JPH0121356B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Object of the Invention (Field of Industrial Application) The present invention relates to a guide device for a swinging inclined plate in a variable displacement compressor used for vehicle air conditioning or the like.

(Prior art) A rotary support body is provided with a suction chamber, a discharge chamber, and a crank chamber, and a rotary support body is mounted on a drive shaft so as to be able to rotate synchronously, and a swinging inclined plate for reciprocating a piston is engaged with the rotary support body. A part of the inclined plate engages with a guide rail installed parallel to the drive shaft, allowing the inclined plate to swing back and forth, but preventing rotation around the drive shaft. The variable capacity compressor is equipped with a restraining guide device and the inclination angle of the swinging inclined plate is changed according to the differential pressure between the crank chamber pressure and the suction pressure to control the compression capacity. The guide device for the swinging inclined plate was constructed as shown in FIGS. 11 and 12. That is, a square columnar guide rail 42 is fixed with bolts 41 between the cylinder block and the front housing (not shown), and a shaped slider 43 is slid on the guide rail 42 in the longitudinal and vertical directions. Furthermore, the slider 43 is engaged with the swinging inclined plate 44 so as to be relatively rotatable in a direction perpendicular to the radial direction of the swinging inclined plate 44, so that the swinging inclined plate 44 can be swung in the front-rear direction. I was trying to allow some movement.

(Problems to be Solved by the Invention) However, in the conventional guide device, when the swinging inclined plate 44 is tilted in the front-rear direction, the inclined plate 44 does not receive the force exerted by the rotary support to rotate. Therefore, as shown by the chain line in FIG. 12, the sliding surface 43a of the slider 43 is pressed against the sliding surface 42a of the guide rail 42 fixed at a fixed position for noise prevention in an inclined state, and both sliding surfaces 42a , 43a hit unevenly, locally damaging the sliding surface and reducing durability.

Structure of the Invention (Means for Solving the Problems) The first invention has been made by focusing on the above-mentioned problems, and is directed to an inclined plate and a guide rail in an oscillating inclined plate type variable capacity compressor. In the guide device, the slider is fitted so that it can reciprocate in the front and rear directions relative to the guide rail and can rotate around the rail, and the slider is fitted on both left and right sides of the slider so that the slider can move back and forth in the front and rear directions. The shoe is fitted in a concave and convex relationship so as to be movable in the front and rear directions in synchronization with the slider, and the opposite side of the shoe to the slider is formed into a convex slide surface having an arcuate cross section; Slide grooves each having an arcuate cross section are formed parallel to each other and in the same direction as the radial direction of the inclined plate on the inner surfaces of both left and right sides of the fitting recess formed on a part of the outer periphery of the swinging inclined plate. The convex slide surface is slidably engaged with the slide groove.

Moreover, the second invention includes, in addition to the configuration of the first invention,
Further, an oil passage and/or oil groove is provided on the sliding contact surface between the guide rail and the slider and the sliding contact surface between the slider and the shoe.

(Function) Therefore, in the first invention, the slider is moved in the front and back direction with respect to the guide rail, and
The shoe is rotated around the guide rail, the shoe is rotated in the front and back direction with respect to the slider, and the shoe is further moved along the slide groove of the swinging inclined plate and rotated relative to the slider. Displacement or twisting in any direction during the swinging of the swinging inclined plate is easily allowed by the slider, shoe, etc.

Moreover, the second invention, in addition to the effects of the first invention,
Oil contained in the refrigerant in the crank chamber is guided from the oil passage or oil groove to the respective sliding surfaces of the guide rail and the slider, and the slider and the shoe, thereby lubricating the sliding surfaces.

(Embodiment) Hereinafter, the configuration of an embodiment embodying the first invention will be described with reference to FIGS. 1 to 6.

As shown in FIG. 2, a rear housing 3 is fixedly connected to the right end surface of the cylinder block 1 via a valve plate 2. An annular suction chamber 4 is defined at the outer periphery of the rear housing 3, and a discharge chamber 6 is defined at the center of the rear housing 3. connected to the circuit. A front housing 8 is fixedly connected to the left end surface of the cylinder block 1.
A crank chamber 9 is formed inside thereof. A drive shaft 10 is rotatably supported by the cylinder block 1 and the front housing 8 via a pair of bearings 11 and a shaft seal mechanism 12.

