DE19821265A1 - Coolant compressor - Google Patents

Description

The invention relates to a coolant compressor, and in particular one Coolant compressor with a high pressure chamber, which on an outside of a cylinder body is designed to pulsate the flow of the Reduce cooling gas.

The state of the art

Fig. 1 shows in cross section the entirety of a swash plate compressor (coolant compressor) according to the prior art.

The compressor has a cylinder body 101 formed with a plurality of cylinder bores 106 , which cylinder bores 106 extend axially through it and are arranged at predetermined angular intervals around a drive shaft 105 . The rear end of the cylinder body 101 is fastened via a valve plate 102 to a rear head part 103 , which is formed with a delivery pressure chamber 112 and a suction chamber 113 .

The front end face of the cylinder body 101 is fastened to a front head part 104 . In the front head part 104 , a swash plate chamber 108 is formed which receives a swash plate 110 .

The rear head part 103 , the cylinder body 101 and the front head part 104 are longitudinally compressed by a plurality of through bolts (not shown) so as to connect the parts together as a whole.

A high pressure chamber 122 is formed on an outside of the cylinder body 101 to reduce a high pressure from the flow of the cooling gas. The outside of the cylinder body 101 is formed with a recess 101 a, and a cover 160 is attached to an edge of the opening of the recess 101 a with the interposition of an O-ring 153 .

The high pressure chamber 122 is limited by the inner sides of the cover 160 and the recess 101 a of the cylinder body 101 . The high pressure chamber 122 is connected to the outlet chamber 112 through a communication passage 134 which extends parallel to the drive shaft 105 and an oblique bore 135 which extends radially outward from the outlet chamber 112 and obliquely with respect to the axis of the drive shaft 105 .

Coolant outlet passages 116 are formed in the valve plate 102 , the function of which is to establish a connection between the relevant cylinder bore 106 and the delivery pressure chamber 112 . Furthermore, coolant inlet passages 115 are provided in the valve plate 102 , the function of which is to establish a connection between the respective cylinder bore 106 and the suction chamber 113 .

The coolant outlet passages 116 are each opened and closed by a corresponding outlet valve 117 , which is fastened on the rear end face of the valve plate 102 together with valve stops 118 by a rivet 119 .

A guide recess 127 is formed in the vicinity of the rivet 119 in order to connect the delivery pressure chamber 112 via a throttle 126 to a recess 125 which is formed in the cylinder body 101 . As shown, the recess 125 serves to receive a radial bearing 147 .

High-pressure cooling gas from the delivery pressure chamber 112 is fed via the guide recess 127 and the throttle 126 to the recess 125 which serves to receive the radial bearing 147 , and from there it is further fed to the swash plate chamber 108 via a recess 128 which serves to receive an axial bearing 146 . In this way, the thrust bearings 145, 146, the radial bearings 147, 148 and the other parts are provided in the swash plate chamber 108 with the cooling gas contained in the oil.

A cooling gas flow conveyed from a compression chamber to the delivery pressure chamber 112 expands in the delivery pressure chamber 112 . The flow rate of the cooling gas flowing out of the discharge pressure chamber 112 is throttled through the oblique bore 135 and the communication passage 134 . The cooling gas expands again as it flows into the high pressure chamber 122 , and finally its flow rate is throttled through an outlet passage 123 , whereupon the cooling gas flows out of the compressor. In this way, the pulsation generated by the flow of the cooling gas within the compressor is reduced.

The problem here, however, is that since the flow of the cooling gas is slowed down as it flows into the delivery pressure chamber 112 and the high pressure chamber 122 , part of the gaseous oil contained in the cooling gas is separated from the cooling gas and settles in lower regions of the two chambers 112 and 122 collects or remains.

Since the compressor is designed so that the cooling gas flows out of the high-pressure chamber 122 , the flow of the cooling gas is braked, particularly within the high-pressure chamber 122 , when it hits the inside of the cover 160 . Therefore, due to the different specific densities of the oil and the cooling gas, the oil simply separates from the cooling gas and collects in the lower region of the high-pressure chamber 122 .

