KR20100122055A - Fixed displacement piston type compressor - Google Patents

Abstract

PURPOSE: A fixed capacity type piston compressor is provided to limit a specific connection path and prevent a relative rotation of a thrust race and a cylinder block. CONSTITUTION: A fixed capacity type piston compressor comprises a cylinder block(11), a swash plate, a piston, a swash chamber, a plurality of connection paths(39), a thrust bearing, and a thrust race rotation preventing unit(71,72). The cylinder block supports a rotation axis and includes a plurality of cylinder bores(40) arranged around the rotation axis. The swash plate is integrated with the rotary shaft. The refrigerant of a suction pressure is inputted to the swash chamber. The plurality of connection paths connect the swash chamber and the suction chamber. The thrust bearing is arranged between the cylinder block and the swash plate. The thrust race rotation preventing device prevents the rotation about the cylinder block of a cylinder block side thrust race(63) and narrows or blocks the part of connection paths.

Description

FIXED DISPLACEMENT PISTON TYPE COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fixed displacement piston compressor, and more particularly, to a fixed displacement type piston having a swash plate, a swash plate chamber for accommodating the swash plate, and a plurality of communication paths for passing refrigerant before compression from the swash plate to the suction chamber. It relates to a piston compressor.

Conventional fixed displacement piston compressors include a plurality of communication paths through which refrigerant passes from a swash plate chamber to a suction chamber, and a compressor having a thrust bearing between the cylinder block and the swash plate exists.

If the thrust race on the cylinder block side provided in the thrust bearing can rotate with respect to the cylinder block, wear of the cylinder block occurs by the sliding contact of both. For this reason, it is requested to prevent the thrust race on the cylinder block side and the relative rotation of a cylinder block.

Moreover, the function of a specific communication path among the plurality of communication paths which let refrigerant | coolant pass from a swash plate chamber to a suction chamber in order to store lubricating oil as much as possible in a swash plate chamber, and to adjust the compression balance in several compression chambers. There is a case to limit.

For example, Patent Document 1 discloses a swash plate type compressor capable of preventing relative rotation of a cylinder's thrust race and a cylinder in a thrust bearing.

The swash plate type compressor includes a swash plate which is inclined with respect to the shaft center and is driven to rotate about the shaft center, a piston disposed at a position eccentric from the shaft center, and reciprocated in a direction parallel to the shaft center according to the rotational movement of the swash plate, The cylinder which accommodates a piston is provided. A thrust bearing is disposed between the cylinder and the swash plate, and a recess is formed in the cylinder side thrust race of the thrust bearing, while a protrusion is formed in the cylinder, and the protrusion and the recess are engaged. By engaging these projections with the concave grooves, relative rotation of the thrust race and the cylinder can be prevented, and abrasion between the thrust race and the cylinder can be prevented.

In addition, Patent Document 2 discloses a compressor that can limit the function of a specific suction passage among a plurality of suction passages through which a refrigerant passes from the swash plate chamber to the suction chamber.

In this compressor, the suction chamber for supplying refrigerant to the plurality of operation chambers is connected to the suction port connected to the external refrigerant circuit on the evaporator side via the swash plate chamber, so that the refrigerant flowing into the suction port passes through the swash plate chamber to the suction chamber. Inflow. In this compressor, the passage resistance of the suction passage which opens toward the space from the upper side of the shaft among the plurality of the suction passages which guides the fluid in the swash plate to the suction chamber of the suction passage which opens toward the swash chamber from the lower side of the shaft. It is comprised so that it may become small compared with passage resistance.

As a result, a large amount of fluid is sucked into the suction chamber from the suction passage opened on the upper side of the shaft compared to the suction passage opened on the lower side of the shaft, so that a large amount of liquid fluid can be prevented from being sucked into the suction chamber.

Patent Document 1: Japanese Utility Model Application Laid-Open No. 7-10474 Patent Document 2: Japanese Unexamined Patent Publication No. 2000-297745

In the prior art disclosed in Patent Document 1, the projections and concave grooves for preventing relative rotation of the thrust race and the cylinder are merely formed for the purpose of preventing the relative rotation of both.

On the other hand, the prior art disclosed in Patent Document 2 is merely a technique for reducing the hole diameter of the suction passage using a dedicated member such as a throttle means for limiting the function as the passage of the suction passage.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a mechanism having a function of preventing a relative rotation of a thrust race and a cylinder block and a function of restricting a function as a passage of a specific communication path. The present invention provides a fixed displacement piston compressor.

