SCROLL TYPE COMPRESSOR WITH VARIABLE DISPLACEMENT MECHANISM

Abstract: A scroll type compressor with a variable displacement mechanism includes a housing (l0) having fluid inlet and outlet ports. A fixed scroll (2l) is fixed within the housing and has a circular end plate (2ll) from which a first spiral element (2l2) extends. The end plate of the fixed scroll partitions the inner chamber of the housing (l0) into a front chamber (27) connected to the fluid inlet port and a rear chamber (28). The rear chamber is divided into a discharge chamber (28l) connected to the fluid outlet port and an intermediate pressure chamber (282). The end plate of the fixed scroll has at least two holes (2l4, 2l5) which connect the fluid pockets to the intermediate pressure chamber (282) and also has a communicating hole (283) which connects the front chamber and the intermediate chamber. A control device (36) which controls the communication between the front chamber and the intermediate pressure chamber is disposed on a portion of the intermediate pressure chamber and includes a cylinder (36l) and communicating means (363). The communicating means (363) leaks compressed fluid in the cylinder (36l) into the suction chamber (27l) to effect a stable varying displacement operation of the compressor.

Description: The present invention relates to a scroll type compressor, and more particularly, to a scroll type compressor with a variable displacement mechanism. When the air conditioning load in the compartment of a car is decreased by an air conditioning system, or the temperature in the compartment of a car is below the predetermined temperature, the displacement of the compressor for the air conditioning system does not need to be at its maximum. Accordingly, the compression ratio can be decreased. Scroll type compressors which can vary the compression ratio are well known, see for example, US-A-450565l and our copending U.S. Patent Application Serial No. 669,389 filed on November 8, l984, which show scroll type compressors with variable displacement mechanisms. However, in US-A-450565l, the change of the compression ratio is not sufficiently large. Also, in the mechanism shown in U.S. Patent Application Serial No. 669,389, the temperature of discharge fluid increases abnormally when the compressor operates at high speed. One resolution to above problems is disclosed in our copending U.S. Patent Application Serial No. 875,56l filed on June l8, l986. Referring to Figure l, a variable displacement mechanism which is disclosed in U.S. Patent Application Serial No. 875,56l is explained. A control mechanism l for varying the displacement of the compressor includes a cylinder 2, a piston 3 which is slidably disposed in the cylinder 2 and a spring 4 which is disposed between the bottom portion of the cylinder 2 and the piston 3. When an electromagnetic valve 5 is energized, compressed gas in a discharge chamber (not shown) is introduced into the cylinder 2 through a capillary tube (not shown). Since the pressure of the compressed gas is larger than the recoil strength of the spring 4 and the pressure in an intermediate pressure chamber 6, the piston 3 is urged downward and closes the opening of the intermediate pressure chamber 6. Accordingly, the compression ratio of the compressor is increased. On the other hand, when the electromagnetic valve 5 is de-energized, compressed gas is not supplied to the cylinder 2. Thus, the pressure in the cylinder 2 becomes less than the recoil strength of the spring 4 and the pressure in the intermediate pressure chamber 6, and the piston 3 is urged upward, the intermediate pressure chamber 6 being connected with a communciating chamber 7 through the cylinder 2. Accordingly, refrigerant gas in the intermediate pressure chamber 6 flows into the communicating chamber 7 through the cylinder 2. Thus, since the volume of compressed gas which is discharged into the discharge chamber is decreased, the compression ratio of the compressor is decreased. In a scroll type compressor with the above-mentioned variable displacement mechanism, if the electromagnetic valve 5 is closed the communication between the cylinder 2 and the discharge chamber to change the maximum compression ratio towards the minimum compression ratio, high pressure gas in the cylinder 2 gradually leaks into the communicating chamber 7 and the intermediate chamber 6 through a gap between the inner surface of the cylinder 2 and the outer peripheral portions of the piston 3. Thus, the pressure in the cylinder 2 gradually decreases, and if