The cylinder block 1 has six (only one shown) cylinder chambers 13 formed in parallel with the drive shaft 10, passing through both ends thereof. A piston 14 is mounted in each cylinder chamber 13 so as to be able to reciprocate and slide, and a piston rod 15 is articulated to the left end surface of the piston 14. A suction valve mechanism 16 for introducing refrigerant gas from the suction chamber 4 into the compression chamber of each cylinder chamber 13 is formed in each of the valve plates 2 . Similarly, the valve plate 2 is provided with a discharge valve mechanism 17 for guiding the refrigerant gas compressed in the compression chamber of each cylinder chamber 13 to the discharge chamber 6.

A rotary body 18 is fitted and fixed on the drive shaft 10, and a rotary drive plate 20 is attached to the rotary body 18 in the front-rear direction (right side and left side in FIG. ) is mounted so that it can be tilted and rotated integrally with the rotating body 18.

As shown in FIGS. 2 and 3, a sleeve 21 is fitted onto the drive shaft 10 so as to be able to slide back and forth in the axial direction, and a pair of pins 22 are attached to the sleeve 21.
is fixed, and the pin 22 is engaged with an engagement hole 20b formed in the boss portion 20a of the rotary drive plate 20.

A swinging inclined plate 25 is supported on the rotary drive plate 20 via a journal bearing 23 and a thrust bearing 24 so as to be tiltable in the front and back direction together with the drive plate 20, and non-rotatably supported by a guide device 28 which will be described in detail later. There is. The left end portions of the respective piston rods 15 are connected to the swinging inclined plate 25, and the rotating body 18 is rotated by the rotation of the drive shaft 10.
When the swinging inclined plate 25 swings back and forth, the piston 14 is reciprocated via the piston rod 15. And crank chamber 9
The piston stroke changes in accordance with the differential pressure between the crank chamber pressure and the suction pressure in the suction chamber 4, and the tilt angle of the swinging inclined plate 25 changes, thereby controlling the compression capacity.

In this embodiment, a rotary support body 26 that supports the swinging inclined plate 25 is constituted by the rotary body 18, the connecting pin 19, the rotary drive plate 20, the sleeve 21, the pin 22, etc. described above.

A bleed passage 27 is provided through the cylinder block 1 and the valve plate 2 to constantly communicate the crank chamber 9 and the suction chamber 4. The refrigerant gas blow-by into the crank chamber 9 is returned to the suction chamber 4, thereby suppressing an increase in crank chamber pressure.

Next, the swinging inclined plate 25 according to the present invention is configured to allow swinging of the swinging inclined plate 25 in the front-rear direction and to prevent accompanying rotation by the rotation support 26.
The guide device 28 will be explained.

A fitting recess 25a is provided in the front housing 8 and the cylinder block 1, parallel to the drive shaft 10, and recessed at the lower end of the swinging inclined plate 25.
A guide rail 29 passes through the guide rail 29, and a threaded end portion 29a thereof is screwed and fixed to the rear housing 3. A cylindrical slider 30 is mounted on the cylindrical portion 29b of the guide rail 29 so as to be slidable in the front and rear directions through an insertion hole 30a extending in the diametrical direction so as to be orthogonal to the axial direction of the rail 29. It is fitted so as to be rotatable around the columnar part 29b. Sliding surfaces 3 at both left and right ends of the slider 30
Engagement pins 31 are integrally protruded from each of the engagement pins 31 and 0b, and a shoe 32 is inserted through an engagement hole 32a extending through the center of each of the engagement pins 31.
1, and are fitted so as to be rotatable in the front and rear directions. The slider 30 has a sliding contact surface 30 on the same shoe 32.
A sliding surface 32b in contact with the slider 3 is formed.
A convex sliding surface 32c having an arcuate cross section is formed on the opposite side surface.

On the other hand, slide grooves 25b having an arcuate cross section are formed on both left and right side surfaces of the fitting recess 25a of the swinging inclined plate 25 so as to extend in the radial direction of the inclined plate 25. The convex slide surface 32c is slidably fitted into the slide groove 25b so as to be relatively movable in the radial direction and relatively rotatable along the arcuate sliding surface 32c.

The guide rail 29 and shoe 32 are made of iron-based material, and the slider 30 is made of high-Si-based Al material (for example, A390).

In this embodiment, the guide device 28 is located at the lowest part of the crank chamber 9, so that the oil stored in the crank chamber is supplied to the slider 30, shoe 32, etc.

Next, the operation of the variable capacity compressor configured as described above will be explained.

