JP6685809B2 - Condenser - Google Patents

Description

  Embodiments of the present invention relate to a condenser.

  Generally, a condenser that condenses exhaust steam discharged from a steam turbine to generate condensed water is known. For example, the condenser 100 includes a rectangular casing 101 as shown in FIG. 7, and a steam turbine 102 is installed above the casing 101. A tube group 103 including a large number of heat transfer tubes is provided below the housing 101. In FIG. 7, a tube group 103 divided into four is provided in the housing 101. Each heat transfer tube is supported by a tube plate 104 and extends horizontally in a direction along a pair of side walls 105 of the housing 101 that face each other. A cooling medium (for example, seawater or cooling water supplied from a cooling tower) flows through each heat transfer tube, and the exhaust steam discharged from the steam turbine 102 is cooled by exchanging heat with the cooling medium and discharged. The steam contained in the steam is deprived of latent heat and condensed. The condensed condensed water is collected as condensed water in the hot well 106 (condensate reservoir) provided at the bottom of the housing 101. Condensation increases the concentration of the non-condensable gas contained in the exhaust steam, and the exhaust steam is extracted from the gas extraction port provided in the tube group and discharged to the outside of the condenser 100.

JP-A-8-226776 JP, 2003-302175, A US Pat. No. 5,649,590

  By the way, the flow velocity of the exhaust steam discharged from the steam turbine 102 and flowing into the casing 101 of the condenser 100 becomes large on the side wall 105 side of the casing 101 described above, as shown in FIG. 7. On the other hand, a large gap is formed between the tube group 103 and the side wall 105 to serve as a flow path for the exhaust steam. This facilitates the flow of the exhaust steam having a large flow velocity to flow through the large gap. For this reason, it is difficult for the exhaust steam flowing down in the casing 101 to flow into the tube group 103, and it is difficult to improve the condensation performance of the condenser 100.

  The present invention has been made in consideration of such a point, and an object thereof is to provide a condenser that can improve the condensation performance.

  The condenser according to the embodiment is a condenser that condenses exhaust steam discharged from the steam turbine with a cooling medium. The condenser is provided with a housing having a pair of side walls facing each other, a pair of steam inlets provided in an upper portion of the housing, and a pair of steam inlets into which the exhaust steam flows, and below the steam inlet. And a pair of tube group constructs. One steam inlet extends from one side wall to the inside of the housing, and the other steam inlet extends from the other side wall to the inside of the housing. One tube group structure is arranged on one side wall side, and the other tube group structure is arranged on the other side wall side. The tube group constituent member has an upper tube group and a lower tube group arranged below the upper tube group, respectively. The upper tube group and the lower tube group each have a plurality of heat transfer tubes that extend in the direction along the side wall and through which the cooling medium flows. The gap between the upper tube group and the side wall corresponding to the upper tube group is smaller than the gap between the lower tube group arranged below the upper tube group and the side wall.

  According to the present invention, the condensation performance can be improved.

FIG. 1 is a side outline view showing a condenser according to a first embodiment of the present invention. FIG. 2 is a front view showing the internal configuration of the condenser shown in FIG. FIG. 3 is a diagram for explaining the arrangement pitch of the heat transfer tubes in the tube group constituent body shown in FIG. 2. FIG. 4 is a front view showing the internal configuration of the condenser according to the second embodiment of the present invention. FIG. 5: is a front view which shows the internal structure of the condenser in the 3rd Embodiment of this invention. FIG. 6 is a front view showing the internal configuration of the condenser according to the fourth embodiment of the present invention. FIG. 7 is a front view showing an internal configuration of a general condenser.

  Hereinafter, a condenser according to an embodiment of the present invention will be described with reference to the drawings.

(First embodiment)
First, the condenser according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 3. Here, the condenser is for condensing the exhaust steam discharged from the steam turbine by the cooling medium. Although not shown, the condenser may be connected in parallel to form a composite condenser. It should be noted that, as used in the present specification, terms such as “horizontal” and “vertical” that specify the degree of shape, geometric condition, and the like are not restricted to a strict meaning, and have similar functions. It should be interpreted including the range of what can be expected.

  As shown in FIGS. 1 and 2, the condenser 10 is provided in a housing 11, a pair of steam inlets 12A and 12B into which exhaust steam discharged from the steam turbine 1 flows, and the housing 11. , And a pair of tube group constituent bodies 20A, 20B each having a plurality of heat transfer tubes 23. Among them, the heat transfer pipe 23 is provided with a cooling medium (hereinafter, referred to as cooling water as an example of the cooling medium) for cooling the exhaust steam and condensing the exhaust steam (more specifically, the steam included in the exhaust steam). It is designed to flow.

  As shown in FIG. 1, when the housing 11 is viewed from the side, water chambers 13A and 13B are provided on both sides of the housing 11. One of the water chambers 13A is provided with a cooling water inlet 14 through which cooling water flows from the outside, and the other water chamber 13B is provided with a cooling water outlet 15 for discharging the cooling water to the outside.

  As shown in FIG. 2, the housing 11 has a pair of side walls 16A and 16B facing each other. In FIG. 1, one side wall 16A is shown, and the other side wall 16B exists behind the one side wall 16A.

  As shown in FIG. 2, the pair of steam inlets 12 </ b> A and 12 </ b> B are provided in the upper part of the housing 11. One steam inlet 12A of the pair of steam inlets 12A and 12B extends from one side wall 16A of the pair of side walls 16A and 16B of the housing 11 to the inside of the housing 11 and the other steam inlet 12A. 12B extends inward from the other side wall 16B. More specifically, in FIG. 2, the left steam inlet 12A extends from the left side wall 16A to the right side, and the right steam inlet 12B extends from the right side wall 16B to the left side. In the present embodiment, the left-right direction in FIG. 2, in other words, the lateral direction when the condenser 10 is viewed from the front is the width direction. The steam inlets 12A and 12B also extend in a direction perpendicular to the plane of FIG.