the pressure in the cylinder 2 becomes less than the recoil strength of spring 4 and the pressure in the intermediate pressure chamber 6, the piston 3 is pushed upwards. As a result of this movement of the piston 3, the volume in the cylinder 2 is increased. Therefore, the piston 3 is urged downward again. However, the compressed gas in the cylinder 2 is continuously leaking into the communicating and intermediate chambers so that the piston 3 gradually moves up with a reciprocating or vibratory motion. If vibration of the piston occurs in each operation, durability of the piston is reduced. Noise is also generated by the vibration of the piston. Furthermore, if the piston is vibratedly reciprocated within the cylinder, the operation of the variable displacement mechanism cannnot be achieved stably. On the other hand, when the piston 3 is urged downwards and closes the opening of the intermediate pressure chamber 6, the outer edge of the piston 3 abuts against the inner bottom surface of the cylinder 2 and causes impact noise. Also, the piston 3 is abraded due to the impact intermediately, and the reliability of the control mechanism is reduced. It is a primary object of the present invention to provide a scroll type compressor with a variable displacement mechanism which can operate stably to vary the displacement. It is another object of the present invention to provide a scroll type compressor with a variable displacement mechanism which has high durability. It is still another object of the present invention to provide a scroll type compressor with a variable displacement mechanism which can function with reduced noise levels. According to a first aspect of the present invention there is provided a scroll type compressor including a housing having an inlet port and outlet port; a fixed scroll fixedly disposed within the housing and having a circular end plate from which a first spiral element extends; an orbiting scroll having a circular end plate from which a second spiral element extends, the first and second spiral elements interfitting at an angular and radial offset to make a plurality of line contacts to define at least one pair of fluid pockets within the interior of the housing; a driving mechanism operatively connected to the orbiting scroll to effect orbital motion of the orbiting scroll to change the volume of the fluid pockets; a rotation preventing mechanism for preventing rotation of the orbiting scroll during orbital motion, the circular end plate of the fixed scroll dividing the interior of the housing into a front chamber and a rear chamber, the front chamber being connected with the inlet port, and the rear chamber being divided into a discharge chamber which connects the outlet port and a central fluid pocket formed between the scrolls, and an intermediate pressure chamber; at least one pair of holes formed through the circular end plate of the fixed scroll to form a fluid channel between the fluid pockets and the intermediate pressure chamber; a communication channel formed through the circular plate of the fixed scroll to form a fluid channel between the intermediate pressure chamber and the front chamber, and a control means disposed on a portion of the intermediate pressure chamber for controlling the communication between the intermediate pressure chamber and the suction chamber, characterised in that the control means comprises a cylinder; a piston slidably disposed with the cylinder; and a communicating means, the cylinder connecting with the intermediate pressure chamber, the suction chamber (27l) and the discharge chamber (28l), the piston sliding within the cylinder in accordance with the pressure difference between the pressure in the cylinder (36l) and the pressure in the intermediate pressure chamber (282), and the communicating means (363) leaking the discharged gas in the cylinder into the suction chamber (27l) when the piston is pushed upwards from the lowermost position. A second aspect of the invention is characterized in that the control means comprises a cylinder; a piston slidably disposed with the cylinder and a shock absorbing element, the cylinder connecting with the intermediate pressure chamber, the suction chamber and the discharge chamber, the piston sliding with the cylinder in accordance with the pressure difference between the pressure in the cylinder and the pressure in the intermediate pressure chamber, and the shock absorbing element being disposed on bottom surface of the cylinder for absorbing the impact force between the inner end surface of