MEANS TO SOLVE THE PROBLEM In order to solve the said subject, this invention is accommodated in the cylinder block which supports a rotating shaft, and has a several cylinder bore arrange | positioned around the said rotating shaft, the swash plate integrated with the said rotating shaft, and the said several cylinder bore, A housing coupled to an end of the cylinder block, a swash plate chamber in which the piston interlocked with the rotation of the rotary shaft, the swash plate is accommodated, and a refrigerant of suction pressure is introduced therein, and a suction chamber and a discharge chamber; A plurality of communication paths for communicating the swash plate chamber and the suction chamber, a thrust bearing disposed between the cylinder block and the swash plate and configured to provide a thrust bearing of the swash plate, and the cylinder block provided in the thrust bearing. For fixing with a thrust race anti-rotation mechanism for preventing rotation of the side thrust race with respect to the cylinder block. In the piston type compressor, the thrust race-rotating mechanism is characterized in that of a plurality of the communication, or narrowing or blocking a part of the communication.

According to the present invention, the thrust race on the cylinder block side in the thrust bearing is prevented from rotating to the cylinder block by the thrust race anti-rotation mechanism. In addition, some of the communication paths are narrowed or blocked by the thrust race anti-rotation mechanism.

As a result, the thrust race anti-rotation member can prevent relative rotation of the thrust race and the cylinder block on the cylinder block side, and can limit the function as a passage of some communication paths.

Moreover, in this invention, in the state in which the said compressor is installed in the vehicle, the said thrust race anti-rotation mechanism may narrow or prevent the said communication path which becomes the lowest in the up-down direction among the said several communication paths. .

In this case, in the state where the compressor is installed in the vehicle, lubricating oil is stored in the bottom of the swash plate chamber, and the communication path which becomes the lowest in the vertical direction is narrowed or blocked by the thrust race anti-rotation mechanism. As a result, the passage of lubricating oil in the lowermost communication path is restricted, and the lubricating oil can be easily stored in the swash plate chamber.

Moreover, in this invention, the coolant introduction port which introduces the refrigerant | coolant of a suction pressure into the said swash plate chamber is provided, The thrust race anti-rotation mechanism narrows the said communication path closest to the said refrigerant introduction port among the said several communication paths. Or may be prevented.

In this case, the communication path closest to the refrigerant inlet is closed or blocked by the thrust race anti-rotation mechanism. In the communication path closest to the refrigerant inlet, many refrigerants are more likely to flow compared to the communication path away from the refrigerant inlet, but the communication path closest to the refrigerant inlet is narrowed or blocked, so as to connect to the communication path closest to the refrigerant inlet. It is possible to improve the balance of the refrigerant inflow amount with respect to the communication path away from the refrigerant port.

Moreover, in this invention, the said thrust race anti-rotation mechanism is provided with the protrusion part which protruded from the periphery of the said thrust race, and the protrusion which is formed in the said cylinder block, and regulates the movement of the said protrusion part. It may be provided, and the protrusion piece may narrow or prevent some of the communication paths.

In this case, of the plurality of communication paths, some of the communication paths are narrowed or blocked by the protrusions, and the protrusions are restricted by the protrusions to prevent rotation of the thrust race.

It is possible to prevent the relative rotation of the thrust race and the cylinder block by forming a protrusion piece in the thrust race and to form a protrusion in the cylinder block, and to narrow or prevent some communication paths.

The present invention can provide a fixed displacement piston compressor having a mechanism that has a function of preventing relative rotation of a thrust race and a cylinder block, and a function of restricting a function as a passage of a specific communication path.

BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows the fixed displacement type piston compressor which concerns on 1st Embodiment.
FIG. 2 (a) is an arrow line diagram of AA in FIG. 1, and FIG. 2 (b) is a diagram showing a state where the thrust race is separated in FIG. 2 (a).
Fig. 3 (a) is an arrow line diagram BB in Fig. 1, and Fig. 3 (b) is a diagram showing a state in which the thrust race is separated in Fig. 3 (a).
4: (a) is a longitudinal cross-sectional view which shows the principal part of the fixed displacement type piston compressor which concerns on 2nd Embodiment, and FIG. 4 (b) is a front view seen from the swash plate side cross section of the cylinder block 11. As shown in FIG.