  Here, the steam inlets 12 </ b> A and 12 </ b> B mean openings through which exhaust steam discharged from the steam turbine 1 passes when flowing into the housing 11 of the condenser 10. For example, as shown in FIG. 2, the tip of a diffuser 4 that guides the flow of exhaust steam that has passed through the rotor blades 3 in the final paragraph provided in the turbine casing 2 of the steam turbine 1 and the housing of the condenser 10. It may be an opening formed between the side walls 16A and 16B of the eleventh. The side walls 16A and 16B of the turbine casing 2 are formed so as to be continuous from the side walls 16A and 16B of the casing 11 of the condenser 10. Further, for example, although not shown, in the case where an upper wall located below the steam turbine 1 is provided in the upper part of the casing 11 of the condenser 10, between the upper wall and each of the side walls 16A and 16B. It is also possible to provide an opening and use this opening as the steam inlets 12A and 12B.

  Next, the tube group constituent bodies 20A and 20B will be described.

  The pair of tube group constituent bodies 20A and 20B are provided below the steam inlets 12A and 12B. One of the pair of tube group constituents 20A, 20B is arranged on the side of one side wall 16A of the pair of side walls 16A, 16B of the housing 11 and the other tube group constituent body 20A. 20B is arranged on the side of the other side wall 16B. More specifically, in FIG. 2, the left tube group structure 20A is arranged on the left side wall 16A side, and the right tube group structure 20B is arranged on the right side wall 16B side. In other words, in the width direction of the housing 11, the pair of tube group constituent bodies 20A, 20B are arranged between the pair of side walls 16A, 16B and are arranged in parallel in the horizontal direction.

  Each of the tube group constituent bodies 20A, 20B has an upper tube group 21A, 21B and a lower tube group 22A, 22B arranged below the upper tube group 21A, 21B, respectively. The upper tube groups 21A, 21B and the lower tube groups 22A, 22B are formed in a rectangular shape when viewed in a cross section perpendicular to the longitudinal direction of the heat transfer tube 23 (when viewed as in FIG. 2). The upper tube groups 21A and 21B and the corresponding lower tube groups 22A and 22B are separated from each other. Each upper tube group 21A, 21B and each lower tube group 22A, 22B has a plurality of heat transfer tubes 23 described above, respectively. Each heat transfer tube 23 extends horizontally (in a direction perpendicular to the plane of FIG. 2) along the side walls 16A and 16B of the housing 11. More specifically, a turbine rotor (not shown) of the steam turbine 1 extends in a horizontal direction which is a direction vertical to the side walls 16A and 16B of the housing 11, and each heat transfer tube 23 is viewed from above. In this case, it extends in a direction orthogonal to the longitudinal direction of the turbine rotor. Further, each heat transfer tube 23 penetrates a tube plate (not shown) extending in the vertical direction and is supported by the tube plate. The tube plates are provided at both ends in the longitudinal direction (horizontal direction in FIG. 1) of the heat transfer tube 23, and partition the water chambers 13A and 13B described above from the space inside the housing 11.

  A gap W1 is formed between the upper tube groups 21A, 21B of the respective tube group constituents 20A, 20B and the side walls 16A, 16B corresponding to the upper tube groups 21A, 21B. Between the lower tube groups 22A and 22B corresponding to the groups 21A and 21B (lower tube groups 22A and 22B arranged below the upper tube groups 21A and 21B) and the side walls 16A and 16B, a gap indicated by W2. Are formed. The gap W1 is smaller than the gap W2. More specifically, in FIG. 2, the gap W1 between the left upper tube group 21A and the left side wall 16A is smaller than the gap W2 between the left lower tube group 22A and the left side wall 16A. The gap W1 between the right upper tube group 21B and the right side wall 16B is smaller than the gap W2 between the right lower tube group 22B and the right side wall 16B. Here, the gap W1 corresponds to the widthwise dimension of the space (flow path of exhaust steam) formed between the upper pipe groups 21A and 21B and the corresponding side walls 16A and 16B, and the gap W2 is the lower pipe. It corresponds to the widthwise dimension of the space (flow path of exhaust vapor) formed between the groups 22A and 22B and the corresponding side walls 16A and 16B. The left-side gap W1 and the right-side gap W1 are not limited to be the same, and the left-side gap W2 and the right-side gap W2 are not necessarily the same.

  Further, the gap W1 between the upper tube groups 21A and 21B of the respective tube group constituents 20A and 20B and the side walls 16A and 16B corresponding to the upper tube groups 21A and 21B is equal to the steam flow extending from the side walls 16A and 16B. It is smaller than the width W3 of the inlets 12A and 12B. More specifically, in FIG. 2, the gap W1 between the left upper tube group 21A and the left side wall 16A is smaller than the width W3 of the left steam inlet 12A, and the right upper tube group is A gap W1 between the right side wall 16B and the side wall 21B is smaller than a width W3 of the right steam inlet 12B. The left side width W3 and the right side width W3 are not limited to be the same.

