SLANT PLATE TYPE COMPRESSOR WITH VARIABLE DISPLACEMENT MECHANISM

Abstract: A slant plate type compressor with a capacity or displacement adjusting mechanism is disclosed. The compressor includes a housing (10) having a cylinder block (21) provided with a plurality of cylinders (70) and a crank chamber (22). A piston (71) is slidably fitted within each of the cylin­ ders (70) and is reciprocated by a drive mechanism which includes a mem­ ber (50) having a surface with an adjustable incline angle. The incline angle is controlled by the pressure situation in the crank chamber (22). The pressure in crank chamber (22) is controlled by control mechanism which comprises a passageway communicating between the crank chamber (22) and a suction chamber (242) and valve device (19) to control the clos­ ing and opening of the passageway. The valve device (19) includes a valve element (193a) which directly controls the closing and opening of passage­ way. A valve device (19) includes a bellows (193) valve element and a valve shifting element (195). The valve shifting element (195) is coupled to the bellows (193) to apply a force to the bellows (193) and thereby shift a control point of the bellows in response changes in the discharge chamber pressure (251).

Description: The present invention relates to a refrigerant compressor, and more particularly, to a slant plate type compressor, such as a wobble plate type compressor, with a variable displacement mechanism suitable for use in an automotive air conditioning system. It has been recognized that it is desirable to provide a slant plate type piston compressor with a displacement or capacity adjusting mechanism to control the compression ratio in response to demand. As disclosed in US-A-4428718, the compression ratio may be controlled by changing the slant angle of the sloping surface of a slant plate in response to the operation of a valve control mechanism. The slant angle of the slant plate is adjusted to maintain a constant suction pressure in response to a change in the heat load of the evaporator of an external circuit including the compressor or a change in rotation speed of the compressor. In an air conditioning system, a pipe member connects the outlet of an evaporator to the suction chamber of the compressor. Accordingly, a pressure loss occurs between the suction chamber and the outlet of the evaporator wich is directly proportional to the "suction flow rate" therebetween as shown in Figure 5. As a result, when the capacity of the compressor is adjusted to maintain a constant suction chamber pressure in response to appropriate changes in the heat load of the evaporator or the rotation speed of the compressor, the pressure at the evaporator outlet increases. This increase in the evaporator outlet pressure results in an undesirable decrease in the heat exchange ability of the evaporator. Above mentioned US-A-4428718 discloses a valve control mechanism, to eliminate this problem. The valve control mechanism, which is responsive to both suction and discharge pressures, provides controlled communication of both suction and discharge fluid with the compressor crank chamber and thereby controls compressor displacement. The compressor control point for displacement change is shifted to maintain a nearly constant pressure at the evaporator outlet portion by means of this compressor displacement control. The valve control mechanism makes use of the fact that the discharge pressure of the compressor is roughly directly proportional to the suction flow rate. However, in the above-mentioned valve control mechanism, a single movable valve member, formed of a number of parts, is used to control the flow of fluid both between the discharge chamber and the crankcase chamber, and between the crankcase chamber and the suction chamber. Thus, extreme precision is required in the formation of each part and in the assembly of the large number of parts into the control mechanism in order to assure that the valve control mechanism operates properly. Furthermore, when the heat load of the evaporator or the rotation speed of the compressor is changed quickly, discharge chamber pressure increases and an excessive amount of discharge gas flows into the crank chamber from the discharge chamber through a communication passage of the valve control mechanism due to a lag time to such the action between the operation of the valve control mechanism and the response of the external circuit including the compressor. As a result of the excessive amount of discharge gas flow, a decrease in compression efficiency of the compressor, and a decline of durability of the compressor internal parts, occurs. The variable displacement control mechanism in a slant plate type of compressor, in accordance with the present invention, was developed to take advantage of the relationship between discharge pressure and suction flow rate in a manner which overcomes the disadvantages of a prior art mechanism such as disclosed in the ′718 patent. That is, the control mechanism of the present invention was designed to have a simple