(1st embodiment)

Hereinafter, the fixed displacement piston compressor (hereinafter, simply referred to as "compressor") according to the first embodiment will be described based on the drawings.

As shown in FIG. 1, the front housing 13 and the rear housing 16 are joined to the edge part of the pair of cylinder blocks 11 and 12 joined together.

The front housing 13 and the rear housing 16 are fastened together by a plurality of bolts 19. The bolt 19 is inserted into the cylinder block 11, 12 and the bolt through holes 11A, 12A, 13A formed in the front housing 13, and the bolt end 19 The male screw portion 19A is screwed into the female screw hole 16A formed in the rear housing 16. In addition, in FIG. 1, only one bolt 19, the bolt through-holes 11A-13A, and the female threaded hole 16A are shown.

The discharge chamber 14 and the suction chamber 15 are formed in the front housing 13, and the discharge chamber 17 and the suction chamber 18 are formed in the rear housing 16. Between the cylinder block 11 and the front housing 13, the valve plate 20, the valve formation plate 22, and the retainer formation plate 24 are interposed. The valve plate 26, the valve forming plate 28, and the retainer forming plate 30 are interposed between the cylinder block 12 and the rear housing 16.

The discharge port 21 is formed in the valve plate 20, and the discharge valve 23 is formed in the valve formation plate 22. The discharge valve 23 opens and closes the discharge port 21. The retainer 25 is formed in the retainer forming plate 24. The retainer 25 defines the maximum opening degree of the discharge valve 23.

The discharge port 27 is formed in the valve plate 26, and the discharge valve 29 is formed in the valve formation plate 28. The discharge valve 29 opens and closes the discharge port 27. A retainer 31 is formed in the retainer forming plate 30. The retainer 31 defines the maximum opening degree of the discharge valve 29.

The cylinder shafts 11 and 12 are supported so that the rotation shaft 32 can rotate.

The rotary shaft 32 is inserted through the shaft hole 34 formed in the cylinder block 11 and the shaft hole 35 formed in the cylinder block 12. The rotating shaft 32 is directly supported by the cylinder blocks 11 and 12 via the shaft holes 35 and 36. A shaft seal member 33 is interposed between the front housing 13 and the rotation shaft 32. The front housing 13, the rotating shaft 32, and the shaft sealing member 33 form a sealed shaft sealing space 48, and the suction chamber 15 and the shaft sealing space 48 are connected to the communication passage 13B. Is communicated by.

The swash plate 36 is fixed to the rotating shaft 32, and the swash plate 36 is integrated with the rotating shaft 32. The swash plate 36 is housed in a swash plate chamber 37 formed between the cylinder blocks 11 and 12.

A thrust bearing 46 is interposed between the swash plate-side end face 11B of the cylinder block 11 and the annular base 36A of the swash plate 36. A thrust bearing 47 is interposed between the swash plate side end surface 12B of the cylinder block 12 and the base 36A of the swash plate 36.

The cylinder block 11 is provided with a refrigerant inlet 38 for communicating an external refrigerant circuit (not shown) with the swash plate chamber 37. The cylinder block 11 is provided with a communication path 39 for communicating the swash plate chamber 37 and the suction chamber 15 of the front housing 13. The cylinder block 12 is provided with a communication path 49 for communicating the swash plate chamber 37 and the suction chamber 18 of the rear housing 16.

The cylinder block 11 is formed such that a plurality of cylinder bores 40 are arranged around the rotation shaft 32. The cylinder block 12 is formed such that a plurality of cylinder bores 50 are arranged around the rotation shaft 32.

The double-headed piston 44 as a piston is accommodated in the cylinder bores 40 and 50 which are paired in the front-rear (front-side housing 13 side and front-side housing 16 side). The double head piston 44 is in cooperation with the rotation of the rotation shaft 32 in addition to partitioning the compression chambers 41 and 51 in the cylinder bores 40 and 50. The shoe 45 which transmits rotation of the swash plate 36 to the double head piston 44 is provided.

A portion of the inner circumferential surface of the shaft hole 34 passing through the rotation shaft 32 is formed as the seal circumferential surface 42, and a portion of the inner circumferential surface of the shaft hole 35 is formed as the seal circumferential surface 52. The diameters of the seal circumferential surfaces 42 and 52 are set smaller than the diameters of the other inner circumferential surfaces in the shaft holes 34 and 35. The rotating shaft 32 is directly supported by the cylinder blocks 11 and 12 via the seal circumferential surfaces 42 and 52.