  As shown in FIG. 2, each of the tube group constituent bodies 20A and 20B has a plurality of vertical channels 24 (mountain channels). The vertical flow path 24, when viewed in a cross section perpendicular to the longitudinal direction of the heat transfer tube 23, is the tube group constituent body of the upper edges (upper part of the outer edges) of the tube group constituent bodies 20A and 20B. It extends downward from the portion of the side wall 16A, 16B corresponding to the tube group constructing body 20A, 20B with respect to the center of 20A, 20B. In the present embodiment, the vertical flow path 24 is provided in each of the upper tube groups 21A and 21B. More specifically, in FIG. 2, the vertical channel 24 provided in the left upper tube group 21A extends from the left part of the upper edge of the left upper tube group 21A, and the right upper part The vertical channel 24 provided in the tube group 21B extends from the right side portion of the upper edge of the right upper tube group 21B.

  In addition, each of the tube group constituent bodies 20A and 20B further includes a plurality of radial flow paths 25 (flare flow paths). The radial flow path 25 extends from the outer edge of the tube group constituent bodies 20A, 20B toward the center of the tube group constituent bodies 20A, 20B when viewed in a cross section perpendicular to the longitudinal direction of the heat transfer tube 23. Has been formed. In the present embodiment, the radial flow passage 25 is located on the outer edge of the tube group constructing bodies 20A, 20B on the side of the other tube group constructing bodies 20A, 20B with respect to the center of the tube group constructing bodies 20A, 20B. From the portion and the portion of the lower tube groups 22A and 22B that is on the side of the side walls 16A and 16B corresponding to the tube group constituents 20A and 20B with respect to the center, the tube group constituents 20A and 20B It extends toward the center. In the present embodiment, the radial flow path 25 is provided in each of the upper tube groups 21A and 21B and each of the lower tube groups 22A and 22B. More specifically, in FIG. 2, the radial flow path 25 provided in the left upper tube group 21A extends from the right side portion of the upper edges of the left upper tube group 21A and the right edge. ing. The radial flow path 25 provided in the right upper tube group 21B extends from the left side portion of the upper edge of the right upper tube group 21B and the left edge. Further, the radial flow passage 25 provided in the left lower tube group 22A extends from the right side edge, the lower edge, and the left side edge of the left lower tube group 22A. The radial flow path 25 provided in the lower tube group 22B on the right side extends from the left edge, the lower edge, and the right edge of the lower tube group 22B on the right side.

  The exhaust steam in which the concentration of the non-condensable gas has been increased by condensing the steam contained in the exhaust steam in each of the tube group constituent bodies 20A and 20B is exhausted to the outside of the condenser 10. That is, the condenser 10 is provided with the gas extraction duct 30 for extracting the exhaust vapor in which the concentration of the non-condensed gas is increased, and the gas extraction port 31 of the gas extraction duct 30 has each upper tube group 21A, 21B and each of the lower tube groups 22A and 22B. Of these, the gas extraction ports 31 provided in the upper tube groups 21A, 21B are preferably arranged near the center of the upper tube groups 21A, 21B or below the center in the cross section in FIG. The gas extraction ports 31 provided in the lower tube groups 22A and 22B are preferably arranged near the center of the lower tube groups 22A and 22B or above the center thereof. A gas extraction device (not shown) (for example, a vacuum pump) is connected to the gas extraction duct 30. With this gas extraction device, the exhaust vapor in which the concentration of the non-condensable gas in the tube group constituent bodies 20A, 20B is increased is extracted through the gas extraction duct 30 and discharged to the outside of the condenser 10. Has become.

  As shown in FIG. 3, it is preferable that the arrangement pitch of the heat transfer tubes 23 forming the respective tube group constituent bodies 20A and 20B be different between the outer edge side and the center side of the tube group constituent bodies 20A and 20B. is there. In the present embodiment, the arrangement pitch of the heat transfer tubes 23 adjacent to each other on the outer edge side of each tube group constituent body 20A, 20B is such that the heat transfer tubes 23 adjacent to each other on the center side of the tube group constituent body 20A, 20B. It is larger than the array pitch of. For example, as shown in FIG. 3, the arrangement pitch of the heat transfer tubes 23 in the horizontal direction (x direction) is set to x1, x2, x3 (x1 <x2 <x3 from the center of the tube group constituent bodies 20A, 20B toward the outer edge. ), And may be gradually increased. In this case, the arrangement pitch of the heat transfer tubes 23 is x1 on the center side of the tube group constituent bodies 20A and 20B, and the arrangement pitch of the heat transfer tubes 23 is on the left side edge and the right side edge side of the tube group constituent bodies 20A and 20B. x3. Further, as shown in FIG. 3, the arrangement pitch of the heat transfer tubes 23 in the up-down direction (y direction) is set to y1, y2, y3 (y1 <y2 <y3 from the center of the tube group constituent bodies 20A, 20B toward the outer edge). ), And may be gradually increased. In this case, the arrangement pitch of the heat transfer tubes 23 is y1 on the center side of the tube group constituting bodies 20A, 20B, and the arrangement pitch of the heat transfer tubes 23 is on the upper edge and the lower edge side of the tube group constituting bodies 20A, 20B. It becomes y3. That is, the origin O shown in FIG. 3 corresponds to the center of the tube group constituting bodies 20A, 20B in a cross section perpendicular to the longitudinal direction of the heat transfer tube 23, and the heat conducting tube 23 shown in FIG. 3 has the tube group constituting bodies 20A, 20B. Corresponds to a region on the upper right side in the case of being divided into four vertically and horizontally, and the other region has an array of heat transfer tubes 23 symmetrical to this.

  As shown in FIG. 2, between the upper tube groups 21A and 21B and the lower tube groups 22A and 22B corresponding to the upper tube groups 21A and 21B, the upper tube groups 21A and 21B and the lower tube group 22A are provided. , 22B is provided with an imidation prevention plate 33 that prevents exhaust steam flowing in the central flow path 32 from flowing toward the gas extraction port 31. The imination prevention plates 33 extend in the direction along the heat transfer tubes 23, and two are provided in each of the tube group constituent bodies 20A and 20B. The two pairs of imidation prevention plates 33 are arranged on both sides of the gas extraction port 31 in the width direction of the housing 11.