In this way, the oil contained in the cooling gas is gradually reduced in quantity while flowing in the compressor, until finally sufficient cooling and lubrication of the thrust bearing 145 , the radial bearing 148 and the other parts in the swash plate chamber 108 is not possible. This can occur above all if the compressor has an operating state with high speed at low load with a minimal delivery rate or delivery rate, in which the flow rate of the cooling gas is low.

It is therefore an object of the invention to provide a new coolant compressor to provide.

According to a first aspect of the invention, this object is achieved by the Subject of claim 1. According to this coolant compressor the oil or lubricant contained in the cooling gas in the second High pressure chamber through the oil separator from the cooling gas separated, and the oil is at the bottom of the second high pressure chamber collected. Thereupon the collected oil is passed through the connection passage  fed back to the swash plate chamber, so that the Swashplate chamber supplied amount of oil is increased, and so one Thrust bearing, a radial bearing and other parts within the Swashplate chamber Oil in sufficient quantity for its lubrication is fed.

So you get a reliable coolant compressor with a construction which enables a thrust bearing, a radial bearing and other parts also supply enough oil within a swash plate chamber when the compressor is in a high speed operating condition low load in which the amount of coolant flow is small.

A preferred embodiment of the invention results from the Subject of claim 2. According to this preferred Embodiment is the cooling gas flow through at least one through the plate continuous recess throttled which plate between the Recess and the lid is formed. This will make it through in one the inner walls of the recess and the plate defined space generated pulsation of the cooling gas is further reduced. Continue to be Cooling gas flows slowed down when they hit the plate, and that in the Oil contained in the cooling gas is due to the different densities of oil and Cooling gas separated from the cooling gas.

Another preferred embodiment of the invention results from the Subject of claim 3. The throttle causes a uniform Oil flow to the swash plate chamber and thus an even one Lubricate. Furthermore, the pressure difference between the Maintain high pressure chamber and swash plate chamber.

Another preferred embodiment of the invention results from the Subject of claim 4. The seal seals between the Cylinder body and the front headboard to prevent gas and oil from escaping from the swash plate chamber and the oil return from the second To prevent high pressure chamber.

Another preferred embodiment of the invention results from the Subject of claim 5. The seal is here simultaneously as  Throttle used for oil return. This allows greater freedom in the formation of the oil return connection.

An alternative to the embodiment of the invention according to claim 5 results from the subject matter of claim 6. The recess Small diameter is in the manufacture of the front of the Cylinder body made of simple and therefore inexpensive to install.

Another preferred embodiment of the invention results from the Subject of claim 7. The second passage allows one Oil supply that extends further into the swash plate chamber, and thus better lubrication. The oil supply from the area of the front Head section provides better lubrication of the thrust and radial bearings and reliably prevents the bearings from seizing.

Another preferred embodiment of the invention results from the Subject of claim 8. Since the flow restriction in the is formed front head part, the oil of the swash plate chamber are supplied from near the axial bearing and the radial bearing, and this reliably prevents these bearings from seizing. The throttling through the second continuous recess causes a more even oil supply to the swash plate chamber.

Another preferred embodiment of the invention results from the Subject of claim 9. By shaping the continuous recess with a small diameter with a desired angle of inclination it is possible to a desired range of Swashplate chamber oil for the lubrication of the radial bearing and axial bearing supply, which further increases the lubrication performance of the compressor.

Another preferred embodiment of the invention results from the Subject of claim 10. Implementation of the second continuous recess at the location of the rotatable part and its Bearing improves the lubrication of this part.

Another preferred embodiment of the invention results from the Subject of claim 11. This construction makes it possible  Oil one by rotating the drive hub and the other parts flow of cooling gas generated within the swash plate chamber feed and thus further improve the lubrication of the components.

Another preferred embodiment of the invention results from the Subject of claim 12. The formation of the plate with a Multiple holes increase security since plugging a hole does not affect the function of the plate. Furthermore, a more regular one Flow guaranteed.

Another preferred embodiment of the invention results from the Subject of claim 13. Since the baffle plate, which also serves as a seal serves, which has bulged protuberance for sealing the high pressure chamber, the O-ring used in the prior art can be omitted become, and it is no longer necessary to carry out a work process Create a groove in which the O-ring is inserted.