The supply passage 54 is formed in the rotating shaft 32.

The start end of the supply passage 54 is located at the inner end face of the rotation shaft 32 and is opened to the suction chamber 18 in the rear housing 16. The introduction shafts 55 and 56 are formed in the rotating shaft 32 so that the supply passage 54 may communicate.

The suction block 43 is formed in the cylinder block 11 so that the cylinder bore 40 and the shaft hole 34 may communicate. The inlet 43A of the suction passage 43 is opened on the seal circumferential surface 42. The outlet 55A of the introduction passage 55 is intermittently communicated with the inlet 43A of the suction passage 43 with the rotation of the rotation shaft 32.

The suction block 53 is formed in the cylinder block 12 so that the cylinder bore 50 and the shaft hole 35 may communicate with each other. The inlet 53A of the suction passage 53 is opened on the seal circumferential surface 52. The outlet 56A of the introduction passage 56 is intermittently communicated with the inlet 53A of the suction passage 53 with the rotation of the rotation shaft 32.

The part of the rotating shaft 32 surrounded by the seal circumferential surfaces 42 and 52 becomes a rotary valve integrally formed with the rotating shaft 32.

As shown in FIG. 1, communication holes 57 and 58 are formed in the peripheral surface of the rotating shaft 32. As shown in FIG. The communication holes 57 and 58 overlap with the passages 60 and 61 formed in the base 36A when viewed in the radial direction of the rotation shaft 32. The communication holes 57 and 58 and the passages 60 and 61 communicate the supply passage 54 and the swash plate chamber 37.

The rotary shaft 32 is formed with a through passage 59 in communication with the axial seal space 48.

The thrust bearing 46 is a cylindrical roller 64 interposed between the thrust race 62 on the swash plate 36 side, the thrust race 63 on the cylinder block 11 side, and both thrust races 62 and 63. ). The thrust bearing 47 is a cylindrical roller 67 interposed between the thrust race 65 on the swash plate 36 side, the thrust race 66 on the cylinder block 12 side, and both thrust races 65 and 66. ).

As shown in FIG. 2 (a), the compressor of this embodiment has thrust race anti-rotation mechanisms 70 and 71 for preventing relative rotation of the thrust race 63 and the cylinder block 11 of the thrust bearing 46. Equipped with. Moreover, the compressor is provided with the thrust race anti-rotation mechanism 80, 81 which prevents the relative rotation of the thrust race 66 of the thrust bearing 47, and the cylinder block 12, as shown to FIG. 3 (a). have.

FIG. 2 (a) is an arrow diagram along the line A-A in FIG. 1, and shows a thrust race 63 on the cylinder block 11 side of the thrust bearing 46. FIG. 2 (b) shows a state in which the thrust race 63 is separated from the cylinder block 11 in FIG. 2 (a). In addition, in FIG.2 (a) and FIG.2 (b), illustration of the double head piston 44 is abbreviate | omitted for convenience.

The thrust race anti-rotation mechanisms 70 and 71 which prevent the relative rotation of the thrust race 63 and the cylinder block 11 of the thrust bearing 46 are demonstrated.

As shown to FIG.2 (a) and FIG.2 (b), the thrust race 63 is provided with the two protrusion pieces 72 and 73 which protruded in the radial direction from the peripheral part. One of the protrusion pieces 72 covers the communication path 39 closest to the refrigerant inlet port 38. The other protrusion piece 73 covers the communication path (lowest communication path in FIG. 2) 39 which becomes the lowest in the state in which the compressor was installed in the vehicle.

In the swash plate side end surface 11B in the cylinder block 11, a pair of protrusion bodies 74 and 75 which protrude toward the swash plate 36 side are formed. The protrusion body 74 is formed in the position which opposes the circumferential side end surface of the protrusion piece 72, and the protrusion body 75 is formed in the position which opposes the circumferential direction side end surface of the protrusion piece 73. As shown in FIG.

The protrusions 74 and 75 restrict the movement of the protrusion pieces 72 and 73, and regulate the movement in the circumferential direction of the thrust race 63 about the axis center P. As shown in FIG. In other words, the protrusion pieces 72 and 73 and the protrusions 74 and 75 constitute the thrust race anti-rotation mechanisms 70 and 71.

