Variable Displacement Wobble Plate Compressor Slide and Guide Joint

These and other objects, advantages and features of the present invention will become more apparent from the following description and drawing in which:

FIG. 1 is a longitudinal sectional view of a variable displacement wobble plate compressor having incorporated therein one embodiment of the multiple axis joint of the present invention. This figure further includes a schematic of a motor vehicle air conditioning system in which the compressor is connected.

FIG. 2 is an enlarged view taken along the line 2--2 in FIG. 1.

FIG. 3 is a view taken along the line 3--3 in FIG. 2.

FIG. 4 is a view taken along the line 4--4 in FIG. 2.

FIG. 5 is an enlarged three-dimensional view of the one-piece bearing body in the previous figures.

FIG. 6 is a view of the lower portion of the compressor in FIG. 1 but with another embodiment of the multiple axis joint of the present invention.

FIG. 7 is an enlarged view taken along the line 7--7 in FIG. 6.

FIG. 8 is a view taken along the line 8--8 in FIG. 7.

FIG. 9 is a view taken along the line 9--9 in FIG. 7.

FIG. 10 is an enlarged three-dimensional view of the one-piece bearing body in FIGS. 6-9.

Referring to the drawings wherein the same numbers are employed to identify the same parts throughout the several views, there is shown in FIG. 1 a variable displacement wobble plate compressor 10 adapted for use as a refrigerant compressor and connected in a motor vehicle air conditioning system having the normal condenser 12, orifice tube 14, evaporator 16 and accumulator 18 arranged in that order between the compressor's discharge and suction sides. The compressor is driven by the motor vehicle's engine (not shown) through a V-belt 20 and electromagnetic clutch 22 and comprises a cylinder block 24 that is closed at one end by a crankcase 26 and at the other end by a cylinder head 28. A drive shaft 30 connected to the output of the clutch is rotatably mounted in the cy linder block and crankcase and drives a drive plate 32 that in turn wobbles a wobble plate 34 in the compressor's wobble plate mechanism 36 enclosed by the crankcase. The wobble plate 34 operates through ball-ended connector rods 37 to drive five pistons 38 mounted in the cylinder block (only one rod and piston being shown). A round guide rod or pin 40 mounted in the compressor parallel to the drive shaft operates through a multiple axis joint 42 to prevent rotation while permitting angulation of the wobble plate from the full stroke position shown in outline in FIG. 1 to a minimum stroke position shown in phantom line in the same view. A control valve 44 mounted in the cylinder head 28 responds to both suction and discharge pressure to control the pressure differential between the crankcase and the suction pressure and thereby control the angle of the wobble plate and thus the displacement of the compressor. The compressor thus far described, apart from the details of the multiple axis joint now to be described, is like that disclosed in U.S. Pat. No. 4,428,718 assigned to the assignee of this invention and which is hereby incorporated by reference.

Describing now the multiple axis joint 42 as best seen in FIGS. 2-5, there are formed a pair of opposed, concave, cylindrical, radially extending guides 54 and 56 in a radial slot 58 in the throttle plate through which the guide rod passes. A bearing body 60 having a slot 62 that slidably receives the guide rod has convex cylindrical surfaces 63 and 64 on opposite sides thereof slidably received in the respective radially extending guides 54 and 56 in the wobble plate. As best seen in FIGS. 4 and 5, the slot 62 through the bearing body tapers inwardly at both ends from an oval shape to a round shape where they intersect as a circular line of engagement 65 with and about the guide rod. This tapering of the slot allows angular as well as linear motion of the bearing body on the guide rod as the wobble plate is angled between its two extreme positions without any loss of contact about the guide rod with the bearing body and wherein the bearing body is caused to slide in the wobble plate guides. In such relative movement, there is thus substantial surface contact directly between the wobble plate and the bearing body but less direct contact between the bearing body and the guide rod. However, this latter contact may be expanded as seen in the embodiment in FIGS. 6-10, to present more wear surface should the wear prove significant and depending on the particular combination of materials selected for the guide rod, bearing body and wobble plate.

In the embodiment in FIGS. 6-10, parts and details similar to those in FIGS. 1-5 are identified by the same reference numerals only primed and altered structure where otherwise not readily so referenced is identified by new numerals. As seen in FIGS. 6-9, the guide rod 40' of the multiple axis joint 42' is formed with parallel flat sides 70 along the length thereof leaving diagonally opposite and parallel rounded or fixed radius arcuate sides 72. And the slot 62' in the bearing body 60' has flat sides 74 that extend parallel to each other and the flat sides of the guide rod so as to have flat surface-to-surface contact therewith radial to the centerline of the wobble plate 34'. The rounded or fixed radius arcuate sides of the slot, however, remain tapered inwardly from both ends as before so as to converge at the center of the bearing body but now at two diagonally oppositely located circular line segments 76 as seen in FIGS. 7, 9 and 10 that contact with the rounded sides 72 of the guide rod to allow angular as well as linear motion of the bearing body on the guide rod while the bearing body slides in the wobble plate guides like in the FIGS. 1-5 embodiment. And thus the bearing load area for resisting rotation of the wobble plate is now the width of the guide rod flats 70 times the length of the slot flats 74 which is also the full width of the bearing body as viewed alongside the guide rod.

The bearing body may be manufactured in a very cost-effective manner such as by being machined from rod stock on a screw machine or molded of plastic or powdered metal. Preferably, the bearing body is formed of a bearing grade plastic material such as polyimide which has inherent lubricity and in addition a significant damping factor not normally available with metal. The guide rod may also be manufactured in a very cost-effective manner even in the flat-sided form by machining either round or rectangular bar stock or using barstock extruded to the desired cross-sectional shape and with a material selection of either metal or plastic compatible with the bearing body. Furthermore, it will be appreciated that the assembly cost is reduced as compared with the prior three-part design as a result of the elimination of two parts and their respective orientation.

The above described preferred embodiments are illustrative of the invention which may be modified within the scope of the appended claims.