JPH08303346A - Displacement variable swash plate type compressor - Google Patents

Abstract

PURPOSE: To prevent uneven wearing of a drive swash plate and sleeve and abnormal sounds by suppressing the blacklash of the drive swash plate of displacement variable swash plate type compressor. CONSTITUTION: A drive swash plate 15 and a rotation supporting member 21 are brought into contact with each other in two points by two projecting parts 50 and 50, when the drive swash plate 15 is inclined to maximum. The drive inclined plate 15 is supported by three points, i.e., two projecting parts 50 and 50 and a hinge mechanism H.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity swash plate compressor used in an air conditioner for automobiles, and more particularly to a compressor which prevents uneven wear and abnormal noise due to rotation of the swash plate.

[0002]

2. Description of the Related Art A conventional variable capacity swash plate compressor is
It has a drive swash plate that is connected to the rotary support member that protrudes from the drive shaft in a direction perpendicular to the axis and is rotatably synchronously and that is variable in inclination angle via a hinge mechanism. The drive swash plate is attached to the drive shaft via a sleeve having a spherical peripheral surface so that the inclination angle is variable, and has a pair of connecting arms projecting from the rear side and a pair of supporting arms projecting from the rotation supporting member side. The long hole provided in the arm is connected by a pin to transmit the rotation of the rotation support member that rotates in synchronization with the drive shaft to the drive swash plate and support the force acting on the drive swash plate.

That is, a plurality of pistons provided in parallel to the cylinder block at predetermined intervals are connected to the outer peripheral portion of the drive swash plate via shoes to reciprocate the tilt rotary motion of the drive swash plate. While being converted into dynamic motion, the hinge mechanism supports the reaction force when each piston is compressed.

Since the stroke of the piston in this compressor is set to a predetermined length depending on the discharge capacity of the compressor, etc., the inclination angle of the drive swash plate that determines this stroke, that is, the inclination of the drive shaft with respect to the plane perpendicular to the axis. It is sufficient if the angle can take a predetermined maximum inclination angle from zero degree.

Therefore, in the conventional compressor, as shown in FIG. 4, the state where the drive swash plate 15 is substantially perpendicular to the drive shaft and the sleeve 20 and the rotation support member 21 are in contact with each other at the portion A shown in the figure. The maximum tilt angle is regulated so that it can rotate between these two angles.

However, even if the central portion of the drive swash plate 15 is supported by the sleeve 20 which is a spherical bearing, the central portion of the drive swash plate 15 is in spherical contact, so that it is not firmly supported firmly.
In the upper portion of the drive swash plate 15, a pair of connecting arms 24 projecting from the drive swash plate 15 and a pair of support arms 22 projecting from the rotation supporting member 21 side have a long hole 23 and a pin 25 as a hinge mechanism. Because they are linked by H,
So to speak, it is in a fluttered state, and the long hole 23
Drive swash plate 1 due to the gap that exists between the
5 causes rattling, which causes abnormal noise and uneven wear of the drive swash plate 15 or the rotation support member 21.

Therefore, the maximum inclination angle is not regulated by the contact between the sleeve 20 and the rotation support member 21 described above, and the drive swash plate 15 is contacted before the contact between the sleeve 20 and the rotation support member 21 occurs. The balancer 15b is proposed so as to contact the rotation support member 21.

That is, as shown in FIG. 5, an arcuate convex surface 40 is formed on the rotary support member 21, and the maximum inclination angle is regulated by the balancer 15b of the drive swash plate 15 contacting the convex surface 40. I am configuring. According to this structure,
When the drive swash plate 15 is tilted to the maximum, a gap exists in the portion A shown in FIG. 4, so that the above-described problems of noise generation and wear are solved.

[0009]

However, in the structure shown in FIG. 5, the arcuate convex surface 40 formed on the rotary support member 21 is not always accurately formed, and depending on the case, the balancer 15b may be formed. The rotation support member 21 may contact at one point, and since the upper portion of the drive swash plate 15 is supported in a fluttered state, the drive swash plate 15 can prevent backlash only by the one-point contact. Not
The fact is that the rattling of the drive swash plate 15 has not been eliminated yet.

The present invention has been made in view of the above problems, and provides a variable displacement swash plate compressor capable of preventing abnormal noise and wear by reliably preventing the drive swash plate from rattling. The purpose is to do.