FIG. 3A is an arrow line B-B in FIG. 1 and shows a thrust race 66 on the cylinder block 12 side of the thrust bearing 47. FIG. 3 (b) shows a state in which the thrust race 66 is separated from the cylinder block 12 in FIG. 3 (a). In addition, in FIG.3 (a) and FIG.3 (b), illustration of the double head piston 44 is abbreviate | omitted for convenience.

The thrust race anti-rotation mechanisms 80 and 81 which prevent the relative rotation of the thrust race 66 and the cylinder block 12 of the thrust bearing 47 are demonstrated. As shown in FIG.3 (a) and FIG.3 (b), the thrust race 66 is provided with two protrusion pieces 82 and 83 which protruded in the radial direction from the peripheral part. One of the protrusion pieces 82 covers the communication path 49 that is closest to the refrigerant inlet port 38. The other protrusion piece 83 covers the communication path (lowest communication path in FIG. 2) 49 which becomes the lowest in the state in which the compressor was installed in the vehicle.

In the swash plate side end surface 12B in the cylinder block 12, a pair of protrusions 84 and 85 which protrude toward the swash plate 36 side are formed. The protrusion body 84 is formed in the position which opposes the circumferential side end surface of the protrusion piece 82, and the protrusion body 85 is formed in the position which opposes the circumferential direction side end surface of the protrusion piece 83. As shown in FIG. The protrusions 84 and 85 restrict the movement of the protrusion pieces 82 and 83, and regulate the movement in the circumferential direction of the thrust race 66 around the axis P. As shown in FIG.

In other words, the protrusion pieces 82 and 83 and the protrusions 84 and 85 constitute the thrust race preventing mechanisms 80 and 81.

Next, the operation of the compressor will be described.

When the rotary shaft 32 rotates in response to the rotational force from the driving source, the rotary motion of the swash plate 36 which rotates integrally with the rotary shaft 32 is transmitted to the double head piston 44 via the shoe 45, thereby providing a double head piston ( 44) The cylinder bores 40 and 50 reciprocate.

The refrigerant of suction pressure in the external refrigerant circuit is introduced into the swash plate chamber 37 through the refrigerant introduction port 38. The refrigerant introduced into the swash plate chamber 37 is introduced into the supply passage 54 through the passage 60 and the communication hole 57 and the passage 61 and the communication hole 58. In addition, a part of the refrigerant introduced into the swash plate chamber 37 is introduced into the suction chambers 15 and 18 through the communication paths 39 and 49.

The refrigerant in the suction chamber 15 is introduced into the supply passage 54 via the communication passage 13B and the shaft seal space 48, and the refrigerant in the suction chamber 18 is introduced directly into the supply passage 54.

When the cylinder bore 40 is in the state of the suction stroke (that is, the stroke in which the double head piston 44 moves from left to right in FIG. 1), the outlet 55A and the inlet 43A of the suction passage 43 are Communicating. When the cylinder bore 40 is in the intake stroke state, the refrigerant in the supply passage 54 of the rotary shaft 32 passes through the introduction passage 55 and the suction passage 43 (the compression chamber of the cylinder bore 40). 41).

When the cylinder bore 40 is in the state of the discharge stroke (that is, the stroke in which the double head piston 44 moves from the right side to the left side in FIG. 1), the outlet 55A and the inlet 43A of the suction passage 43 are formed. Communication is blocked. When the cylinder bore 40 is in the discharge stroke state, the refrigerant in the compression chamber 41 pushes the discharge valve 23 from the discharge port 21 and is discharged to the discharge chamber 14. The refrigerant discharged to the discharge chamber 14 flows out to an external refrigerant circuit (not shown).

When the cylinder bore 50 is in the state of the suction stroke (that is, the stroke in which the double head piston 44 moves from the right side to the left side in FIG. 1), the outlet 56A and the inlet 53A of the suction passage 53 are Communicating. When the cylinder bore 50 is in the suction stroke, the refrigerant in the supply passage 54 of the rotary shaft 32 passes through the introduction passage 56 and the suction passage 53 to the compression chamber of the cylinder bore 50 ( 51).

When the cylinder bore 50 is in the state of the discharge stroke (that is, the stroke in which the double head piston 44 moves from left to right in FIG. 1), the outlet 56A and the inlet 53A of the suction passage 53 are formed. Communication is blocked. When the cylinder bore 50 is in the discharge stroke state, the refrigerant in the compression chamber 51 pushes the discharge valve 29 from the discharge port 27 and is discharged to the discharge chamber 17. The refrigerant discharged to the discharge chamber 17 flows out to the external refrigerant circuit. The coolant flowing out to the external coolant circuit is returned to the swash plate chamber 37 through the coolant introduction port 38.