the cylinder and the piston and for securing sealing between the piston and the inner end surface of the cylinder. Examples of mechanisms constructed in accordance with the invention will now be described with reference to the accompanying drawings, in which:- Figure l is a partly cross-sectional view of a scroll type compressor illustrating a conventional variable displacement mechanism; Figure 2 is a cross-sectional view of a scroll type compressor in accordance with one embodiment of this invention; Figure 3(a) is a cross-sectional view taken along the line A-A of Figure l; Figure 3(b) is a cross-sectional view taken along the line B-B of Figure l; Figure 4 is a perspective view of a piston ring which is used in the variable displacement mechanism shown in Figure 2; Figure 5 is a cross-sectional view of a variable displacement mechanism with a modification of the mechanism shown in Figure 2; Figure 6 is a cross-sectional view of a second variable displacement mechanism for a scroll type compressor as in Figure 2; Figure 7 is a cross-sectional view of a variable displacement mechanism which is a modification of the mechanism shown in Figure 6; Figure 8 is a cross-sectional view of a third variable displacement mechanism for a scroll type compressor as in Figure 2; Figure 9 is a cross-sectional view of a variable displacement mechanism which is a modification of the mechanism shown in Figure 8; and, Figure l0 is a cross-sectional view of a fourth variable displacement mechanism for a scroll type compressor as in Figure 2. The scroll type compressor shown in Figure 2 includes a compressor housing l0 having a front end plate ll and a cup-shaped casing l2 which is attached to an end surface of the end plate ll. A hole lll is formed in the centre of the front end plate ll for receiving a drive shaft l3. An annular projection ll2 is formed on a rear surface of front end plate ll, facing the cup-shaped casing l2 and is concentric with the hole lll. An outer peripheral surface of the projection ll2 extends into an inner wall of the opening of the cup-shaped casing l2. Thus, an opening l2l of the cup-shaped casing l2 is covered by the front end plate ll. An O-ring l4 is located between the outer peripheral surface of the annular projection ll2 and the inner wall of the opening of the cup-shaped casing l2 to seal the mating surface of the front end plate ll and the cup-shaped casing l2. An annular sleeve l6 projects from the front end surface of the front end plate ll to surround the drive shaft l3 and define a shaft seal cavity. In the embodiment shown in Figure 2, the sleeve l6 is formed separately from the front end plate ll and is fixed to its front end surface by screws (not shown). Alternatively, the sleeve l6 may be formed integrally with the front end plate ll. The drive shaft l3 is rotatably supported by the sleeve l6 through a bearing l7 located within the front end of the sleeve l6. The drive shaft l3 has a disk-shaped rotor l3l at its inner end which is rotatably supported by the front end plate ll through a bearing l5 located within the opening lll in the front end plate ll. A shaft seal assembly l8 is coupled to the drive shaft l3 within the cavity of the sleeve l6. A pulley 20l is rotatably supported by a ball bearing l9 which is carried on the outer surface of the sleeve l6, and an electromagnetic coil 202 is fixed about the outer surface of the sleeve l6 by a support plate. An armature plate 203 is elastically supported in the outer end of the drive shaft l3. The pulley 20l, magnetic coil 202 and armature plate 203 form a magnetic clutch 20. In operation, the drive shaft l3 is driven by an external power source, for example, the engine of an automobile, through the magnetic clutch. A fixed scroll 2l, an orbiting scrolling 22, a driving mechanism for the orbiting scroll, and a rotation preventing thrust bearing mechanism 24 for the orbiting scroll 22 are disposed in the interior of the housing l0. The fixed scroll 2l includes a circular end plate 2ll and a spiral element 2l2 affixed to or extending from one end surface of the circular end plate 2ll. The fixed scroll 2l is fixed within the inner chamber of the cup-shaped casing l2 by screws 25 screwed into the end plate 2ll from outside the cup-shaped casing l2. The circular end plate 2ll partitions the inner chamber of the cup-shaped casing l2 into two chambers, a front chamber 27 and a rear chamber 28. The spiral element 2l2 is located within the front chamber 27. A partition wall l22 axially projects from the inner end surface of the cup-shaped