portion (2a) are separately formed, and the material forming the flat plate portion (2b) is made of a material having a high Young's modulus. A swash plate compressor characterized in that the flat plate portion (2b) is made as thin as possible. 2. The swash plate compressor according to claim 1, wherein the flat plate portion (2b) is made of steel. 3. The flat plate portion (2b) is provided with the journal portion (2).
The device according to claim 1, which is configured to be attached to a).
Alternatively, the swash plate compressor described in 2.