Now, when the drive shaft 10 is rotated by the power of an engine or the like, the swinging inclined plate 25 is reciprocated by the guide device 28 via the rotation support 26 in a rotationally restricted state. As a result, each piston 14 is reciprocated via the piston rod 15, and the refrigerant gas sucked into the compression chamber of the cylinder chamber 13 from the suction chamber 4 via the suction valve mechanism 16 is compressed in the compression chamber and then discharged. It is fed under pressure into the discharge chamber 6 via the valve mechanism 17.

On the other hand, the refrigerant gas blow-by from the compression chamber into the crank chamber 9 is returned from the crank chamber 9 into the suction chamber 4 via the bleed passage 27 which is always open.
At the beginning of the compressor startup, if the temperature inside the vehicle to be cooled is high and the cooling load is large, the crank chamber pressure is slightly higher than the suction pressure and the differential pressure is smaller than a predetermined value. is maintained, the piston 14 is reciprocated at the maximum stroke, and operation with the full compression capacity is performed with the swinging inclined plate 25 having a large inclination angle.

When the compressor is operated in this manner, and the temperature inside the vehicle compartment decreases and the cooling load decreases, the suction pressure decreases, and as a result, the differential pressure increases, causing the piston 14 to reciprocate with a small stroke. The operation with a small compression capacity is performed in a state where the tilt angle of the swinging inclined plate 25 is small.

When the swinging inclined plate 25 is swung back and forth around the connecting pin 19, the slide groove 25b formed in the inclined plate 25 is displaced back and forth and up and down while changing the angle of inclination. This slide groove 25b
The displacement of the inclination angle of the slider 30 is
2 is rotatable, displacement in the front-rear direction is permissible because the slider 30 is slidable in the front-rear direction with respect to the guide rail 29, and further displacement in the vertical direction is allowed because the slider 32 is slidable in the slide groove 25b. This is allowed because it can be slid in the vertical direction.

Further, the swinging inclined plate 25 receives an external force (see arrow) in the direction of pressing the shoe 32 in FIG. In addition, since the slide groove 25b of the inclined plate 25 can move relative to the convex slide surface 32c of the shoe 32, the slide groove 25b does not come into partial contact with the convex slide surface 32c, and the sliding Localized wear of the parts is prevented.

Further, the swinging inclined plate 25 receives a torsional force in the direction of the arrow in FIG.
is allowed because it is relatively rotated.

Next, an embodiment of the second invention will be described based on FIGS. 7 and 8.

This embodiment is the seventh embodiment of the first invention.
As shown in the figure, the oil passage 30 is connected to the slider 30.
c is provided so as to communicate with the insertion hole 30a, and on the other hand, an oil groove 32d is formed in a cross shape on the sliding surfaces 32b of both shoes 32. The rest of the structure is the same as that of the previous embodiment.

Therefore, in this embodiment, the oil stored in the lower part of the crank chamber 9 is supplied from the oil passage 30c to the gap between the sliding part of the guide rail 29 and the slider 30, and the sliding part is smoothly lubricated. be exposed. and,
When the swinging inclined plate 25 is swung back and forth, as shown in FIG. 8, the gap between the slider 30 and the top surface of the fitting recess 25a of the swinging inclined plate 25 changes. of oil is easily supplied to the oil passage 30c, and the lubrication efficiency is improved.

Further, oil is also introduced from the oil groove 32d into the gap between the sliding portion of the slider 30 and the shoe 32, and the sliding portion is smoothly lubricated.

Note that the present invention can also be embodied as follows.

(1) As shown in FIG. 9, a spiral oil groove 30d is provided in the insertion hole 30a of the slider 30, and the
An annular oil groove 32d is also formed on the sliding surface 32b of No. 2.

(2) As shown in FIG. 10, instead of the engaging pin 31, both end surfaces of the slider 30 are formed into horizontal truncated conical engaging portions 33, while the sliding surface 32b of the shoe 32 has the Forming an engagement recess 32e having the same shape into which the engagement portion 33 is rotatably and slidably fitted.

Effects of the Invention As detailed above, in the first invention, the tilting plate can be freely adjusted not only when the tilting plate swings back and forth, but also when the tilting plate swings at the same time as the angle of the tilting plate is changed. Even if the guide rail, slider, shoe, and swinging inclined plate are displaced or twisted in any direction, the sliding parts of the guide rail, slider, shoe, and swinging inclined plate will not come into uneven contact, and local wear of the sliding parts will be prevented. This has the effect of improving the durability and seizure resistance of the material.

Moreover, the second invention has, in addition to the effects of the first invention,
This has the effect of reliably lubricating each sliding part, suppressing noise, and further improving durability and seizure resistance.