Further details and advantageous developments of the invention result result from the following described and shown in the drawing, in no way to be understood as a limitation of the invention Exemplary embodiments, as well as from the subclaims. It shows:

Fig. 1 shows a longitudinal section through a refrigeration compressor (swash plate compressor) according to the prior art,

Fig. 2 is a longitudinal section through a refrigeration compressor (swash plate compressor) according to a first embodiment of the invention,

Fig. 3 is an enlarged sectional view of essential parts of the compressor of Fig. 2,

FIG. 4A is a plan view of a baffle plate of Fig. 3,

FIG. 4B is a sectional view of the baffle plate,

Fig. 5 is a plan view of a gasket which is used in Fig. 2,

Fig. 6 is an enlarged view showing essential parts showing a modification of the swash plate type compressor,

Fig. 7 is an enlarged section showing essential parts of a further modification of the swash plate compressor, and

Fig. 8 is an enlarged view showing essential parts of a refrigerant compressor (swash plate compressor) shows a second embodiment of the present invention.

Fig. 2 shows the whole arrangement of a swash plate compressor (refrigerant compressor) according to a first embodiment of the invention, Fig. 3 essential parts of the compressor on an enlarged scale, Fig. 4A is a plan view of a baffle plate, Fig. 4B is a sectional side view thereof, and Fig. 5 a top view of a seal.

The swash plate compressor has a cylinder body 1 , one end face of which is attached to a rear head part 3 via a valve plate 2 and the other end face of which is attached to a front head part 4 via a seal 80 .

The rear head part 3 , the cylinder body 1 and the front head part 4 are longitudinally compressed by a plurality of through bolts (not shown) extending from the rear head part 3 through the cylinder body 1 and the front head part 4 , and so the various parts connect to a whole.

In the cylinder body 1 , 5 cylinder bores 6 are formed, which extend through it in the axial direction and are arranged at a predetermined angular distance around a drive shaft 5 . A displaceable piston 7 is arranged in each cylinder bore 6 .

A high pressure chamber (second high pressure chamber) 22 is formed on an outer side on the circumference of the cylinder body 1 . The peripheral outside of the cylinder body 101 is formed with a recess 1 a. A cover 60 is attached to an edge 1 b of an opening of the recess 1 a via a baffle plate (oil separating member) 50 .

The high pressure chamber 22 is delimited by the inside of the cover 60 and the recess 1 a of the cylinder body 1 . Cooling gas flows through a discharge passage 23 from the high pressure chamber 22 and passes to a (not shown) on a front surface of a capacitor mounted radiator (not shown).

The baffle plate 50 , which also serves as a seal, is formed from a cold-rolled steel / steel strip with a cut length and has the same shape as that of a cross section through the recess 1 a together with the opening and the edge 1 b defining the opening. The baffle plate 50 has an annular bulge 51 , which is formed by embossing an outer part opposite the edge 1 b, and a plurality of through holes 52 , all of which are formed over a part thereof opposite the opening of the recess 1 a ( Fig. 4). The holes 52 serve as passages through which cooling gas flows.

The baffle plate 50 is attached to the edge 1 b and to the cover 60 by two bolts (not shown) which extend through through holes 53 . The baffle plate 50 divides an inner space of the high pressure chamber 22 into a lower high pressure chamber 22 A and an upper high pressure chamber 22 B.

The recess 1 a has a rear wall in which a passage 31 is formed, which is connected via a pipe connector 70 to a passage 34 formed in the rear head part 3 . An O-ring 71 is provided for sealing between the pipe connector 70 and the cylinder body 1 and an O-ring 72 for sealing between the pipe connector 70 and the rear head part 3 .

In the rear head part 3 , a delivery pressure chamber (first high pressure chamber) 12 and, around this, a suction chamber 13 are formed. The delivery pressure chamber 12 and the passage 34 are connected to each other via an inclined recess 35 , which is formed radially outward from the delivery pressure chamber 12 and obliquely with respect to the axis of the drive shaft 5 , but not through the suction chamber 13 .