physical structure and to operate in a direct manner on a valve controlling element in response to discharge pressure changes, thereby resolving the complexity, excessive discharge flow and slow response time problems. The ′718 patent discloses a capacity adjusting mechanism used in a wobble plate type compressor. As is typical in this type of compressor, the wobble plate is disclosed at a slant or incline angle relative to the drive axis, mutates but does not rotate, and drivingly couples the pistons to the drive source. This type of capacity adjusting mechanism, using selective fluid communication between the crank chamber and the suction chamber, however, can be used in any type of compressor which uses a slanted plate or surface in the drive mechanism. For example, US-A-4,664,604, issued to Terauchi, discloses this type of capacity adjusting mechanism in a swash plate type compressor. The swash plate, like the wobble plate, is disclosed at a slant angle and drivingly couples the pistons to the drive source. However, while the wobble plate only nutates, the swash plate both nutates and rotates. The term slant plate type compressor will therefore be used therein to refer to any type of compressor, including wobble and swash plate types, which use a slanted plate or surface in the drive mechanism. US-A-4428718 discloses a slant plate type refrigerant compressor including a compressor housing having a central portion, a front end plate at one end and a rear end plate and its other end, the housing having a cylinder block provided with a plurality of cylinders and a crank chamber adjacent to the cylinder block, a respective piston slidably fitted within each of the cylinders, a drive mechanism coupled to the pistons to reciprocate the pistons within the cylinders, the drive mechanism including a drive shaft rotatably supported in the housing, a rotor coupled to the drive shaft and rotatable therewith, and coupling means for drivingly coupling the rotor to the pistons such that rotatary motion of the rotor is converted into reciprocating motion of the pistons, the coupling means including a member having a surface disposed at an inclined angle relative to the drive shaft, the inclined angle of the member being adjustable to vary the stroke length of the pistons and the capacity of the compressor, the rear end plate having a suction chamber and a discharge chamber, a passageway connected between the crank chamber and the suction chamber, and valve means for controlling the closing and opening of the passageway to vary the capacity of the compressor by adjusting the inclined angle, the valve control means including a valve member opening and closing the passageway in response to changes in the crank chamber or suction chamber pressure, and a valve shifting element comprising a cylinder member and an actuating rod coupled to the valve member to apply a force to the valve member and shift a control point of the valve member in response to changes in the discharge pressure; the actuating rod having a first end adjacent to the valve member and a second end disposed in the discharge chamber such that the actuating rod tends to move the valve member longitudinally in response to the discharge pressure; and the actuating rod being slidably disposed within a cylinder member having a first end adjacent to the valve member and a second end remote from the valve member and adjacent to the discharge chamber; and, according to the invention, such a compressor is characterised in that the discharge chamber and the crank chamber are permanently isolated from each other by an O-ring disposed between an inner surface of the cylinder member and an outer surface of the actuating rod; and in that the second end of the actuating rod is disposed in the discharge chamber and receives an axial force from the pressure in the discharge chamber. In the accompanying drawings: Figure 1 is a vertical longitudinal sectional view of a wobble plate type refrigerant compressor in accordance with a first embodiment of this invention; Figure 2 is an enlarged partially sectional view of a valve control mechanism shown in Figure 1; Figure 3 is a vertical longitudinal sectional view of a wobble plate type refrigerant compressor in accordance with a second embodiment of this invention; Figure 4 is a vertical longitudinal sectional view of a wobble plate type refrigerant compressor in accordance with a third embodiment of this invention; and, Figure 5 is a graph showing the relationship between the pressure loss occurring between the evaporator outlet portion and the compressor suction chamber and the suction flow rate. With reference to Figure 1, the construction of a slant plate type compressor, specifically a wobble plate type refrigerant compressor 10 in accordance with one embodiment of the present invention is shown. Compressor 10 includes cylindrical housing assembly 20 including cylinder block 21, front end plate 23 at one end of cylinder block 21, crank chamber 22 formed between cylinder block 21 and front end plate 23, and rear end plate 24 attached to