casing l2 and the end surface of the partition wall l22 contacts the end surface of the circular end plate 2ll. Thus, the partition wall l22 divides the rear chamber 28 into a discharge chamber 28l formed centrally and an intermediate chamber 282. An O-ring 26 may be disposed between the end surfaces of the partition wall l22 and the end plate 2ll to secure the sealing. The orbiting scroll 22, which is located in the front chamber 27, includes a spiral element 222 affixed to or extending from one end surface of a circular end plate 22l. The spiral element 222 and the spiral element 2l2 interfit at an angular offset of l80° and have a predetermined radial offset. Sealed spaces are thus formed between the spiral elements 2l2 and 222. The orbiting scroll 22 is rotatably supported by an eccentric bushing 23, which is connected with the inner end of the disc-shaped portion l3l eccentrically of the axis of the drive shaft l3, through a radial needle bearing 30. While the orbiting scroll 22 orbits, the rotation of orbiting scroll 22 is prevented by the rotation preventing thrust bearing mechanism 24 which is located between the inner end surface of the front end plate ll and the circular end plate 22l. The rotation preventing thrust bearing mechanism 24 includes a fixed ring 24l, a fixed race 242, an orbiting ring 243, an orbiting race 244 and balls 245. The fixed ring 24l is attached to the inner end surface of the front end plate ll through a fixed race 242 and has a plurality of circular holes 24la. An orbiting ring 243 is attached to the rear end surface of the orbiting scroll 22 through an orbiting race 244 and has a plurality of circular holes 243a. Each ball 245 is placed between a hole 24la of the fixed ring 242 and a hole 253a of the orbiting ring 243, and moves along the edges of both circular holes 24la, 243a. Also, the axial thrust lead from the orbiting scroll 22 is supported by the front end plate ll through the balls 245. The compressor housing l0 is provided with an inlet port (not shown) and an outlet port (not shown) for connecting the compressor to an external refrigerating circuit. Refrigerant gas from the external circuit is introduced into the suction chamber 27l through the inlet port and is taken into the sealed spaces between the spiral elements 2l2 and 222, through open spaces between the spiral elements. The shape of the openings is formed by the outer terminal end of one spiral element and the outer side surface of the other spiral element, respectively. The openings sequentially open and close during the orbital motion of the orbiting scroll 22. When the opening is open, fluid to be compressed is taken into these spaces but no compression occurs. When the opening is closed, thereby sealing off the spaces, no additional fluid is taken into the spaces and compression begins. Since the location of the outer terminal ends of each spiral element 2l2 and 222 is at the final involute angle, location of the openings is directly related to the final involute angle  end. Furthermore, refrigerant gas in the sealed space is moved radially inwardly and compressed in accordance with the orbital motion of the orbiting scroll 22. Compressed refrigerant gas at the centre sealed space is discharged to the discharge chamber 28l through a discharge port 2l3, which is formed at the centre of the circular end plate 2ll. Referring to Figures 3(a) and 3(b), a pair of holes 2l4, 2l5 are formed in the end plate 2ll and the fixed scroll 2l and are located symmetrically so that an axial end surface of the spiral element 222 of the orbiting scroll 22 simultaneously cross over holes 2l4, 2l5. The holes 2l4, 2l5 communicate between the sealed space and the intermediate pressure chamber 282. The hole 2l5 is placed at a position defined by the involute angle ₁ and opens along the inner side wall of the spiral element 2l2. The other hole 2l4 is placed at a position defined by the involute angle (₁ - π) and open along the outer side wall of the spiral element 2l2. A control device, such as a valve member 34 having a valve plate 34l is attached by a fastening device 342 to the end surface of the end plate 2ll to oppose the holes 2l4, 2l5. The valve plate 34l is made of a spring type material so that the recoil strength of the valve plate 34l pushes itself against the opening of the respective holes 2l4, 2l5 to close each hole. A control mechanism 36, which controls communication between the communication chamber 283 and the intermediate chamber 282, includes a cylinder 36l, an I-shaped piston 362 being slidably