In the valve plate 2 , coolant outlet passages 16 are formed, the function of which is to establish a connection between the relevant compression chamber 91 , which is formed in the corresponding cylinder bore 6 , and the delivery pressure chamber 12 , and coolant inlet passages 15 , the task of which is to establish a connection between the relevant compression chamber 91 and the suction chamber 13 , in each case at predetermined angular intervals.

The coolant outlet passages 16 are each opened and closed by a corresponding outlet valve 17 , which is fastened together with valve stops 18 on the rear face of the valve plate 2 by a rivet 19 .

On the other hand, the coolant inlet passages 15 are opened and closed by corresponding suction valves 21 , which are fastened on the front end face of the valve plate 2 by the rivets 19 , with which the outlet valves 17 and their valve stops 18 are also fastened.

A guide recess 27 is formed in the vicinity of the rivet 19 and serves to connect the delivery pressure chamber 12 via a throttle 26 to a recess 25 formed in the cylinder body 101 for receiving a bearing.

High-pressure cooling gas from the delivery pressure chamber 12 is supplied to the recess 25 via the guide recess 27 and the throttle 26 , and from there it is supplied to a swash plate chamber 8 via a recess 28 (for receiving a bearing 46 ).

Furthermore, the recess 1 a connected to the swash plate chamber 8 through a communication passage 32 is formed which has a passage 32 A, the lower at a portion or bottom portion of a front side wall of the recess 1 a, and a passageway having 32 B, which at the rear end of the front head part 4 is formed with the interposition of the seal 80 .

The seal 80 seals between the cylinder body 1 and the front head part 4 in order to prevent gas and oil from escaping from the swash plate chamber 8 .

The seal 80 is formed by stamping and stamping a cut length of cold rolled steel / steel strip into a generally annular member 81 , as shown in FIG. 5. A small diameter hole 83 and a plurality of through holes 82 through which bolts extend are formed in the annular member 81 . The hole 83 with a small diameter is formed or located at an intermediate region of the connection passage 32 and serves as a throttle between the high-pressure chamber 22 and the swash plate housing 8 , which have different pressures.

The swash plate housing 8 receives a pressure receiving flange 41 , a drive hub 42 and a swash plate 10 .

The pressure receiving flange 41 is rigidly connected to the drive shaft 5 and is rotatably supported on an inner wall of the front head part 4 by an axial bearing 43 .

The drive hub 42 is rotatably mounted on the drive shaft 5 via a joint ball 9 and at the same time is connected to the pressure receiving flange 41 via a joint connection 49 .

The swash plate 10 is arranged on the drive hub 42 with the interposition of an axial bearing 45 and a radial bearing 48 so that it can perform a wobble movement.

In the cylinders 6 pistons 7 are arranged to be longitudinally displaceable, and these are each connected to the swash plate 10 via a piston rod 11 in the manner shown, so that when the shaft 5 rotates, the pistons 7 each have their cylinder 6 corresponding to the axial wobble movement of the swash plate 10 perform a reciprocating motion. The angle of inclination of the swash plate 10 changes depending on the pressure in the swash plate chamber 8 .

Way of working

If the torque of a motor, not shown, is transmitted to the drive shaft 5 in order to set it in rotation, then the pressure receiving flange 41 and the drive hub 42 rotate synchronously with the drive shaft 5 , as a result of which the swash plate 10 performs an axial wobble movement. This causes a reciprocating movement of the individual pistons 7 in the cylinder bores 6 , and this causes a change in the volume of the compression chamber 91 in the cylinder 6 , which is assigned to the corresponding piston 7 . With this change in volume of the compression chamber 91 , cooling gas is sucked in, compressed and conveyed in succession. In this way, high-pressure cooling gas is conveyed in an amount which corresponds to the angle of inclination of the swash plate 10 .

When one of the outlet valves 17 opens, cooling gas which has been compressed in the compression chamber 91 is supplied to the delivery pressure chamber 12 via the corresponding coolant outlet passage 16 . Subsequently, the cooling gas in the discharge pressure chamber 12 flows through the inclined bore 35 and the passages 34 and 31 into the lower high pressure chamber 22 A. The flow rate at which the cooling gas is to flow into the lower high pressure chamber 22 A is through the inclined bore 35 and Passages 34 and 31 throttled.