the other end of cylinder block 21. Front end plate 23 is mounted on cylinder block 21 forward (to the left in Figure 1) of crank chamber 22 by a plurality of bolts 101. Rear end plate 24 is mounted on cylinder block 21 at is opposite end by a plurality of bolts 102. Valve plate 25 is located between rear end plate 24 and cylinder block 21. Opening 231 is centrally formed in front end plate 23 for supporting drive shaft 26 by bearing 30 disposed in the opening. The inner end portion of drive shaft 26 is rotatably supported by bearing 31 disposed within central bore 210 of cylinder block 21. Bore 210 extends to a rearward end surface of cylinder block 21 to dispose valve control mechanism 19 as discussed below. Cam rotor 40 is fixed on drive shaft 26 by pin member 261 and rotates with shaft 26. Thrust needle bearing 32 is disposed between the inner end surface of front end plate 23 and the adjacent axial end surface of cam rotor 40. Cam rotor 40 includes arm 41 having pin member 42 extending therefrom. Slant plate 50 is adjacent cam rotor 40 and includes opening 53 through which passes drive shaft 26. Slant plate 50 includes arm 51 having slot 52. Cam rotor 40 and slant plate 50 are connected by pin member 42, which is inserted in slot 52 to create a hinged joint. Pin member 42 is slidable within slot 52 to allow adjustment of the angular position of slant plate 50 with respect to the longitudinal axis of drive shaft 26. Wobble plate 60 is rotatably mounted on slant plate 50 through bearings 61 and 62. Fork shaped slider 63 is attached to the outer peripheral end of wobble plate 60 and is slidably mounted on sliding rail 64 held between front end plate 23 and cylinder block 21. Fork shaped slider 63 prevents rotation of wobble plate 60 and wobble plate 60 nutates along rail 64 when cam rotor 40 rotates. Cylinder block 21 includes a plurality of peripherally located cylinder chambers 70 in wich pistons 71 reciprocate. Each piston 71 is connected to wobble plate 60 by a corresponding connecting rod 72. Rear end plate 24 includes peripherally located annular suction chamber 241 and centrally located discharge chamber 251. Valve plate 25 is located between cylinder block 21 and rear end plate 24 and includes a plurality of valved suction ports 242 linking suction chamber 241 with respective cylinders 70. Valve plate 25 also includes a plurality of valved discharge ports 252 linking discharge chambers 251 with respective cylinders 70. Suction ports 242 and discharge ports 252 are provided with suitable reed valves as described in US-A-4,011,029. Suction chamber 241 includes inlet portion 241a which is connected to an evaporator of the external cooling circuit (not shown). Discharge chamber 251 is provided with outlet portion 251a connected to a condenser of the cooling circuit (not shown). Gaskets 27 and 28 are located between cylinder block 21 and the inner surface of valve plate 25, and the outer surface of valve plate 25 and rear end plate 24 respectively, to seal the mating surfaces of cylinder block 21, valve plate 25 and rear end plate 24. With reference to Figure 2, additionally, valve control mechanism 19 includes cup-shaped casing member 191 defining valve chamber 192 therewithin. O-ring 19a is disposed between an outer surface of casing member 191 and an inner surface of bore 210 to seal the mating surfaces of casing member 191 and cylinder block 21. A plurality of holes 19b are formed at a closed end (to the left in Figures 1 and 2) of casing member 191 to lead crank chamber pressure into valve chamber 192 through a gap 31a existing between bearing 31 and cylinder block 21. Bellows 193 is disposed in valve chamber 192 to longitudinally contract and expand in response to crank chamber pressure. Projection member 193b attached at forward (to the left in Figures 1 and 2) end of bellows 193 is secured to vial projection 19c formed at a center of closed end of casing member 191. Valve member 193a is attached at rearward (to the right in Figures 1 and 2) end of bellows 193. Cylinder member 194 including valve seat 194a penetrates a center of valve plate assembly 200 which includes valve plate 25, gaskets 27, 28, suction valve member 271 and discharge valve member 281. Valve seat 194a is formed at forward end of cylinder member 194 and is secured to an opened end of casing member 191. Nuts 100 are screwed on cylinder member 194 from a rearward end of cylinder member 194 located in discharge chamber 251 to fix cylinder member 194 to valve plate assembly 200 with valve retainer 253. Conical shaped opening 194b receiving valve member 193a is formed at valve seat 194a and is linked to cylinder 194c axially formed in cylinder member 194. Actuating rod 195 is slidably disposed within cylinder 194c, slightly projects from the rearward end of cylinder 194c, and is linked to valve member 193a through bias spring 196. O-ring 197 is disposed between an inner surface of cylinder 194c and an outer surface of actuating rod 195 to seal the mating surfaces of cylinder 194c and actuating rod 195. Radial hole 151 is formed at valve seat 