  A hot well 34 is provided at the bottom of the housing 11. The hot well 34 is provided below the lower tube groups 22A and 22B of the tube group constituents 20A and 20B, and stores condensed water (condensate) condensed in the tube group constituents 20A and 20B. The condensed water stored in the hot well 34 is supplied to a feed water heater 35 described later.

  A feed water heater 35 is provided between the steam inlets 12A, 12B and the tube group constituent bodies 20A, 20B. The feed water heater 35 heats the condensate supplied from the hot well 34. More specifically, the feed water heater 35 has a cylindrical feed water heating pipe 36 through which the condensate flows, and the feed water heating pipe 36 extends in the horizontal direction along the heat transfer pipe 23. It extends (in the direction perpendicular to the paper surface in FIG. 2). When the condensate flows through the feed water heating pipe 36, the condensate is heated by exchanging heat with the exhaust steam flowing from the steam inlets 12A and 12B. In this way, by providing the feed water heater 35 in the housing 11 of the condenser 10, space saving of the power generation plant and simplification of the structure are achieved.

  Next, the operation of the present embodiment having such a configuration will be described.

  The exhaust steam discharged from the steam turbine 1 flows into the housing 11 through steam inlets 12A and 12B provided in the upper part of the housing 11 of the condenser 10. The exhaust steam that has flowed into the housing 11 flows down inside the housing 11 and flows around the tube group constituent bodies 20A and 20B. Around the tube group constituents 20A, 20B, the exhaust steam mainly flows down through the central flow path 32 formed between the two tube group constituents 20A, 20B, and below the lower tube groups 22A, 22B. In the space, the current flows around the lower tube groups 22A and 22B. During this period, the discharged steam gradually flows into the pipe group constituent bodies 20A and 20B while flowing around the pipe group constituent bodies 20A and 20B.

  When the exhaust steam flows into the tube group constituent bodies 20A and 20B, it flows in from the outer edges of the upper tube groups 21A and 21B and into the inside from the outer edges of the lower tube groups 22A and 22B. In the present embodiment, the arrangement pitch of the heat transfer tubes 23 on the outer edge side of the tube group constituent bodies 20A, 20B is larger than the arrangement pitch of the heat transfer tubes 23 on the center side of the tube group constituent bodies 20A, 20B. There is. As a result, the exhaust steam can smoothly flow into the gas extraction ports 31 from the outer edges of the upper tube groups 21A and 21B and the outer edges of the lower tube groups 22A and 22B. Therefore, it is possible to suppress the occurrence of pressure loss in the inflowing exhaust steam, and to reduce the flow velocity of the inflowing exhaust steam.

  The exhaust vapor flowing into the upper tube groups 21A and 21B and the lower tube groups 22A and 22B flows around the heat transfer tubes 23. On the other hand, the cooling water flows from the cooling water inlet 14 toward the cooling water outlet 15 via the one water chamber 13A, the heat transfer pipe 23, and the other water chamber 13B. As a result, the exhaust steam exchanges heat with the cooling water and is cooled. Therefore, the steam contained in the exhaust steam is deprived of latent heat and condensed, and condensed water is generated. The generated condensed water drops and is stored as condensate in the hot well 34 provided at the bottom of the housing 11. The exhaust vapors in the upper pipe groups 21A, 21B and the lower pipe groups 22A, 22B are further condensed while flowing toward the gas extraction port 31, and the concentration of the non-condensed gas is increased. The exhaust vapor with the concentration of the non-condensed gas increased is extracted at the gas extraction port 31 and discharged to the outside of the condenser 10 through the gas extraction duct 30.

  By the way, the flow velocity of the exhaust steam flowing into the casing 11 of the condenser 10 is high in the vicinity of the side walls 16A and 16B of the casing 11, as shown in FIG. As a result, most of the exhaust steam flowing down inside the housing 11 flows down along the side walls 16A and 16B at a high flow velocity.

  However, in the present embodiment, the gap W1 between the upper tube group 21A, 21B and the side wall 16A, 16B is smaller than the gap W2 between the corresponding lower tube group 22A, 22B and the side wall 16A, 16B. ing. As a result, the gap W1 between the upper tube groups 21A, 21B and the side walls 16A, 16B becomes smaller, and the exhaust steam flowing down in the housing 11 near the side walls 16A, 16B becomes the upper tube groups 21A, 21B. Further flow down through the gap W1 between the side walls 16A and 16B is suppressed. In addition, the gap W1 between the upper tube group 21A, 21B and the side wall 16A, 16B is smaller than the width W3 of the corresponding steam inlet 12A, 12B. As a result, the exhaust steam that has flowed in from the steam inlets 12A and 12B is suppressed from flowing straight down toward the gap W1 between the upper tube groups 21A and 21B and the side walls 16A and 16B. In this way, the exhaust steam flowing down near the side walls 16A and 16B is directed to the upper edges of the upper tube groups 21A and 21B.

  In the present embodiment, the vertical flow path 24 is provided in a portion on the side wall 16A, 16B side of the upper edges of the upper tube groups 21A, 21B. As a result, the exhaust steam having a large flow velocity flowing near the side walls 16A and 16B can smoothly flow into the upper tube groups 21A and 21B through the vertical passages 24. Therefore, it is possible to suppress pressure loss when flowing into the upper tube groups 21A and 21B, and to suppress retention of the flow of exhaust vapor in the upper tube groups 21A and 21B. In this case, the exhaust steam that has flowed into the upper tube groups 21A and 21B can be smoothly flowed toward the gas extraction port 31 provided in the upper tube groups 21A and 21B, and the concentration of the non-condensed gas is increased. The discharged steam can be suppressed from staying in an undesired place in the upper tube groups 21A and 21B.

