JPH0668273B2 - Swing swash plate compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention converts the rotational movement of a pair of front and rear rotary drive plates whose tilt angle is variable via a pair of front and rear swing swash plates into a reciprocating linear movement of both front and rear pistons. At the same time, the compression capacity is changed by changing the inclination angle of both the front and rear swing swash plates by the pressure difference between the suction pressure and the pressure in the crank chamber that houses the front and rear rotation drive plates and the front and rear swing swash plates. The present invention relates to a rocking swash plate type compressor to be controlled.

[Prior Art] In this type of rocking swash plate type compressor disclosed in Japanese Patent Laid-Open No. 62-55477, suction and discharge are performed before and after the compressor. The stability of the rotational balance is superior to that of the swash plate type compressor that sucks and discharges only on one side before and after the compressor, and noise or vibration can be reduced. Further, the diameter of the piston can be reduced by doubling the number of cylinders, and the overall diameter of the compressor, which is required to be compact, can be reduced.

[Problems to be Solved by the Invention] However, although the assembly structure from the connecting portion of the rotary drive plate and the swing swash plate to the connecting portion of the piston rod and the piston, although each constituent member is the same before and after, It is inevitable that front and rear assembly errors, component dimensional errors, and friction errors in sliding parts will occur, and the tilt angle variable rate of the front and rear swing swash plates that swing independently of each other will cause the above error. Due to this, a difference easily occurs. Such a difference in the variable ratio causes an imbalance between the front and rear suction and discharge, which causes an increase in the noise level and an increase in the torque fluctuation or the discharge pulsation of the entire compressor.

[Means for Solving the Problems] Therefore, in the present invention, the swing center axes of both the front and rear rotary drive plates are shifted from each other by 180 ° in the rotational direction of the rotary shaft, and the front rotary drive plate and the rear rotary drive plate are linked. It was operatively linked so that it could be linked.

[Action] The link mechanism is displaced symmetrically about the axis of symmetry,
When the link mechanism is displaced, the shaft connecting portion between the link mechanism and the rotary drive plate is displaced symmetrically about the center axis of symmetry. Due to this symmetrical displacement, the swing displacement of one of the front and rear swing swash plates is transmitted as an equivalent swing displacement to the local swing swash plate via the link mechanism, and the front and rear swing swash plates have the same tilt angle. Shows variability.

[Embodiment] An embodiment embodying the present invention will be described below with reference to FIGS.

A front cylinder block 1 and a rear cylinder block 2 that form a housing of the entire compressor are joined and fixed to each other, and a front housing 3 is joined and fixed to a front end of the front cylinder block 1 and a rear cylinder block 2 is formed. A rear housing 15 is joined and fixed to the rear end. A crank chamber C is formed between the front and rear cylinder blocks 1 and 2, and the front housing 3 and
A rotary shaft 4 is rotatably supported on the front cylinder block 1 and the rear cylinder block 2 through a crank chamber C.

In the crank chamber C, a rotary support 5 is fixed to the rotary shaft 4, a support arm 6 is provided in front of the rotary support 5, and a long hole 6a is provided at the tip of the support arm 6. Is transparently installed. A pin 7 is slidably fitted in the long hole 6a, and a front rotation drive plate 8 is connected to the pin 7 with a variable tilt angle. Similarly, a support arm 9 is provided on the rear surface of the rotary support 5 so as to project at a position deviated by 180 ° from the projecting position of the support arm 6 in the circumferential direction about the rotation axis l ₁ of the rotation shaft 4. with the arm 9 tip is Toru設long hole 9a elongated hole 6a and axisymmetric position, the axis l ₂ to be the center of symmetry is set to a position perpendicular to the rotational axis l ₁ of the rotary shaft 4 There is. A pin 10 is slidably fitted in the long hole 9a, and a rear rotation drive plate 11 is connected to the pin 10 with a variable tilt angle.

Sleeves 12 and 13 are slidably supported on the rotary shaft 4 in front of and behind the rotary support 5, and shaft pins 12a (only one of which is shown) projecting from the left and right sides of the sleeve 12 are attached to the front rotary drive plate 8. While engaging with the engaging hole (not shown)
Shaft pins 13a (only one of which is shown) projecting from the left and right sides of the sleeve 13 are engaged with engagement holes (not shown) of the rear rotation drive plate 11. As a result, the front and rear rotation drive plates 8 and 11 are rotated
The shaft pins 12a and 13a, which can be displaced in any direction, can be swung in the direction of the rotary shaft 4.