194a to link conical shaped opening 194b to one end opening of conduit 152 formed at cylinder block 21. Conduit 152 includes cavity 152a and also links to suction chamber 242 through hole 153 formed at valve plate assembly 200. Passageway 150, which provides communication between crank chamber 22 and suction chamber 241, is obtained by uniting gap 31a, bore 210, holes 19b, valve chamber 192, conical shaped opening 194b, radial hole 151, conduit 152 and hole 153. In result, the opening and closing of passageway 150 is controlled by the contracting and expanding of bellows 193 in response to crank chamber pressure. During operation of compressor 10, drive shaft 26 is rotated by the engine of the vehicle through an electromagnetic clutch 300. Cam rotor 40 is rotated with drive shaft 26, rotating slant plate 50 as well, which causes wobble plate 60 to nutate. Nutational motion of wobble plate 60 reciprocates pistons 71 in their respective cylinders 70. As pistons 71 are reciprocated, refrigerant gas which is introduced into suction chamber 241 through inlet portion 241a, flows into each cylinder 70 through suction ports 242 and then compressed. The compressed refrigerant gas is discharged to discharge chamber 251 from each cylinder 70 through discharge ports 252, and therefrom into the cooling circuit through outlet portion 251a. The capacity of compressor 10 is adjusted to maintain a constant pressure in suction chamber 241 in response to a change in the heat load of the evaporator or a change in the rotating speed of the compressor. The capacity of the compressor is adjusted by changing the angle of the slant plate witch is dependent upon the crank chamber pressure. An increase in crank chamber pressure decreases the slant angle of the slant plate and thus the wobble plate, decreasing the capacity of the compressor. A decrease in the crank chamber pressure increases the angle of the slant plate and the wobble plate and thus increases the capacity of the compressor. The effect of the valve control mechanism of the present invention is to maintain a constant pressure at the outlet of the evaporator during capacity control of the compressor in the following manner. Actuating rod 195 pushes valve member 192 in the direction to contract belows 193 through bias spring 196, witch smoothly transmits the force from actuating rod 195 to valve member 193a of bellows 193. Actuating rod 195 is moved in response to receiving discharge pressure in discharge chamber 251. Accordingly, increasing discharge pressure in discharge chamber 251 further moves rod 195 toward bellows 193, thereby increasing tendency to contract bellows 193. As a result, the compressor control point for displacement change is shifted to maintain a constant pressure at the evaporator outlet portion. That is, the valve control mechanism makes use of the fact that the discharge pressure of the compressor is roughly directly proportional to the suction flow rate. Since actuating rod 195 moves in direct response to changes in discharge pressure and applies a force directly to bellows 193 (the controlling valve element), the control point at which bellows 193 operates is shifted in a very direct and responsive manner by changes in discharge pressure. Figure 3 shows a second embodiment of the present invention in which the same numerals are used to denote the same elements shown in Figures 1 and 2. In the second embodiment, cavity 220 disposing valve control mechanism 19 is formed at a central portion of cylinder block 21 and is isolated from bore 210 which rotatably supports drive shaft 26. Holes 19b link valve chamber 192 to space 221 provided at the forward end of cavity 220. Conduit 162, linking space 221 to suction chamber 242 through hole 153, is formed in cylinder block 21 to lead suction chamber pressure into space 221. Conduit 163, linking crank chamber 22 to radial hole 151, is also formed in cylinder block 21. Passageway 160 communicating crank chamber 22 and suction chamber 241 is thus obtained by uniting conduit 163, radial hole 151, conical shaped opening 194b, valve chamber 192, holes 19b, space 221, conduit 162 and hole 153. In result, the opening and closing of passageway 160 is controlled by the contracting and expanding of bellows 193 in response to suction chamber pressure. Figure 4 shows a third embodiment of the present invention in which the same numerals are used to denote the same elements shown in Figures 1 and 2. In the third embodiment the cavity, in which the valve control mechanism is disposed, is formed in the cylinder block at a location radially offset from the axis of the drive shaft. That is, cavity 230, receiving the valve control mechanism, is formed in cylinder block 21 at a location radially offset from an axis of drive shaft 26. Conduit 171 is formed in cylinder block 21 to lead crank chamber pressure into valve chamber 192 via holes 19b. The operation of the valve control mechanisms of the second and third embodiments are substantially similar to that in the first embodiment and a further explanation of these operations are omitted.