  Here, if a pressure loss occurs, there is a problem that the partial pressure of the steam contained in the exhaust steam decreases. There is also a problem that when the concentration of the non-condensable gas is increased, the partial pressure of the non-condensed gas is increased and the partial pressure of water vapor is decreased. When the partial pressure of steam decreases, the saturation temperature of the steam, which is the temperature at which the steam condenses, decreases, the difference between the temperature of the steam and the temperature of the cooling water decreases, and the condensation performance may decrease. However, according to the present embodiment, it is possible to suppress the occurrence of pressure loss as described above, and it is possible to suppress the retention of the exhaust steam in which the concentration of the non-condensed gas is increased, so that the decrease in the partial pressure of the steam is suppressed. it can. Therefore, the condensation performance can be improved.

  Further, in the portion of the upper pipe group 21A, 21B and the lower pipe group 22A, 22B in which the radial flow path 25 is provided, the flow of the exhaust steam is the upper pipe group 21A, 21B and the lower pipe group 22A, 22B. It will flow around the circumference of. As a result, the exhaust steam can smoothly flow into the upper tube groups 21A and 21B and the lower tube groups 22A and 22B through the radial flow path 25. Therefore, it is possible to suppress pressure loss when flowing into the upper pipe groups 21A and 21B and the lower pipe groups 22A and 22B, and to discharge the upper pipe groups 21A and 21B and the lower pipe groups 22A and 22B. It is possible to prevent the steam flow from staying. In this case, the exhaust steam flowing into the upper pipe groups 21A and 21B and the lower pipe groups 22A and 22B is directed to the gas extraction port 31 provided in the upper pipe groups 21A and 21B and the lower pipe groups 22A and 22B. It is possible to smoothly flow the exhaust vapor having an increased concentration of the non-condensed gas and to prevent the exhaust vapor from accumulating at undesired locations in the upper tube groups 21A and 21B and the lower tube groups 22A and 22B.

  In addition, the above-mentioned initialization prevention plate 33 is provided between the upper tube groups 21A and 21B and the corresponding lower tube groups 22A and 22B. As a result, it is possible to prevent the exhaust steam heading for the gas extraction port 31 from flowing through the gap between the upper tube group 21A, 21B and the lower tube group 22A, 22B. For this reason, it is possible to prevent the exhaust steam, which is insufficiently condensed in the steam, from going to the gas extraction port 31, and to improve the condensation performance.

  Thus, according to the present embodiment, the gap W1 between the upper tube groups 21A and 21B and the side walls 16A and 16B corresponding to the upper tube groups 21A and 21B corresponds to the upper tube groups 21A and 21B. It is smaller than the gap W2 between the lower tube group 22A, 22B and the side wall 16A, 16B. As a result, the exhaust steam flowing down in the housing 11 can be suppressed from flowing down through the gap W1 between the upper tube groups 21A, 21B and the side walls 16A, 16B. In particular, when the flow velocity is large near the side walls 16A, 16B of the housing 11, the flow rate of the exhaust steam flowing down through the gap W1 between the upper tube groups 21A, 21B and the side walls 16A, 16B is effective. Can be reduced to Therefore, the exhaust steam flowing down in the housing 11 can smoothly flow into the upper tube groups 21A and 21B, and the condensation performance of the condenser 10 can be improved.

  Further, according to the present embodiment, the gap W1 between the upper tube groups 21A and 21B of the respective tube group constituent bodies 20A and 20B and the side walls 16A and 16B corresponding to the upper tube groups 21A and 21B is It is smaller than the width W3 of the steam inlets 12A, 12B extending from the side walls 16A, 16B. As a result, the exhaust steam that has flowed in from the steam inlets 12A and 12B can be suppressed from flowing straight down toward the gap W1 between the upper tube groups 21A and 21B and the side walls 16A and 16B. Therefore, the discharged steam can be further suppressed from flowing down through the gap W1 between the upper tube group 21A, 21B and the side walls 16A, 16B, and the condensing performance of the condenser 10 can be further improved. it can.

  Further, according to the present embodiment, the tube bundle constituents 20A, 20B are arranged so that the vertical flow extending downward from the corresponding side wall 16A, 16B side portion of the upper edges of the tube bundle constituents 20A, 20B. It has a passage 24. As a result, the exhaust steam having a large flow velocity that flows down near the side walls 16A and 16B can smoothly flow into the upper tube groups 21A and 21B by the vertical flow path 24. Therefore, the condensation performance of the condenser 10 can be further improved. Further, by causing the exhaust steam to flow into the vertical flow path 24, it is possible to prevent the heat transfer tubes 23 of the upper tube groups 21A and 21B from vibrating due to the flow rate of the exhaust steam, and the heat transfer tube 23 may be damaged. The reliability can be improved by reducing the amount.

  Further, according to the present embodiment, the tube group constituting bodies 20A, 20B have radial flow paths 25 extending from the outer edges of the tube group constituting bodies 20A, 20B toward the centers of the tube group constituting bodies 20A, 20B. is doing. As a result, the exhaust steam flowing around the upper tube groups 21A, 21B and the lower tube groups 22A, 22B is guided by the radial flow path 25 into the upper tube groups 21A, 21B and the lower tube groups 22A, 22B. It can be smoothly flowed in. Therefore, the condensation performance of the condenser 10 can be further improved.