In the state where the compressor is driven, the swash plate 36 rotates integrally with the rotation shaft 32, but the thrust bearings 46 and 47 are subjected to a load in the thrust direction. At this time, the force which tries to rotate the thrust race 63 in the same direction as the rotation direction of the rotation shaft 32 acts on the thrust race 63 of the thrust bearing 46 in addition to the load of a thrust direction.

Even if the thrust race 63 tries to rotate in the rotational direction of the rotation shaft 32, the protrusion pieces 72 and 73 abut against the protrusions 74 and 75, and the rotation of the thrust race 63 is regulated. do. In short, the relative rotation of the thrust race 63 of the thrust bearing 46 and the cylinder block 11 is prevented by the thrust race anti-rotation mechanisms 70 and 71.

The protrusion piece 72 of the thrust race 63 covers the communication path 39 closest to the refrigerant inlet port 38 so as to be narrowed, and the protrusion piece 73 covers the communication path 39 which becomes the lowest.

The communication path 39 which is closest to the refrigerant introduction port 38 is covered with the protrusion piece portion 72, so that the communication path 39 covered with the protrusion piece portion 72 is limited in function as a passage. The communication path 39 covered by the projection piece 72 is less likely to introduce the refrigerant introduced through the refrigerant inlet 38 into the communication path 39 closest to the refrigerant inlet 38. The balance of the amount of refrigerant with the other communication paths 39 becomes good.

Moreover, since the communication path 39 which becomes the lowest is covered by the protrusion piece 73, the communication path 39 covered by the protrusion piece 73 is limited as a passage. The communication path 39 covered by the protrusion piece 73 is hardly led out to the suction chamber 15 through the communication path 39 in which the lubricating oil stored in the swash plate 37 is the lowest.

On the other hand, in addition to the load in the thrust direction, the force which tries to rotate the thrust race 66 in the same direction as the rotation direction of the rotating shaft 32 also acts on the thrust race 66 of the thrust bearing 47. Even when the thrust race 66 tries to rotate in the same direction as the rotation direction of the rotation shaft 32, the projection piece 82, 83 abuts the projections 84, 85, and the rotation of the thrust race 66 is restricted. In short, the relative rotation of the thrust race 66 and the cylinder block 12 of the thrust bearing 47 is prevented by the thrust race anti-rotation mechanisms 80 and 81. The protrusion piece 82 of the thrust race 66 covers the communication path 49 closest to the refrigerant inlet port 38 so as to be narrowed, and the protrusion piece 83 covers the communication path 49 which becomes the lowest.

The communication path 49 closest to the refrigerant introduction port 38 is covered with the protrusion piece 82, so that the communication path 49 covered with the protrusion piece 82 is limited as a passage. The communication path 49 covered by the projection piece 82 is less likely to be introduced into the communication path 49 that is closest to the refrigerant inlet port 38 by the refrigerant introduced through the refrigerant inlet port 38. The balance of the amount of refrigerant with the other communication paths 49 becomes good.

Moreover, the communication path 49 which becomes the lowest is covered by the protrusion piece 83, and the communication path 49 covered by the protrusion piece 83 is restrict | limited as a path | pass. The communication path 49 covered by the projection piece 83 is hardly led to the suction chamber 18 through the communication path 49 in which the lubricating oil stored in the swash plate chamber 37 becomes the lowest.

According to this embodiment, the following effects are exhibited.

(1) The thrust race 63 (66) on the cylinder block 11 (12) side is provided to the cylinder block 11 (12) by the thrust race anti-rotation mechanisms 70 (80) and 71 (81). Rotation is prevented. In addition, among the plurality of communication paths 39 (49), some of the communication paths 39 (49) are narrowed by the thrust race anti-rotation mechanisms 70 (80, 71). As a result, the relative rotation of the thrust race 63 (66) and the cylinder block 11 (12) can be prevented, and the function of some communication paths 39 (49) can be limited. As a result, abrasion due to the relative rotation of the thrust race and the cylinder block can be prevented, and the performance deterioration as a compressor or a refrigeration cycle can be suppressed by the functional limitation of some communication paths.