[0011]

In order to achieve the above object, the invention according to claim 1 is a cylinder block in which a drive shaft is rotatably supported and a plurality of cylinder bores are formed around the drive shaft. And a housing coupled to the cylinder block and having a crank chamber or a discharge chamber formed therein,
A rotation supporting member that is housed in the crank chamber and rotates together with the drive shaft, is attached via a hinge mechanism to the rotation supporting member, and is provided between the drive shaft and the drive shaft so that the inclination angle can be displaced. A drive swash plate, a piston connected to the drive swash plate via a shoe, and a protrusion provided from the drive swash plate so as to contact the rotation supporting member when the drive swash plate is tilted to the maximum. In a variable displacement swash plate compressor having a balancer provided, a convex portion is formed so that the rotary support member and the balancer are in two-point contact when the drive swash plate is tilted to the maximum.

The two convex portions may be formed on the rotation supporting member or the driving swash plate, and one of the two convex portions is formed on the rotation supporting member and the other is formed. Can also be formed on the drive swash plate.

According to a second aspect of the present invention, the two convex portions are arranged so as to be laterally distributed with respect to a straight line connecting a center of a fulcrum of the hinge mechanism and a center of the drive shaft.

[0014]

According to the invention of claim 1 having such a configuration, when the drive swash plate is tilted to the maximum, the drive swash plate and the rotation support member are surely brought into contact with each other at two points by the two convex portions. When the drive swash plate is maximally tilted, the convex portion reliably prevents the hinge mechanism from rattling, and it is possible to prevent uneven wear and abnormal noise of the drive swash plate or other parts.

According to a second aspect of the present invention, the two convex portions are
The points supporting the drive swash plate are arranged substantially evenly with respect to the center of the drive swash plate because they are arranged so as to be laterally distributed with respect to a straight line connecting the fulcrum center of the hinge mechanism and the drive shaft center point. The rattling of the drive swash plate is further suppressed,
Uneven wear and abnormal noise of the drive swash plate or other parts can be more reliably prevented.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. 1 is a vertical sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention, FIG. 2A is a sectional view taken along line 2-2 of FIG. 1, and FIG. 2B is FIG. 2) is an enlarged cross-sectional view taken along the line P-P in FIG. 3 and FIG. 3 is a vertical cross-sectional view of a main part of a variable capacity swash plate compressor according to another embodiment of the present invention. The members common to those shown in FIGS. 4 and 5 are designated by the same reference numerals.

This variable capacity swash plate type compressor 10 is
A cylinder block 12 that rotatably supports a drive shaft 11 that is rotationally driven by an engine (not shown) is provided. One end of the cylinder block 12 internally has the crank chamber 1
The front housing 14f is attached so as to form 3 and the rear housing 14r is attached to the other end so that the discharge chamber 26 is formed inside.

In the crank chamber 13, the drive shaft 1
1 is provided with a substantially disk-shaped drive swash plate 15 and a plurality of single-headed pistons 16. Each single-headed piston 16 has a cylinder block 1 around a drive shaft 11.
It is housed in each of a plurality of cylinder bores 12a formed in the No. 2 cylinder. Each piston 16 has a head 17 and a neck 1.
8 and an outer edge portion 15a of the drive swash plate 15 on the neck portion 18.
Are connected via substantially hemispherical shoes 19a, 19b.

A sleeve 20 having a spherical peripheral surface 20a slidable in the axial direction is mounted on the drive shaft 11, and a drive swash plate 15 is swingably abutted and supported on the spherical peripheral surface 20a of the sleeve 20. ing. The rotation support member 2 is attached to the drive shaft 11.
1 is mounted so as to rotate synchronously with the drive shaft 11, and has a pair of support arms 22a protruding from the rotation support member 21.
An arc-shaped long hole 23 is formed at the tip of 22b, and a pin 25 provided on a pair of connecting arms 24 extending from the drive swash plate 15 side is fitted into the long hole 23 to form a hinge mechanism H. The drive swash plate 15 can rotate on the outer peripheral surface 20a of the sleeve 20 about the pin 25 while being rotated by the drive shaft 11.

The inclination angle displacement of the drive swash plate 15 is set by opening and closing the communication passage R, which connects the crank chamber 13 and the discharge chamber 26 provided in the cylinder block 12, with the control valve Cv.
This is done by adjusting the pressure in the crank chamber 13.

That is, the valve plate 27 sandwiched between the rear housing 14r and the cylinder block 12 is formed with the suction port 30 and the discharge port 31, and the suction port 30.
The return refrigerant having the suction pressure Ps flows into the chamber through the suction chamber 32, and the refrigerant having the discharge pressure Pd, which is compressed by the piston 16 from the discharge port 31, is formed on the valve plate 33 (not shown). Overcoming the elastic closing force of the discharge chamber 26
It is designed to be discharged.