  Further, according to the present embodiment, the arrangement pitch of the heat transfer tubes 23 adjacent to each other on the outer edge sides of the tube group constituent bodies 20A and 20B is such that the heat transfer tubes adjacent to each other on the center side of the tube group constituent bodies 20A and 20B. It is larger than the arrangement pitch of 23. As a result, the flow velocity of the exhaust steam flowing around the heat transfer tubes 23 on the outer edge side of the tube group constituent bodies 20A, 20B can be reduced, and the pressure loss can be reduced. Further, it is possible to suppress the vibration of the heat transfer tube 23 due to the flow velocity of the exhaust steam, reduce the possibility of damage of the heat transfer tube 23, and improve the reliability.

(Second embodiment)
Next, a condenser according to the second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment shown in FIG. 4, a pair of protective members is provided between the steam inlet and the pipe group structure, and the width of the protective member is larger than the width of the steam inlet. The point is mainly different, and the other structure is substantially the same as that of the first embodiment shown in FIGS. 1 to 3. In FIG. 4, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

  In the present embodiment, as shown in FIG. 4, a pair of protection members 40A, 40B are provided between the steam inlets 12A, 12B and the upper tube groups 21A, 21B of the tube group constituent bodies 20A, 20B. ing. The protection members 40A, 40B receive the exhaust steam flowing in and flowing down from the steam inlets 12A, 12B, and direct the exhaust steam to the central flow path 32 provided between the two tube group constituent bodies 20A, 20B. invite. One protection member 40A of the pair of protection members 40A and 40B is arranged above the upper tube group 21A of the one tube group constituent body 20A, and the other protection member 40B is the other tube group constituent body. It is arranged above the upper tube group 21B of 20B. Each protection member 40A, 40B extends from the corresponding side wall 16A, 16B toward the inside of the housing 11. More specifically, in FIG. 4, the left protection member 40A is arranged above the left upper tube group 21A and extends horizontally from the left side wall 16A toward the right side. On the other hand, the right protection member 40B is disposed above the right upper tube group 21B and extends horizontally from the right side wall 16B toward the left side. In addition, it is preferable that each protection member 40A, 40B is arranged closer to the corresponding upper tube group 21A, 21B than the corresponding steam inlet 12A, 12B, and in particular, as shown in FIG. It is preferable to be arranged near the upper tube groups 21A and 21B.

  The configuration of the protection members 40A and 40B is not particularly limited, but for example, a plurality of protection tubes 41 extending horizontally in a direction along the heat transfer tube 23 (in a direction perpendicular to the paper surface of FIG. 4) are horizontal. They may be arranged side by side in the direction. Other than this, for example, round bars or square members may be arranged in parallel, or may be continuously configured by a plate-shaped member. Moreover, the protection members 40A and 40B may be configured to pass a part of the exhaust steam. For example, when the protection members 40A and 40B are composed of the protection tube 41, a plurality of protection tubes 41 may be arranged side by side, and when they are composed of plate-shaped members. The plate-shaped member may be provided with a hole through which a part of the exhaust steam passes. When a part of the exhaust steam is passed in this way, the force that the protective members 40A, 40B receive from the exhaust steam can be reduced, and the possibility of damage to the protective members 40A, 40B is reduced and reliability is improved. Can be achieved.

  As shown in FIG. 4, the width W4 of the protection members 40A and 40B is larger than the width W3 of the steam inlets 12A and 12B corresponding to the protection members 40A and 40B. More specifically, in FIG. 4, the width W4 of the left protection member 40A is larger than the width W3 of the left steam inlet 12A, and the width W4 of the right protection member 40B is larger than that of the right steam inlet 12B. It is larger than the width W3. The left side width W4 and the right side width W4 are not limited to be the same.

  Thus, according to the present embodiment, the width W4 of the protective members 40A, 40B provided above the upper tube groups 21A, 21B is the width of the vapor inlets 12A, 12B corresponding to the protective members 40A, 40B. It is larger than W3. As a result, the exhaust steam flowing down from the steam inlets 12A, 12B can be received by the protection members 40A, 40B and guided to the central flow passage 32 provided between the two tube group constituent bodies 20A, 20B. . Therefore, it is possible to suppress the exhaust steam that has flowed in from the steam inlets 12A and 12B from flowing straight down to the upper tube groups 21A and 21B. Further, it is possible to prevent the heat transfer tubes 23 of the upper tube groups 21A and 21B from vibrating when the protection members 40A and 40B receive the flow velocity of the exhaust steam. As a result, the protection members 40A and 40B can protect the upper tube groups 21A and 21B, the possibility of damage to the heat transfer tubes 23 can be reduced, and the reliability can be improved. Further, since the exhaust steam flowing down from the steam inflow ports 12A, 12B can be guided to the central flow path 32, the exhaust steam flowing into the tube group constituent bodies 20A, 20B can be guided around the tube group constituent bodies 20A, 20B. Can be equalized. Therefore, it is possible to equalize the flow rates of the exhaust steam flowing in the tube group constituent bodies 20A and 20B, and it is possible to further improve the condensation performance.

(Third Embodiment)
Next, a condenser according to the third embodiment of the present invention will be described with reference to FIG.

  In the third embodiment shown in FIG. 5, a pair of feed water heating pipes are provided between the steam inlet and the pipe group structure, and the gap between the feed water heating pipe and the side wall is the steam inlet. The main difference is that the width is smaller than the width, and the other structure is substantially the same as that of the first embodiment shown in FIGS. 1 to 3. In FIG. 5, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

  In the present embodiment, as shown in FIG. 5, feedwater heater 35 has a pair of feedwater heating pipes 36A and 36B. One of the pair of feed water heating pipes 36A and 36B is provided with one feed water heating pipe 36A on the side wall 16A side, and the other feed water heating pipe 36B is provided on the side wall 16B of the other side. More specifically, in FIG. 5, the left side feed water heating pipe 36A is arranged on the left side wall 16A side, and the right side feed water heating pipe 36B is arranged on the right side wall 16B side. In other words, in the width direction of the housing 11, the pair of feed water heating pipes 36A and 36B are arranged between the pair of side walls 16A and 16B, and are arranged side by side in the horizontal direction.