disposed within the cylinder 36l and having a piston ring 363. The cylinder 36l is defined with a first cylinder portion and a second cylinder portion below the first cylinder portion and having a smaller diameter than that of the first cylinder portion. A taper-shaped step portion 36la connects the first portion and the second portion. As shown in Figure 2, the inner surface of the first cylinder portion is formed as an annular surface. Alternatively, the inner surface of the first cylinder portion can formed with a recessed surface to enlarge the diameter from lower portion to upper portion, as shown in Figure 5. A first opening 36lb is formed on the side surface of the cylinder 36l to be connected with the communication chamber 283, and a second opening 36lc is formed on the bottom portion of the cylinder 36l to be connected with the intermediate pressure chamber 282. The upper portion of the cylinder 36l is connected with the discharge chamber 28l through a capillary tube (not shown). The communication between the cylinder 36l and the discharge chamber 28l may be controlled by an electromagnetic valve 367 disposed on the housing l0. The piston ring 363 is loosely fitted in a groove formed in the upper portion of the piston 362 and has a cut out portion C as shown in Figure 4. When the piston ring 363 is in the first cylinder portion, the cut out portion C is expanded by its own recoil strength. Also, since the diameter of the second cylinder portion is less than that of the first cylinder portion, if the piston ring 363 is in the second cylinder portion, the piston ring 363 is forced so as to become smaller in diameter and the cut out portion C becomes smaller. The operation of the control mechanism 36 will now be described. When the orbiting scroll 22 is operated by the rotation of the drive shaft l3, refrigerant gas which is taken into the sealed spaces defined between the spiral elements 2l2 and 222. The refrigerant gas in the sealed spaces moves toward the centre of the spiral elements 2l2 and 222 with the result of volume reduction and compression, and is discharged from the discharge port 2l3 to the discharge chamber 28l. In this condition, when the electromagnetic valve 367 is energized, i.e. compressed gas in the discharge chamber 28l is introduced into the cylinder 36l through the capillary tube, the pressure in the first cylinder portion becomes higher than that in the second cylinder portion which is connected with the intermediate pressure chamber 282, and the piston 362 is urged downward by the force of compressed gas in the first cylinder portion. In this situation, the second hole 36lc which connects the cylinder 36l with the intermediate pressure chamber 282 is covered by the piston 362, and communication between the communication chamber 283 and the intermediate pressure chamber 282 is prevented. Therefore, the pressure in the intermediate pressure chamber 282 is gradually increased due to leakage of gas from fluid pockets through the holes 2l4 and 2l5. This leakage of compressed gas continues until pressure in the intermediate pressure chamber 282 is equal to the pressure in the fluid pockets. When pressure equalization occurs, holes 2l4, 2l5 are closed by the spring tension of valve plate 34l so that the compression cycle operates normally and the displacement volume of the sealed off fluid pockets is maximized. When the second opening 36lc is closed by the piston 362, the control mechanism 36 is formed so that the upper end portion of the piston 362 is located on the second cylinder portion below the taper-shaped step portion 36la, or lower portion of the recessed surface of the first cylindrical portion. Therefore, the leakage of the compressed fluid into first cylindrical portion is restricted. On the other hand, if the electromagnetic valve 367 is de-energized, communication between the discharge chamber 28l and the cylinder 36l is prevented. Since the upper end portion of the piston 362 is within the second cylinder portion and the piston ring 363 which is disposed on the outer peripheral surface of the upper end portion 362 has a small gap, compressed gas leaks from the first cylinder portion to the second cylinder portion gradually, and the pressure in the first cylinder portion gradually decreases. When the pressure in the cylinder 36l is lower than that in the intermediate pressure chamber 282, piston 362 is pushed upward by the pressure force of the refrigerant gas in the intermediate pressure chamber 282. At that time, the upper end portion of the piston 362 crosses