A front swing swash plate 14 is rotatably supported on the front surface of the front rotary drive plate 8 so that the crank chamber C, the suction chamber 3a and the discharge chamber 3b in the front housing 3 are connected to each other. A front piston 17 and a front swash plate 14 in a plurality of cylinder bores 16 penetrating in 1 are connected by a piston rod 18. Similarly, a rear swing swash plate is provided on the rear surface of the rear rotary drive plate 11.
A rear piston is provided in a plurality of cylinder bores 20 which are rotatably supported by the rear cylinder block 2 so as to connect the crank chamber C, the suction chamber 15a and the discharge chamber 15b in the rear housing 15 to each other. 21 and rear swing swash plate 19
And are connected by a piston rod 22. Therefore,
The rotary motion of the rotary shaft 4 is oscillated through the rotary drive plates 8 and 11.
The pistons 17 and 21 are moved back and forth in the cylinder bores 16 and 20 by being converted into forward and backward reciprocating swings of 14 and 19. This allows the suction chambers 3a, 15
The refrigerant gas sucked into the cylinder bores 16 and 20 from a is discharged to the discharge chambers 3b and 15b while being compressed, but depending on the pressure difference between the pressure in the crank chamber C and the suction pressure via the pistons 17 and 20. As a result, the strokes of the pistons 17, 21 change, and the tilt angles of the swing swash plates 14, 19 that affect the compression capacity change.

In the rotary support 5, the support shaft 23 is in axial symmetry with both elongated holes 6a, 9
It is fixed through so that it passes through the symmetry center axis l ₂ of a,
The pins 7 and 10 and the support shaft 23 are parallel to each other. Center links 24 and 25 are rotatably supported at both projecting ends of the support shaft 23. One end of the center links 24 and 25 on the same side and the pin 10 are connected by the front links 26 and 27, and the other end of the center links 24 and 25 and the pin 7 are connected by the rear links 28 and 29. There is. Shaft pins 24a, 25a connecting the center links 24, 25 and the front links 26, 27, and shaft pins 24b, 25 connecting the center links 24, 25 with the rear links 28, 29.
b is set at an axially symmetrical position about the support shaft 23, and the distance from the pin 10 to the shaft pins 24a and 25a is set to be the same as the distance from the pin 7 to the shaft pins 24b and 25b.

A control valve mechanism 30 is built in the rear housing 15,
Bellows 31 with a valve hole 30a communicating with the discharge chamber 15b communicating with the outside
It is openably closed by a ball valve 33 which is acted upon by an internal pressing spring 32. When the ball valve 33 opens the valve hole 30a, the discharge chamber 15b communicates with the crank chamber C through the valve hole 30a and the passage 34 which serve as a pressure control passage, and the pressure in the crank chamber C is controlled by the discharge pressure.

The front rotation drive plate 8 and the rear rotation drive plate 11 whose tilt angles are controlled by the pressure difference between the pressure in the crank chamber C and the suction pressure via the pistons 17, 21 are center links 24, 25 which form a link mechanism, Front links 26, 27 and rear links 2
They are connected by 8, 29, and when one swing swash plate is displaced by displacement, the other swing swash plate is interlocked. Center link 24,2
Shaft pins 24a, 25a connecting 5 and the front links 26, 27
And the shaft pins 24b, 25b connecting the center links 24, 25 and the rear links 28, 29 have an axially symmetric relationship about the support shaft 23, and guide the pin 7 connected to the front links 26, 27. Long hole 6a to regulate and pin 1 connected to rear links 28 and 29
The long hole 9a that guides and regulates 0 has an axisymmetric relationship with the support shaft 23 as the center. Both pins 7 and 10 are guided and arranged in the long holes 6a and 9a at axially symmetrical positions around the support shaft 23. Therefore, the link mechanisms 24, 26 and 28 are the pin 7, the pin 10, the shaft pin 24a and the shaft pin 2
It is a parallel four-bar link mechanism having a center of symmetry on the support shaft 23 with the four-axis positions of 4b as nodes.
7,29 is a four-bar link mechanism having a center of symmetry on the support shaft 23 with four shaft positions of the pin 7, the pin 10, the shaft pin 25a and the shaft pin 25b as nodes. Accordingly, one swing displacement of one of the front and rear swing swash plates 14 and 19 is caused by the parallel four-bar link mechanism 24 to It is transmitted as an equivalent swing displacement to the other by the parallel displacement action of 29. Such equal displacement before and after greatly improves the stability of the compression balance of the piston and the rotational balance of the rotary drive plate between the front and rear, and significantly reduces the torque fluctuation or discharge pulsation of the entire compressor that leads to an increase in the noise level. To do.