The cooling gas flows further via the baffle plate 50 into the upper high-pressure chamber 22 B, the baffle plate 50 having the holes 52 which serve to restrict the flow of the cooling gas flowing into the upper high-pressure chamber 22 B. Therefore, the pulsation of the flow of the cooling gas in the upper and lower high pressure chambers 22 A and 22 B is significantly reduced.

Flows of cooling gas which flow into the lower high pressure chamber 22 A impinge on the baffle plate 50 . As a result, the cooling gas flows are decelerated and oil 90 in the cooling gas is separated from the cooling gas and, due to the different specific densities of cooling gas and oil 90, drips down and collects at the bottom of the high-pressure chamber 22 , as shown in FIGS. 2 and 3 can be seen.

Since flows of cooling gas, which flow through the holes 52 into the upper high-pressure chamber 22 B, strike the wall surfaces 60 a of the cover 60 , they are braked, and oil contained in the cooling gas is separated therefrom. This separated oil also collects at the bottom of the high pressure chamber 22 after dripping through the holes 52 .

Since the pressure in the swash plate chamber 8 is lower than that in the high pressure chamber 22 which is collected at the bottom of the high pressure chamber 22 oil 90 flows via the communication passage 32 and the recess 83 with a small diameter in the swash plate chamber 8 and is there to the thrust bearing 45, the radial bearing 48 and fed to the other parts.

According to the first embodiment, the swash plate chamber 8 is increased amount of supply of oil because the separated by the baffle plate from the cooling gas and collected at the bottom of the high pressure chamber 22 oil 90 through the communication passage 32 and the recess is returned 83 with a small diameter in the swash plate chamber 8 , and thus a sufficient supply of oil 90 is ensured for the thrust bearing 45 , the radial bearing 48 and the other parts and at the same time prevents the bearings 45 and 48 from seizing even when the compressor is in a high-speed operating state under low load at which the flow rate of the cooling gas is small. Furthermore, the pulsation of the flow of the cooling gas is further reduced because the high pressure chamber 22 is divided into two parts by the baffle plate 50 .

Since the baffle 50 , which also serves as a seal, has the bulge 51 for sealing the high pressure chamber 22 , the O-ring 153 used in the prior art can be omitted, and it is no longer necessary to have one Carry out operation to create a groove in which the O-ring 153 is inserted.

Fig. 6 shows essential parts of a modification of the swash plate compressor according to the first embodiment in an enlarged view. Components and elements which correspond to those of the above exemplary embodiment have the same reference symbols and are not listed again in the description.

In this modification, a passage 132 A is formed as a recess with a small diameter, which serves as a throttle. The small recess 183 recessed in the seal 180 does not have to serve as a throttle, so that the small hole 183 has a larger inner diameter than that of the passage 132 A.

This modification can have the same effects as the above first embodiment can be obtained.

Fig. 7 shows essential parts of another modification of the swash plate compressor according to the first embodiment and in an enlarged view. Components and elements which correspond to those of the above exemplary embodiment have the same reference symbols and are not listed again in the description.

In this modification, a passage 132 B has an oblique bore 84 which extends through an outer wall of the front head portion 40 , is oblique with respect to the axis of the drive shaft and has a small diameter to serve as a throttle, and further has the Passage 132 B has a passage 85 formed in the rear end wall of the front head part 4 , which serves to establish a connection between a small hole 183 formed in the seal 180 and the oblique bore 84 .

This modification can also provide the same effects as those obtained in the first embodiment. In addition, in this modification compared to the first embodiment, by forming the oblique bore at a suitable angle of inclination with respect to the axis of the drive shaft 5, it is possible to supply the radial bearing 48 and the axial bearing 45 in the swash plate chamber 8 with a larger amount of oil for lubrication and thus further increasing the lubrication performance of the compressor. Fig. 8 shows important parts of a swash plate compressor according to a second embodiment and in an enlarged view. Components and elements which correspond to those of the above exemplary embodiment have the same reference symbols and are not listed again in the description.