Although not shown, the crank chamber 13 and the suction chamber 3
2 communicates with the crank chamber 1 through an orifice.
By controlling the opening / closing of the control valve Cv provided in the communication passage R that connects the discharge chamber 26 with the discharge chamber 26, the high pressure discharge pressure Pd is introduced into the crank chamber 13 to increase the pressure in the crank chamber 13, thereby increasing the pressure in the front and rear of the piston. Control can be performed to increase the pressure difference or to stop the introduction of the high discharge pressure Pd into the crank chamber 13 to reduce the pressure in the crank chamber 13 to eliminate the pressure difference between the front and the rear of the piston. The inclination angle of the drive swash plate 15 is controlled.

For example, when the heat load is small and the return refrigerant has a low pressure, that is, when the suction pressure Ps is low, the suction chamber 32
Since this refrigerant pressure is introduced into the chamber a that is in communication with
The diaphragm b is assisted by the spring force of the spring c to move leftward in the drawing, the valve d is opened, and the high pressure refrigerant in the discharge chamber 26 at the discharge pressure Pd is guided to the crank chamber 13 through the passage e and the communication passage R. Then, the pressure in the crank chamber 13 is increased. Due to this, due to the pressure difference applied to both surfaces of the plurality of pistons 16, the combined force of the forces applied to the back surface acts as a moment about the pin 25, and acts so as to decrease the tilt angle of the drive swash plate 15, The piston 16 in the suction process cannot retract so as to have a sufficiently large stroke, which reduces the amount of compressed discharge of the refrigerant.

On the contrary, when the heat load is large and the return refrigerant has a high pressure, that is, when the suction pressure Ps is high, this refrigerant pressure is introduced into the chamber a communicating with the suction chamber 32. Against the spring force of, go to the right in the figure,
The valve d closes. As a result, the introduction of the discharge pressure is stopped, the pressure in the crank chamber 13 is reduced by the communication passage between the crank chamber 13 and the suction chamber 32, and the pressure in the crank chamber 13 is reduced. In this case,
The maximum is equivalent to the suction chamber 32 side. Therefore, the inclination angle of the drive swash plate 15 is maximized due to the action of the moment described above, and the reciprocating stroke of the piston 16 is lengthened. As a result, the amount of compression of the refrigerant increases.

Various types of control valves Cv can be used. For example, a bellows type valve in which a bellows expands and contracts due to a difference in pressure of the surrounding suction refrigerant gas to enclose a gas for opening and closing the valve. Alternatively, the valve may be electrically opened and closed. A valve that simultaneously controls the communication passage between the crank chamber and the discharge chamber and the communication passage between the crank chamber and the suction chamber may be used.

In particular, in this embodiment, as shown in FIGS. 1 and 2, two convex portions 50, 50 are formed on the rotation supporting member 21, and when the drive swash plate 15 is tilted to the maximum, the drive tilt is increased. The tip end of the balancer 15b provided on the plate 15 is brought into contact with these convex portions 50, 50 so as to make two-point contact.

The protrusions 50, 50 in this embodiment are shown in FIG.
As shown in FIG. 5, the lines are evenly distributed to the left and right with respect to the straight line L connecting the center of the fulcrum of the hinge mechanism H and the center of the drive shaft 11. As a result, when the drive swash plate 15 is tilted at its maximum, if the hinge mechanism H is supported at one point, the drive swash plate 15 is supported at three points for the convenience of the two protrusions 50, 50, and the drive is performed. Since the swash plate 11 is evenly supported with respect to the center thereof, the drive swash plate 15 does not rattle even when the drive shaft 11 rotates at a high speed. Uneven wear of the drive swash plate 15 or other members can be prevented.

Next, the operation of the embodiment will be described. When the cooling cycle operation is performed with a certain heat load, the drive swash plate 15 is rotated at a predetermined inclination angle so that the refrigerant discharge capacity corresponding to the heat load is obtained by the action of the control valve Cv.
The rotation of the drive swash plate 15 is transmitted to the single-headed piston 16 via the shoes 19a and 19b, and the piston 16 is
It reciprocates while sliding in the cylinder bore 12a.

When the return refrigerant has a high pressure, that is, the suction pressure Ps
When is high, this refrigerant pressure is introduced into the chamber a that is in communication with the suction chamber 32, so that the diaphragm b resists the spring force of the spring c and moves rightward in FIG. 1 to close the valve d. This allows
The introduction of the discharge pressure stops and the pressure in the crank chamber drops because it escapes to the suction chamber. Therefore, the inclination angle of the drive swash plate 15 is maximized due to the action of the moment described above, the reciprocating stroke of the piston 16 is lengthened, and as a result, the refrigerant compression amount is increased.