The present invention is, of course, not limited to the above-mentioned embodiment, and instead of connecting the front links 26, 27 and the rear links 28, 29 to the pins 7 and 10, in the above-mentioned embodiment, the shaft pin 12a and Axis pin 13a of sleeve 13
May be connected to the shaft pin 12a and the shaft pin 13 in this case.
A parallel four-node link mechanism having a center of symmetry on the support shaft 23 with the four axis positions of a, the shaft pins 24a, 25a, and the shaft pins 24b, 25b as nodes is configured.

The embodiment shown in FIGS. 3 and 4 is also possible. In this embodiment, the links 35 and 36 are rotatably supported by the support shaft 23.
5 at both ends in the long hole 35a, 35b together are provided in axial symmetry about the axis l ₂ on the support shaft 23, also (only one) long hole 36b at both ends of the link 36 is the axis It is provided in axial symmetry about l ₂ . The long hole 35a is inclined with respect to the long hole 6a, and the long holes 35b, 36b are inclined with respect to the long hole 9a. The pin 7 is fitted into the long hole 35a and the long hole 3a
A pin 10 is fitted in 5b and 36b. Therefore, the position of the pin 7 is restricted at the intersection of the long hole 6a and the long hole 35a, and
The position of the pin 10 is regulated at the intersection of the long hole 9a and the long holes 35b and 36b, and both intersections are located at axially symmetrical positions about the axis l ₂ . As a result, the front and rear swing swash plates 14 and 19 interlock with each other to exhibit the same swing displacement.

[Effects of the Invention] As described in detail above, according to the present invention, since the front and rear rotary drive plates are operatively connected by the link mechanism so that the swing displacements of the front and rear rotary drive plates are equivalent, compression of the piston between the front and rear is performed. The stability of the balance and the rotational balance of the rotary drive plate is greatly improved, and the excellent effect that the torque fluctuation or the discharge pulsation of the entire compressor, which leads to the increase of the noise level, can be significantly reduced is exhibited.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an embodiment embodying the present invention,
2 is a sectional view taken along the line AA of FIG. 1, FIG. 3 is a sectional view of an essential part showing another example, and FIG. 4 is a sectional view taken along the line BB of FIG. The rotary shaft 4, the swing center axis line, and the pins 7 and 10 that serve as the shaft connecting portion,
The front rotary drive plate 8, the rear rotary drive plate 11, the support shaft 23, which is the axis of the center of symmetry, and the link mechanisms 24, 25, 26, 27, 28, 29.

Front page continued (72) Inventor Masaki Ota 2-chome Toyota-cho, Kariya city, Aichi Prefecture Toyota Industries Corporation (56) References JP 62-55477 (JP, A)

Claims (1)

[Claims] 1. A crank chamber, front and rear suction chambers, front and rear discharge chambers, and front and rear cylinder bores connecting these chambers are defined and formed, and a front piston and a rear piston are accommodated in the front and rear cylinder bores so as to be capable of reciprocating linear movement. A front swing swash plate, which supports a pair of rotary drive plates before and after a rotary support on a rotary shaft in a housing with a variable tilt angle, and is supported on the front rotary drive plate so as to be relatively rotatable, and the front swing swash plate. The rotary motion of the rotary drive plate is converted into the reciprocating linear motion of the front piston via the piston rod interposed between the moving swash plate and the front piston, and the rear supported on the rear rotary drive plate for relative rotation. Through the swing swash plate and the piston rod interposed between the rear swing swash plate and the rear piston, the rotary motion of the rotary drive plate is reciprocated by the rear piston. Oscillates due to the pressure difference between the suction pressure and the pressure in the crank chamber, which is controlled by the opening and closing of the control valve mechanism that is converted into the dynamic state and is connected to the pressure control passage that connects the discharge chamber and the crank chamber. In a swing swash plate type compressor that controls the tilt angle of the swash plate, the swing center axes of the front and rear rotary drive plates are displaced 180 ° from each other in the rotation direction of the rotary shaft, and the front rotary drive plate and the rear rotary drive plate are separated from each other. A rocking swash plate compressor that is operably linked by a link mechanism.