Claims: 1. A slant plate type refrigerant compressor (10) including a compressor housing (20) having a central portion, a front end plate (23) at one end and a rear end plate (24) and its other end, the housing having a cylinder block (21) provided with a plurality of cylinders (70) and a crank chamber (22) adjacent to the cylinder block, a respective piston (71) slidably fitted within each of the cylinders, a drive mechanism coupled to the pistons (71) to reciprocate the pistons within the cylinders (70), the drive mechanism including a drive shaft (26) rotatably supported in the housing (20), a rotor (40) coupled to the drive shaft and rotatable therewith, and coupling means for drivingly coupling the rotor to the pistons such that rotatary motion of the rotor is converted into reciprocating motion of the pistons, the coupling means including a member having a surface disposed at an inclined angle relative to the drive shaft, the inclined angle of the member being adjustable to vary the stroke length of the pistons and the capacity of the compressor (10), the rear end plate having a suction chamber (241) and a discharge chamber (251), a passageway (150) connected between the crank chamber and the suction chamber, and valve means (19) for controlling the closing and opening of the passageway to vary the capacity of the compressor by adjusting the inclined angle, the valve control means including a valve member (193a) opening and closing the passageway in response to changes in the crank chamber or suction chamber pressure, and a valve shifting element comprising a cylinder member (194) and an actuating rod (195) coupled to the valve member (193a) to apply a force to the valve member (193a) and shift a control point of the valve member in response to changes in the discharge pressure; the actuating rod (195) having a first end adjacent to the valve member (193a) and a second end disposed in the discharge chamber (251) such that the actuating rod (195) tends to move the valve member (193a) longitudinally in response to the discharge pressure; and the actuating rod (195) being slidably disposed within the cylinder member (194) having a first end adjacent to the valve member (193a) and a second end remote from the valve member (193a) and adjacent to the discharge chamber (251); characterised in that the discharge chamber (251) and the crank chamber (22) are permanently isolated from each other by an O-ring (197) disposed between an inner surface of the cylinder member (194) and an outer surface of the actuating rod (195); and in that the second end of the actuating rod (195) is disposed in the discharge chamber (251) and receives an axial force from the pressure in the discharge chamber. 2. A compressor according to claim 1, wherein the valve control means comprises a longitudinally expanding and contracting bellows (193) with the valve member attached at one end of the bellows. 3. A compressor according to claim 1, further comprising an elastic means (196) disposed between the valve member and the first end of the actuating rod. 4. A compressor according to claim 3, wherein the elastic means is a compression spring (196). 5. A compressor according to any one of the preceding claims, wherein the valve control means (19) controls the opening and closing of the passageway (151) in response to a change in suction chamber pressure (Fig. 3). 6. A compressor according to any one of claims 1 to 4, wherein the valve control means (19) controls the opening and closing of the passageway (151) in response to a change in crank chamber pressure (Figs. 1, 2 and 4). 7. A compressor according to any one of the preceding claims, wherein the actuator rod (195) slides through the O-ring (197) which is fixed in the cylinder member (194).

Inventors: TERAUCHI, KIYOSHI
Applicants: SANDEN CORPORATION
Application year: 1988
Main classification: F04B1
IPC codes: F04B27