over the taper-shaped step portion 36la toward the first cylinder portion. The force which presses the piston ring 363 radially is removed, and the cut out portion C of piston ring 363 is expanded. Thus, compressed gas in cylinder 36l flows out through the enlarged gap in the piston ring 363. As a result of the leakage of compressed gas, the piston 362 is urged upward rapidly, and the intermediate pressure chamber 282 is connected with the communication chamber 283. The pressure in the intermediate pressure chamber 282 is thus decreased. When the pressure in the intermediate pressure chamber 282 is decreased, the valve plate 34l opens the holes 2l4, 2l5, and thus, the compressed gas flows into the intermediate pressure chamber 282 from the fluid pockets through the holes 2l4, 2l5 and into the communication chamber 283 through the cylinder 36l. Therefore, the volume of compressed gas which is discharged from the sealed off spaces between the scroll elements ll2, 222 into the discharge chamber 28l is decreased, and the compression ratio is decreased. Referring to Figure 6, a second embodiment of a control mechanism in accordance with this invention is shown. In this embodiment, a groove 36ld on the inner surface of cylinder 36l extends from the upper end portion to a predetermined position. This groove 36ld may be replaced by a communication passage 36le formed through the cylinder, as shown in Figure 7. When the second opening 36lc is closed by the piston 362, the control mechanism 36 is formed so that the upper end portion of piston 362 is located at a position slightly lower than the bottom end portion of the groove 36ld or the opening of the communication passage 36le. If the electromagnetic valve 367 is de-energized, the communication between the cylinder 36l and the discharge chamber 28l is prevented. At this time, compressed gas in the cylinder 36l leaks gradually through the small gap in the piston ring 363. Therefore, if the pressure in the cylinder 36l is lower than that in the intermediate pressure chamber 282, the piston 362 moves up slightly. When piston 362 moves up slightly, a gap is formed between the outer peripheral surface of the piston 362 and the groove 36ld, and compressed gas in the cylinder 36l flows into the communication chamber 283 through the groove 36ld or the compressed gas flows into the cylinder portion through the communication way 36le. As a result of leakage of compressed gas in the cylinder, the pressure in the cylinder 36l is greatly decreased, and the piston 362 moves up rapidly. Referring in figure 8, the third embodiment of a control mechanism is shown. A shock absorber 362a is attached to the bottom end portion of the piston 362. If the electromagnetic valve 367 is energized, compressed gas flows into the cylinder 36l from the discharge chamber 28l. Since the pressure of the compressed gas is much higher than the pressure in the intermediate pressure chamber 282, the piston 362 is quickly pushed downward to close the second opening 36lc. At that time, the absorber 362a, positioned under the bottom end portion of the piston 362, absorbes the impact force. Referring to Figure 9, a modification of the control mechanism shown in Figure 8 is disclosed. The shock absorber 362a is disposed around the bottom end portion of the cylinder 36l. A step portion 369 is formed around the second opening 36lc. A spring 368 is disposed between the step portion 369 and the piston 362 to urge the piston upward. If the electromagnetic valve 367 is energized, compressed gas flows into the cylinder 36l from the discharge chamber 28l, and the piston 362 is urged downwards against the recoil strength of the spring 368 and the gas pressure in the intermediate pressure chamber 282. At that time, downward movement of the piston 362 is restricted by the recoil strnegth of the spring 368 and also by contact against the shock absorber 362a provided at the bottom end of portion of the cylinder 36l. Harsh contact between the piston and cylinder is thereby prevented. Referring to Figure l0, a further embodiment of a control mechanism is shown. The piston 362 is made of resinous material having the characteristics of self-lubrication and being frictionless, e.g. polytetrafluoroethylene. Since the piston 362 is made of resinous material even if the piston 362 hits the bottom end portion of the cylinder 36l hard, the shock is absorbed and noise is not generated. Also, the piston 362 has the characteristic of self-lubrication, so that the piston 362 can be smoothly reciprocated within the cylinder.