  A gap W5 is formed between the feed water heating pipes 36A and 36B and the side walls 16A and 16B corresponding to the feed water heating pipes 36A and 36B. The gap W5 is smaller than the width W3 of the steam inlets 12A and 12B. More specifically, in FIG. 5, the gap W5 between the left side feed water heating pipe 36A and the left side wall 16A is smaller than the width W3 of the left steam inlet 12A, and the right side feed water heating pipe 36B and the right side The gap W5 between the side wall 16B and the side wall 16B is smaller than the width W3 of the steam inlet 12B on the right side. Here, the gap W5 corresponds to the widthwise dimension of a space (flow path of exhaust steam) formed between the feed water heating pipes 36A and 36B and the corresponding side walls 16A and 16B. Note that the left-side gap W5 and the right-side gap W5 are not limited to being the same.

  Thus, according to the present embodiment, a pair of cylindrical feed water heating pipes 36A, 36B are provided between the steam inlets 12A, 12B and the upper pipe groups 21A, 21B of the pipe group constituent bodies 20A, 20B. The gap W5 between the feed water heating pipes 36A, 36B and the side walls 16A, 16B is smaller than the width W3 of the steam inlets 12A, 12B corresponding to the feed water heating pipes 36A, 36B. As a result, the exhaust steam having a large flow velocity out of the exhaust steam that has flowed in from the steam inlets 12A and 12B can be passed through the gap W5 between the feedwater heating pipes 36A and 36B and the side walls 16A and 16B. The steam can be caused to flow along the cylindrical surface of the feed water heating pipes 36A and 36B by the Coanda effect. Therefore, it is possible to suppress the exhaust steam that has flowed in from the steam inlets 12A and 12B from flowing straight down to the upper tube groups 21A and 21B, and to receive the flow rate of the exhaust steam, the heat transfer tubes 23 of the upper tube groups 21A and 21B. Can be suppressed from vibrating. As a result, it is possible to reduce the possibility of breakage of the heat transfer tube 23 and improve the reliability. Further, since the flow of the exhaust steam flowing down from the steam inlets 12A, 12B can be directed to the central flow path 32, the exhaust steam flowing into the pipe group constructing bodies 20A, 20B is prevented from flowing around the pipe group constructing bodies 20A, 20B. Can be equalized. Therefore, it is possible to equalize the flow rates of the exhaust steam flowing in the tube group constituent bodies 20A and 20B, and it is possible to further improve the condensation performance. Further, although the condenser 10 shown in FIG. 5 may be provided with the protection members 40A and 40B as shown in FIG. 4, it is possible to eliminate the need to provide the protection members 40A and 40B. However, it is possible to suppress an increase in pressure loss of the exhaust steam.

(Fourth Embodiment)
Next, a condenser according to the fourth embodiment of the present invention will be described with reference to FIG.

  In the fourth embodiment shown in FIG. 6, a pair of bending members is provided between the steam inflow port and the tube group constructing body, and the gap between the bending member and the side wall is larger than the width of the steam inflow port. The main difference is that it is also smaller, and other configurations are substantially the same as those of the first embodiment shown in FIGS. 1 to 3. In FIG. 6, the same parts as those of the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

  In the present embodiment, as shown in FIG. 6, a pair of bending members 50A and 50B are provided between the steam inlets 12A and 12B and the tube group constituent bodies 20A and 20B. Each of the bending members 50A and 50B extends in the direction along the heat transfer tube 23.

  One bending member 50A of the pair of bending members 50A and 50B is arranged on the side wall 16A side and is curved so as to be convex toward the side wall 16A. The other bending member 50B is arranged on the side of the other side wall 16B and is curved so as to be convex toward the side wall 16B. More specifically, in FIG. 6, the left side bending member 50A is arranged on the left side wall 16A side and is curved so as to be convex toward the left side wall 16A. The right bending member 50B is arranged on the side of the right side wall 16B and is curved so as to be convex toward the right side wall 16B. In other words, in the width direction of the housing 11, the pair of bending members 50A and 50B are arranged between the pair of side walls 16A and 16B and arranged in parallel in the horizontal direction. The configurations of the bending members 50A and 50B are not particularly limited, but for example, a plate-shaped member may be bent to be curved.

  A gap W6 indicated by W6 is formed between the bending members 50A and 50B and the side walls 16A and 16B corresponding to the bending members 50A and 50B. The gap W6 is smaller than the width W3 of the steam inlets 12A and 12B. More specifically, in FIG. 6, the gap W6 between the left bending member 50A and the left sidewall 16A is smaller than the width W3 of the left steam inlet 12A, and the right bending member 50B and the right sidewall are separated. The gap W6 with 16B is smaller than the width W3 of the steam inlet 12B on the right side. Here, the gap W6 corresponds to the widthwise dimension of the space (flow path of exhaust steam) formed between the curved members 50A and 50B and the corresponding side walls 16A and 16B. The left gap W6 and the right gap W6 are not limited to being the same.