(2) Although more refrigerant flows into the communication path 39 (49) closest to the refrigerant inlet port 38 than the communication path 39 (49) separated from the refrigerant inlet port 38, the refrigerant inlet port ( The communication path 39 (49) closest to 38 is narrowed by the thrust race anti-rotation mechanisms 70 (80) and 71 (81). As a result, a good balance between the refrigerant inflow amount into the communication path 39 (49) closest to the refrigerant inlet port 38 and the refrigerant inflow amount into the communication path 39 (49) away from the refrigerant inlet port 38 is achieved. can do. Thereby, the difference of the compression efficiency in each cylinder bore can be made small.

(3) Although lubricating oil is stored in the bottom part of the swash plate chamber 37, the thrust race anti-rotation mechanisms 70 (80) and 71 (81) narrow the lowermost communication path 39 (49) in the vertical direction. Therefore, the passage of the stored lubricating oil by the lowermost communication path 39 (49) is limited. As a result, the lubricating oil can be easily stored in the swash plate chamber 37, and the outflow of the lubricating oil to the external refrigerant circuit can be suppressed. By suppressing the outflow of lubricating oil to an external refrigerant circuit, the fall of the efficiency of the heat exchange in a refrigeration cycle can be suppressed.

(4) Of the plurality of communication paths 39 (49), some of the communication paths 39 (49) are narrowed by the protrusions 72 (82) and 73 (83), and the protrusions 72 (82). ), 73 (83) are regulated by movement of protrusions 74 (84) and 75 (85). Thus, rotation of the thrust race 63 (66) relative to the cylinder block 11 (12) is prevented. Protrusions 72 (82) and 73 (83) are formed in the thrust race (63), and protrusions (74 (84) and 75 (85)) are formed in the cylinder block (11) (12). Relative rotation of the thrust race 63 (66) and the cylinder block 11 (12) can be prevented only by doing so. In addition, the projection piece 72 (82), 73 (83) can narrow a part of communication path 39 (49), and can limit the function as a path | pass.

(2nd embodiment)

Next, the compressor which concerns on 2nd Embodiment is demonstrated. In 2nd Embodiment, the structure of a thrust race anti-rotation mechanism is different from the thrust race anti-rotation mechanism of 1st Embodiment. Therefore, about the same element as 1st Embodiment, the description in 1st Embodiment is used, and the code | symbol is used in common.

The thrust race anti-rotation mechanism 90 according to the second embodiment includes a protrusion piece 92 formed to protrude in the radial direction to the thrust race 91 as shown in Figs. 4 (a) and 4 (b). The pin 94 is press-fitted to the hole 93 formed in the projection piece 92, and the communication path 39 is comprised.

The pin 94 is set to the diameter which can be inserted into the communication path 39 of the cylinder block 11. The thrust race 91 on which the pin 94 is mounted is faced to the swash plate side end surface 11B of the cylinder block 11, and the pin 94 is inserted into the communication path 39 which becomes the lowest.

According to the thrust race anti-rotation mechanism 90, the compressor is driven and inserted into the communication path 39 even if a force that rotates about the shaft center P of the rotation shaft 32 acts on the thrust race 91. The pin 94 regulates the movement of the protrusion piece 92. Thereby, rotation of the thrust race 91 centering on the shaft center P is prevented. Moreover, by inserting the pin 94 into the communication path 39, the communication path 39 is narrowed and the function as a path | pass is restrict | limited.

In the second embodiment, the pin 94 is inserted into the lowermost communication path 39, but the pin 94 may be inserted into the communication path 39 closest to the refrigerant inlet 38. In addition, another protrusion piece may be formed, a hole may be formed in this protrusion piece to fix the pin 94, and the pin 94 may be inserted into both communication paths 39.

In addition, a thrust race anti-rotation mechanism having a thrust race with a pin may be applied to the thrust race of the thrust bearing of the cylinder block 12 side.

According to the second embodiment, it is not necessary to form the projection on the swash plate side end surface 11B (12B) of the cylinder block 11 (12), and the communication path 39 (49) into which the pin 94 is inserted. You can freely choose)). Therefore, even when the installation posture of the compressor is changed around the shaft center P of the rotating shaft 32, and the communication path 39 (49) which becomes the lowest, for example, changes according to the vehicle model, the lowest position irrespective of the vehicle model. The communication path 39 (49) of can be narrowed.

In addition, the compressor which concerns on said embodiment shows one Embodiment of this invention, This invention is not limited to said embodiment, Various changes are possible within the scope of the invention as follows.