In the second embodiment, as can be seen in Fig. 8, a passage 32 C is formed in a peripheral outer wall of the front head part 204 in the axial direction or along the drive shaft (not shown), which has the function via a in the seal 180 formed through recess 283 to connect to the passage 32 A. The front head part 4 has an inner outer wall which has an oblique throttle 86 which extends from a front end portion of the passage 32 G to the swash plate chamber 8 so as to supply the oil 90 to a desired area of the swash plate chamber 8 .

The oblique throttle 86 is, in the vicinity of the thrust bearing 45 (see FIG. 2) and the radial bearing 48, to a certain extent offset in a direction of rotation of the drive shaft 5 with respect to its axis. This construction enables the oil 90 to be supplied to a flow of cooling gas generated by the rotation of the drive hub 42 and the other parts within the swash plate chamber 8 , thereby improving the lubrication of the components.

In the compressor formed as above, cooling gas flows delivered to the delivery pressure chamber 12 impinge on the inner walls of the delivery pressure chamber 12 and are braked in the process. A part of the oil contained in the cooling gas is separated from it in the delivery pressure chamber 12 and then flows into the high pressure chamber 22 . In the second high pressure chamber 22 , more oil is separated from the cooling gas, and the cooling gas flows through the outlet passage 23 from the compressor into the condenser (not shown).

The oil 90 separated from the cooling gas in the high pressure chamber 22 is supplied to the swash plate chamber 8 via a connecting passage formed with the passages 32 A and 32 G and the oblique bore 85 .

The second embodiment can provide the same effects as with the first embodiment can be obtained.

In addition, according to the swash plate compressor of the second embodiment, the oil 90 separated from the cooling gas in the high pressure chamber 22 can be supplied to the swash plate chamber 8 through the inclined bore 85 formed near the thrust bearing 45 and the radial bearing 48 , and thus sufficient cooling and lubrication of the Thrust bearings 45 , 46 , the radial bearings 47 , 48 and the other parts can be guaranteed. This can prevent the bearings from seizing even when the compressor is in a high-speed, low-load, low-flow operating state where the cooling gas flow rate is small.

Particularly in an operating state of the compressor with high speed and low load, there is a large load on the axial bearing 45 , so that this exemplary embodiment more effectively prevents the axial bearing 45 from seizing than the first exemplary embodiment.

Although in the above exemplary embodiments the baffle plate 50 is formed in its entire central part with the holes 52 through which cooling gas flows, this is not to be understood as a restriction, but it is only necessary that the baffle plate 50 is formed with at least one hole.

Although only cases are described in the above embodiments, in which this invention applied to a swash plate compressor is not to be understood as a limitation either, but rather the Invention can be used for other varied types of refrigerant compressors be applied.

It is also clear to the person skilled in the art that the exemplary embodiments represent preferred embodiments of the invention, and that varied Changes and modifications can be made without to depart from the spirit and field of invention.

Claims (14)