Claims: 1. A scroll type compressor including a housing (l0) having an inlet port and outlet port; a fixed scroll (2l2) fixedly disposed within the housing and having a circular end plate (2ll) from which a first spiral element (2l) extends; an orbiting scroll (22) having a circular end plate (22l) from which a second spiral element (222) extends, the first and second spiral elements interfitting at an angular and radial offset to make a plurality of line contacts to define at least one pair of fluid pockets within the interior of the housing; a driving mechanism (20,l3,30) operatively connected to the orbiting scroll (22) to effect orbital motion of the orbiting scroll to change the volume of the fluid pockets; a rotation preventing mechanism (24) for preventing rotation of the orbiting scroll during orbital motion, the circular end plate of the fixed scroll dividing the interior of the housing into a front (27) chamber, and rear (28) chamber, the front chamber being connected with the inlet port, and the rear chamber being divided into a discharge chamber (28l) which connects the outlet port and a central fluid pocket formed between the scrolls and an intermediate pressure chamber (282), at least one pair of holes (2l4, 2l5) formed through the circular end plate (2ll) of the fixed scroll to form a fluid channel between the fluid pockets and the intermediate pressure chamber (282), a communication channel (283) formed through the circular plate (2ll) of the fixed scroll to form a fluid channel between the intermediate pressure chamber and the front chamber (27), and a control means (36) disposed on a portion of the intermediate pressure chamber for controlling the communication between the intermediate pressure chamber (282) and the suction chamber (27l), characterised in that the control means (36) comprises a cylinder (36l); a piston (362) slidably disposed with the cylinder; and a communicating means (363), the cylinder connecting with the intermediate pressure chamber (282), the suction chamber (27l) and the discharge chamber (28l), the piston sliding with the cylinder in accordance with the pressure difference between the pressure in the cylinder (36l) and the pressure in the intermediate pressure chamber (282), and the communicating means (363) leaking the discharged gas in the cylinder into the suction chamber (27l) when the piston is pushed upwards from the lowermost position. 2. A compressor according to claim l, wherein the communicating means (363) comprises a piston ring which is provided with cut out portion and is loosely fitted in a groove fromed on an upper portion of the piston (362), the cylinder defining a first cylinder portion and a second cylinder portion connected by a step portion (36la), the diameter of the first cylinder portion being greater than that of the second cylinder portion. 3. A compressor according to claim 2, wherein the first cylinder portion has a taper-shaped surface. 4. A scroll type compressor according to claim l, wherein the communicating means comprises a groove (36ld) formed on an inner wall surface of the cylinder. 5. A compressor according to claim l, wherein the communicating means comprises a passage (36le) formed in a wall of the cylinder, one opening of the aperture being positioned on the inner surface of the cylinder to prevent communication between the cylinder and the intermediate pressure chamber and the other opening of the aperture being at the upper end of the cylinder. 6. A scroll type compressor including a housing (l0) having an inlet port and outlet port; a fixed scroll (2l2) fixedly disposed within the housing and having a circular end plate (2ll) from which a first spiral element (2l) extends; an orbiting scroll (22) having a circular end plate (22l) from which a second spiral element (222) extends, the first and second spiral elements interfitting at an angular and radial offset to make a plurality of line contacts to define at least one pair of fluid pockets within the interior of the housing; a driving mechanism (20,l3,30) operatively connected to the orbiting scroll (22) to effect orbtial motion of the orbiting scroll to change the volume of the fluid pockets; a rotation preventing mechanism (24) for preventing rotation of the orbiting scroll during orbital motion, the circular end plate of the fixed scroll dividing the interior of the housing into a front (27) chamber, and a rear (28) chamber, the front chamber being connected with the inlet port, and the rear chamber being divided into a discharge chamber (28l) which connects the outlet port and a central fluid pocket formed between the scrolls and an intermediate pressure chamber (282), at least one pair of holes (2l4, 2l5) formed through the circular end plate (2ll) of the fixed scroll to form a fluid channel between the fluid pockets and the intermediate pressure chamber (282), a communication channel (283) formed through the circular plate (2ll) of the fixed scroll to form a fluid channel between the intermediate pressure chamber and the front chamber (27), and a control means (36) disposed on a portion of the intermediate pressure chamber for controlling the communication between the intermediate pressure chamber (282) and the suction chamber, characterised in that the control means (36) comprises a cylinder (36l); a piston (362) slidably disposed with the cylinder and a shock absorbing element (362a), the cylinder connecting with the intermediate pressure chamber (282), the suction chamber (27l) and the discharge chamber (28l), the piston sliding with the cylinder in accordance with the pressure difference between the pressure in the cylinder (36l) and the pressure in the intermediate pressure chamber (282) and the shock absorbing element (362a) being disposed on bottom surface of the cylinder for absorbing the impact force between the inner end surface of the cylinder and the piston and for securing sealing between the piston and the inner end surface of the cylinder. 7. A compressor according to claim 6, wherein the piston is made of a resinous material.

Inventors: MABE, ATSUSHI, SATO, TADASHI, TERAUCHI, KIYOSHI
Applicants: SANDEN CORPORATION
Application year: 1986
Main classification: F04C29
IPC codes: F04C28, F04C18, F16K31