In the first embodiment described above, the thrust race anti-rotation mechanism is designed to narrow the communication path closest to the refrigerant inlet and the communication path that is the lowest, but may be a thrust race that narrows only one communication path. In addition, although the example in which the coolant inlet is formed in the upper portion of the cylinder block has been described, the coolant inlet is not limited to the upper portion, but may be formed in the side portion or the like except for the bottom portion. In addition, when narrowing several communication paths, you may combine the thrust race anti-rotation mechanism of 1st, 2nd embodiment.

In the first embodiment described above, the protrusion piece of the thrust race is made to narrow the communication path. However, when the communication piece is blocked by the protrusion piece, the refrigerant does not pass through the communication path. . In addition, a gap is formed between the protrusion piece and the communication path, and the distance of the gap is changed according to the direction of the load in the thrust direction and the number is small, and the throttle of the communication path by the protrusion part may function as a substantially variable throttle. .

○ In the second embodiment described above, although the thrust race and the pin are used as separate members, the thrust race and the pin may be formed as a thrust race in which the thrust race and the pin are integrally formed. In addition, the pin is inserted into the communication path, but the cross-sectional shape of the pin is not particularly limited, and the cross-sectional shape may be a cross-sectional shape in which the pin can be inserted into the communication path and functions as a throttle. The cross-sectional shape may be, for example, a circle, a polygon, a semicircle, or the like.

In the above first and second embodiments, the fixed displacement swash plate type compressor having a rotating shaft having the configuration of a rotary valve is provided, but the present invention is not intended to be limited to this type of compressor. For example, the fixed displacement swash plate type compressor which provided the suction port in the valve plate, and formed the suction valve which opens and closes a suction port may be sufficient. In this case, the communication path for communicating the suction chamber from the swash plate chamber serves as a main passage for passing the refrigerant before compression.

11, 12: cylinder block
13: front housing
14, 17: discharge chamber
15, 18: suction chamber
16: rear housing
32: axis of rotation
36: swash plate
37: judge
38: refrigerant inlet
39, 49: communication path
40, 50: cylinder bore
41, 51: compression chamber
43, 53: suction passage
44: double head piston
46, 47: thrust bearing
54: supply passage
55, 56: introduction passage
62, 63, 65, 66, 91: thrust race
64, 67: cylindrical roller
70, 71, 80, 81, 90: thrust race anti-rotation mechanism
72, 73, 82, 83, 92: stone part
74, 75, 84, 85: protrusions
93: hole
94: pin
P: axis

Claims (4)

A cylinder block supporting a rotating shaft and having a plurality of cylinder bores arranged around the rotating shaft;
A swash plate integrated with the rotating shaft,
A piston accommodated in the plurality of cylinder bores and interlocked with the rotation of the rotary shaft;
A swash plate chamber in which the swash plate is accommodated and a refrigerant of suction pressure is introduced;
A housing joined to an end of the cylinder block and having a suction chamber and a discharge chamber;
A plurality of communication paths for communicating the swash plate chamber and the suction chamber,
A thrust bearing disposed between the cylinder block and the swash plate and configured to provide a bearing in the thrust direction of the swash plate;
A fixed displacement piston type compressor having a thrust race anti-rotation mechanism for preventing rotation of the cylinder block side thrust race with respect to the cylinder block provided in the thrust bearing.
The thrust race anti-rotation mechanism,
A fixed displacement piston type compressor comprising: narrowing or blocking a part of the communication paths among the plurality of communication paths. The method of claim 1,
In the state where the compressor is installed in the vehicle,
The thrust race anti-rotation mechanism is a fixed displacement piston compressor, characterized in that for narrowing or blocking the communication path that is the lowest in the vertical direction of the plurality of communication paths. The method of claim 1,
A refrigerant inlet port for introducing a refrigerant of suction pressure into the swash plate chamber,
The thrust race anti-rotation mechanism is one of the plurality of communication paths,
Fixed piston type compressor, characterized in that for narrowing or blocking the communication path closest to the refrigerant inlet. The method according to any one of claims 1 to 3,
The thrust race anti-rotation mechanism,
A protrusion piece formed by protruding from the periphery of the thrust race;
It is formed in the cylinder block, and provided with a projection body for restricting the movement of the protrusion piece,
A fixed displacement piston type compressor, wherein the protrusion piece narrows or blocks part of the communication path.

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