At this time, that is, when the drive swash plate 15 is at the maximum inclination angle, the balancer 15b of the drive swash plate 15 abuts the two convex portions 50, 50 formed on the rotation support member 21, and the inclination angle is Although the drive swash plate 15 is rotated at such a maximum tilt angle, the drive swash plate 15 is prevented from becoming larger than that by the hinge mechanism H in this embodiment.
And the two convex portions 50, 50 are supported at three points for convenience, and moreover, they are evenly supported with respect to the center of the driving swash plate 11, so that the driving swash plate 15 does not rattle and is a so-called striking member. Noise such as noise can be prevented, and uneven wear of the drive swash plate 15 or other members due to backlash can be prevented.

The present invention is not limited to the above embodiments, but can be variously modified within the scope of the claims. For example, in the above embodiment, the protrusion 50 is formed on the rotation support member 21, but the protrusion according to the present invention may be provided on the balancer 15b of the drive swash plate 15 in addition to the rotation support member 21. FIG. 3 is a longitudinal sectional view of a main part of a variable displacement swash plate compressor showing another embodiment of the present invention. In this case, the two convex portions 50, 50 are the balancer 15b.
Is formed at the tip of. Then, the convex portions 50, 50
When the drive swash plate 15 reaches the maximum inclination angle, the drive swash plate 15 is brought into contact with the rotation support member 21 to cause the two protrusions 50,
50 and the hinge mechanism H are supported at three points. Further, although not shown, one of the two protrusions 50, 50 may be formed on the rotation support member 21, and the other protrusion 50 may be formed on the balancer 15b of the drive swash plate 15.

Further, in the above-mentioned embodiment, the drive swash plate 1 is used.
5 is attached to the drive shaft 11 via the sleeve 20 having the spherical peripheral surface 20a, the present invention is not limited to the sleeve having the spherical peripheral surface, and a universal joint in which the drive shaft is connected to the drive swash plate by a pin is also used. It can also be applied to the variable capacity swash plate compressor used.

[0033]

As described above, according to the present invention, when the drive swash plate is tilted to the maximum, the drive swash plate and the rotation support member are in contact with each other at two points by the two convex portions. Backlash is eliminated, and uneven wear and abnormal noise of the drive swash plate or other parts can be prevented.

Particularly, when the two convex portions are arranged so as to be laterally distributed with respect to the straight line connecting the fulcrum center of the hinge mechanism and the drive shaft center point, the point supporting the drive swash plate is located at the center of the drive swash plate. Since the driving swash plate is arranged substantially evenly, rattling of the driving swash plate is further suppressed, and uneven wear or abnormal noise of the driving swash plate or other portions can be more reliably prevented.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing an embodiment of the present invention.

2 (A) is a sectional view taken along line 2-2 of FIG.
FIG. 2B is an enlarged cross-sectional view taken along the line P-P of FIG.

FIG. 3 is a longitudinal sectional view of a main part showing another embodiment of the present invention.

FIG. 4 is a cross-sectional view of essential parts showing a conventional variable displacement swash plate compressor.

FIG. 5 is a front view showing a rotation supporting member in a conventional variable displacement swash plate compressor.

[Explanation of symbols]

11 ... Drive shaft, 12 ... Cylinder block, 12a ... Cylinder bore, 13 ... Crank chamber, 14f, 14r ... Housing, 15 ... Drive swash plate,
15b ... balancer, 16 ... piston, 1
9a, 19b ... shoe, 20 ... sleeve,
21 ... Rotating support member, 22 ... Support arm,
24 ... connecting arm, 25 ... pin,
H ... Hinge mechanism, 50 ... Convex part.

Claims (2)

[Claims] 1. A drive shaft which rotatably supports a drive shaft (11).
A cylinder block (12) having a plurality of cylinder bores (12a) formed around (11) and a crank chamber (13) or a discharge chamber (26) formed inside the cylinder block (12). A housing (14f, 14r) and a rotation support member housed in the crank chamber (13) and rotating together with the drive shaft (11).
(21), a drive which is attached via a hinge mechanism (H) to the rotation support member (21) and is provided between the drive shaft (11) and a drive shaft (11) via a sleeve (20) so that the tilt angle can be displaced. The swash plate (15), the piston (16) connected to the drive swash plate (15) via shoes (19a, 19b), and the rotation support when the drive swash plate (15) is tilted to the maximum. The driving swash plate (15) so as to abut the member (21)
A variable capacity swash plate compressor having a balancer (15b) provided so as to project from the drive swash plate (15)
A variable capacity swash plate compressor characterized in that convex portions (50, 50) are formed so that the rotary support member (21) and the balancer (15b) are in contact with each other at two points when the maximum inclination. 2. The two convex portions (50, 50) are arranged so as to be laterally distributed with respect to a straight line connecting a fulcrum center of the hinge mechanism (H) and the drive shaft center point. The variable capacity swash plate compressor according to claim 1.