  As described above, according to the present embodiment, the pair of bending members 50A and 50B are provided between the steam inlets 12A and 12B and the upper tube groups 21A and 21B of the tube group constituting bodies 20A and 20B, and the bending member 50A is provided. , 50B and the side walls 16A, 16B, a gap W6 is smaller than a width W3 of the steam inlets 12A, 12B corresponding to the bending members 50A, 50B. As a result, of the exhaust steam that has flowed in from the steam inlets 12A and 12B, the exhaust steam having a high flow velocity can pass through the gap W6 between the bending members 50A and 50B and the side walls 16A and 16B. Can be made to flow along the surfaces of the bending members 50A and 50B by the Coanda effect. Therefore, it is possible to suppress the exhaust steam that has flowed in from the steam inlets 12A and 12B from flowing straight down to the upper tube groups 21A and 21B, and to receive the flow rate of the exhaust steam, the heat transfer tubes 23 of the upper tube groups 21A and 21B. Can be suppressed from vibrating. As a result, it is possible to reduce the possibility of breakage of the heat transfer tube 23 and improve the reliability. Further, since the flow of the exhaust steam flowing down from the steam inlets 12A, 12B can be directed to the central flow path 32, the exhaust steam flowing into the pipe group constructing bodies 20A, 20B is prevented from flowing around the pipe group constructing bodies 20A, 20B. Can be equalized. Therefore, it is possible to equalize the flow rates of the exhaust steam flowing in the tube group constituent bodies 20A and 20B, and it is possible to further improve the condensation performance. Further, although the condenser 10 shown in FIG. 6 may be provided with the protection members 40A and 40B as shown in FIG. 4, it is possible to eliminate the need to provide the protection members 40A and 40B. However, it is possible to suppress an increase in pressure loss of the exhaust steam.

  According to the embodiment described above, the condensation performance can be improved.

    Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and the gist of the invention, and are also included in the invention described in the claims and the scope equivalent thereto. Further, as a matter of course, these embodiments can be partially combined as appropriate within the scope of the gist of the present invention.

1: Steam turbine, 10: Condenser, 11: Housing, 12A, 12B: Steam inlet, 16A, 16B: Side wall, 20A, 20B: Tube group constituent body, 21A, 21B: Upper tube group, 22A, 22B : Lower tube group, 23: heat transfer tube, 24: vertical flow path, 25: radial flow path, 36, 36A, 36B: feed water heating tube, 40A, 40B: protective member, 50A, 50B: curved member

Claims (6)

A condenser for condensing exhaust steam discharged from a steam turbine with a cooling medium,
A housing having a pair of side walls facing each other,
A pair of steam inflow ports provided in the upper part of the housing and through which the exhaust steam flows, wherein one of the steam inflow openings extends from one of the side walls to the inside of the housing and the other A pair of steam inlets of which the steam inlets extend from the other side wall to the inside of the housing;
A pair of tube group constituents provided below the steam inlet, one of the tube group constituents is arranged on the side of the one side wall, and the other of the tube group constituents, A pair of tube group constituents arranged on the side of the other side wall,
A central flow path provided between the pair of tube group constituents ,
The tube group constituent member has an upper tube group and a lower tube group arranged below the upper tube group, respectively,
The upper tube group and the lower tube group each have a plurality of heat transfer tubes extending in the direction along the side wall and through which the cooling medium flows,
Wherein the upper tube bundle, the gap between the side wall corresponding to the upper tube group, rather smaller than the gap between the lower tube group and the side wall which is arranged below of the upper tube bundle,
The gap between the upper tube group and the side wall corresponding to the upper tube group is smaller than the width of the steam inlet extending from the side wall,
The arrangement pitch of the heat transfer tubes adjacent to each other on the outer edge side of the tube group constituent is larger than the arrangement pitch of the heat transfer tubes adjacent to each other on the center side of the tube group constituent. vessel. When viewed in a cross section perpendicular to the longitudinal direction of the heat transfer tube, the tube group constituent body corresponds to the tube group constituent body rather than the center of the tube group constituent body in the upper edge of the tube group constituent body. The condenser according to claim 1 , further comprising a vertical flow path extending downward from a portion on the side of the side wall. When viewed in a cross section perpendicular to the longitudinal direction of the heat transfer tube, the tube group constituting body, toward the center of the tube group constituting body, out of the outer edges of the tube group constituting body, the other side of the center. A portion on the side of the tube group constituent and a portion on the side of the side wall corresponding to the tube group constituent with respect to the center, and a part of the lower tube group, having a radial flow path extending from The condenser according to claim 1 or 2 , characterized in that Further comprising a pair of protection members provided between the steam inlet and the pipe group structure, for receiving the exhaust steam flowing from the steam inlet,
One of the protection members is arranged above one of the tube group constituents, and the other protection member is arranged above the other tube group constituents,
The condenser according to any one of claims 1 to 3 , wherein a width of the protection member is larger than a width of the steam inlet corresponding to the protection member. Provided between the steam inlet and the tube group structure, further comprising a pair of cylindrical feed water heating tubes extending in a direction along the heat transfer tube,
One of the feed water heating pipe is arranged on the side of the one side wall, the other feed water heating pipe is arranged on the side of the other side wall,
The clearance between the feed water heating pipe and the side wall corresponding to the feed water heating pipe is smaller than the width of the steam inlet, and the recovery according to any one of claims 1 to 4. Water bottle. Provided between the steam inlet and the tube group structure, further comprising a pair of curved members extending in a direction along the heat transfer tube,
One of the bending members is arranged on the side of the one side wall and curved so as to be convex toward the side wall, and the other bending member is arranged on the side of the other side wall. , Curved so as to be convex toward the side wall,
The condenser according to any one of claims 1 to 4 , wherein a gap between the bending member and the side wall corresponding to the bending member is smaller than a width of the steam inlet. .

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