1. coolant compressor, which has a cylinder body ( 1 ),
a valve plate ( 2 ),
a first head part ( 3 ) which is attached to an end face of the cylinder body ( 1 ) with the interposition of the valve plate ( 2 ),
a second head part ( 4 ) which is fastened to another end face of the cylinder body ( 1 ),
a first high-pressure chamber ( 12 ) which is arranged in the first head part ( 3 ) and which, during operation, is supplied with a pressurized cooling gas from compression chambers ( 91 ) formed in the cylinder body,
a swash plate chamber ( 8 ) formed in the second head part, a second high pressure chamber ( 22 ) which is formed in the cylinder body ( 1 ) and is connected to the first high pressure chamber ( 12 ),
an outlet connection ( 23 ) via which the pressurized cooling gas in the second high-pressure chamber ( 22 ) is conveyed out of the compressor,
an oil separator for separating oil from the pressurized cooling gas flowing to the second high pressure chamber ( 22 ), and a communication passage ( 32 ) for supplying the oil ( 90 ) separated from the pressurized cooling gas in the second high pressure chamber ( 22 ) to the swash plate chamber ( 8 ). 2. Coolant compressor according to claim 1, wherein the second high pressure chamber ( 22 ) has a recess ( 1 a), which is formed in an outer peripheral surface of the cylinder body ( 1 ), and a cover ( 60 ), which at an edge ( 1 b) the opening of this recess ( 1 a) is fastened, the oil separating member having a plate ( 50 ) in which at least one continuous recess ( 52 ) is formed and which is arranged between the recess ( 1 a) and the cover ( 60 ). 3. A coolant compressor according to claim 1 or 2, wherein the connecting passage ( 32 ) is provided with a flow restriction ( 83 , 84 , 86 , 132 A). 4. The refrigeration compressor according to any one of the preceding claims, wherein between the other end side of the cylinder body (1) and the second head part (4) a seal (180, 280) is arranged, and the communication passage (32) a first passage (32 A, 132 A), which extends from the second high-pressure chamber ( 22 ) to the other end of the cylinder body ( 1 ), and a continuous recess ( 83 , 183 , 283 ) which is formed in this seal ( 180 , 280 ). 5. A coolant compressor according to claim 4, wherein the continuous recess is a throttle recess ( 83 ), and the flow restriction is formed by this throttle recess ( 83 ) ( Fig. 3). 6. A coolant compressor according to claim 4, wherein the first passage is a continuous recess ( 132 A) with a small diameter, and the flow restriction is formed by this continuous recess ( 132 A) with a small diameter ( Fig. 6). 7. A coolant compressor according to claim 3, wherein a seal ( 180 , 280 ) is arranged between the other end face of the cylinder body ( 1 ) and the second head part ( 4 ),
and in which the connecting passage ( 32 ) has a first passage ( 32 A) which extends from the second high-pressure chamber ( 22 ) to the other end face of the cylinder body ( 1 ),
a first continuous recess ( 32 A, 132 A) which penetrates the seal ( 180 , 280 ),
a second passage ( 32 C, 85 ) which extends in a peripheral wall of the second head part ( 4 ), which peripheral wall defines the swash plate chamber ( 8 ),
and a second continuous recess ( 84 , 86 ) which extends through the peripheral wall from the second passage ( 32 C, 85 ) to the swash plate chamber ( 1 ) ( Fig. 7, 8). 8. A coolant compressor according to claim 7, wherein the second continuous recess ( 84 , 86 ) is a recess of small diameter, and the flow restriction is formed by this recess ( 84 , 86 ) of small diameter ( Fig. 7, 8). 9. coolant compressor according to claim 8, with a drive shaft ( 5 ) which extends through the swash plate chamber ( 8 ), wherein the recess ( 84 , 86 ) of small diameter through the peripheral wall obliquely, based on the longitudinal axis of the drive shaft ( 5 ), extends ( Fig. 7, 8). 10. Coolant compressor according to claim 8, with a drive shaft ( 5 ) which extends through the swash plate chamber ( 8 ), and with a rotatable part arranged on the drive shaft ( 5 ), which has at least one bearing ( 43 , 45 , 48 ), wherein the second passage ( 86 ) extends through the peripheral wall to a location which corresponds approximately to the position of the at least one bearing ( 43 , 45 , 48 ) ( FIG. 8). 11. A refrigerant compressor according to claim 10, wherein the small-diameter recess ( 86 ) opens to the swash plate chamber ( 8 ) at a position which is offset with respect to a rotational direction of the rotatable member. 12. A refrigerant compressor according to claim 2 or 3, wherein the plate ( 50 ) as at least one through recess ( 52 ) has a plurality of holes ( 52 ) formed on a portion of the plate ( 50 ) that the opening of the recess ( 1 a) is opposite. 13. A coolant compressor according to claim 2 or 3, wherein the plate ( 50 ) has a bead-shaped projection ( 51 ) which is formed on an approximately annular portion which is opposite the edge ( 1 b) of the opening of the recess ( 1 a). 14. A coolant compressor according to claim 12, wherein the plate ( 50 ) has a bead-shaped projection ( 51 ) which is formed on an approximately annular portion which is opposite the edge ( 1 b) of the opening of the recess ( 1 a).