[Brief explanation of drawings]

FIG. 1 is an exploded perspective view of only the guide device of the first invention, FIG. 2 is a vertical sectional view of the central part showing the whole variable displacement compressor, and FIG. 3 is an enlarged sectional view taken along the line A--A in FIG. 2.
FIG. 4 is an enlarged sectional view of the vicinity of the guide device, FIG. 5 is a sectional view taken along the line B--B in FIG. 4, FIG. 6 is a sectional view showing the operating state, and FIG. FIG. 8 is an exploded perspective view, FIG. 8 is a sectional view showing the assembled state of the guide device, FIG. 9 is an exploded perspective view of only the main parts showing another example of the second invention, and FIG. 10 is another example of the first invention. FIG. 11 is an exploded perspective view of only the main parts shown, FIG. 11 is an exploded perspective view of a conventional guide device, and FIG. 12 is a front view of the same assembled state. Suction chamber...4, Discharge chamber...6, Crank chamber...
9, Drive shaft...10, Piston...14, Rotating body...18, Connecting pin...19, Rotating drive plate...2
0, Swinging inclined plate...25, Fitting recess...25a,
Slide groove...25b, Rotating support body...26, Guide device...28, Guide rail...29, Threaded part...29a, Cylindrical part...29b, Slider...
30, Insertion hole...30a, Sliding surface...30b, Oil passage...30b, Oil groove...30c, 32d, Engagement pin...31, Shoe...32, Engagement hole...32
a, Sliding surface...32b, Convex sliding surface...32
c. Engagement recess...32e.

Claims (1)

[Claims] 1. A rotary support body comprising a suction chamber, a discharge chamber, and a crank chamber, a rotary support body mounted on a drive shaft so as to be rotatable in synchronization, and a rotary support body forming a part of the rotary support body capable of swinging in the front-rear direction. The oscillating inclined plate is supported by a bearing on the rotary drive plate and reciprocates the piston, and engages with a guide rail installed parallel to the drive shaft on the outer periphery of the oscillating inclined plate, allowing the oscillating inclined plate to swing back and forth. A guide device is fitted to restrict rotation around the drive shaft, and the inclination angle of the swinging inclined plate changes according to the differential pressure between the crank chamber pressure and the suction pressure, thereby controlling the compression capacity. In such a variable capacity compressor, a slider is fitted to the guide rail so that it can reciprocate in the front and rear directions and can rotate around the rail, and a slider is fitted on both left and right sides of the slider. The direction can be rotated,
The slider is fitted in a concave and convex manner so as to be movable in the front and back direction in synchronization with the slider, and the opposite side of the shoe to the slider is formed into a convex sliding surface with an arcuate cross section, and the swinging slope is On the left and right inner surfaces of the fitting recess formed on a part of the outer periphery of the plate, slide grooves with arcuate cross sections are formed parallel to each other and in the same direction as the radial direction of the inclined plate. On the other hand, there is a guide device for a swinging inclined plate in a variable displacement compressor in which the convex sliding surface is slidably engaged. 2 Comprising a suction chamber, a discharge chamber, and a crank chamber, a rotary support body is mounted on the drive shaft so as to be able to rotate synchronously, and a rotary drive plate that is swingable in the front and rear directions and constitutes a part of the rotary support body is used to drive the bearing. The rocking inclined plate that is supported to reciprocate the piston is engaged with a guide rail installed parallel to the drive shaft on the outer periphery, allowing the swinging inclined plate to swing back and forth, but it is not possible to rotate the piston around the drive shaft. A variable displacement compression system is fitted with a guide device that restricts rotation, and the tilt angle of the swinging inclined plate changes according to the differential pressure between the crank chamber pressure and the suction pressure to control the compression capacity. In the machine, a slider is fitted to the guide rail so that it can reciprocate in the front-rear direction and can rotate around the rail, and a shoe is mounted on both left and right sides of the slider so that it can rotate in the front-rear direction. ,
The slider is fitted in a concave and convex manner so as to be movable in the front and back direction in synchronization with the slider, and the opposite side of the shoe to the slider is formed into a convex sliding surface with an arcuate cross section, and the swinging slope is On the left and right inner surfaces of the fitting recess formed on a part of the outer periphery of the plate, slide grooves with arcuate cross sections are formed parallel to each other and in the same direction as the radial direction of the inclined plate. On the other hand, the convex sliding surface is slidably engaged;
The guide device for a swinging inclined plate in a variable capacity compressor further includes an oil passage and/or an oil groove provided on a sliding contact surface between the guide rail and the slider and a sliding contact surface between the slider and the shoe.